JP2004293862A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the man-hour for molding heat transfer plates composing a heat exchanger, with respect to the heat exchanger used in a heat exchanging ventilation device and the other air conditioner. <P>SOLUTION: The heat conductive plate A1 and the heat transfer plate B2 are simultaneously and integrally molded respectively from one sheet of material to have a corrugated heat transfer face A6, a header part 7, an outer peripheral rib A8, an outer peripheral rib B9, an air trunk rib A13, an air trunk outlet and inlet port 19, a heat transfer face B15, an air trunk end face 12, a projection A14 and an air trunk end face cover 11. Whereby the man-hour for molding the heat transfer plates can be reduced in manufacturing the heat exchanger. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a heat exchanger used in a heat exchange ventilator or other air conditioners, in which a large number of heat transfer plates are alternately stacked to form air paths A and B alternately.
[0002]
[Prior art]
Conventionally, this type of heat exchanger is known from Japanese Patent Application Laid-Open No. Hei 10-89879 (see Patent Document 1).
[0003]
Hereinafter, the heat exchanger will be described with reference to FIGS. 24, 25, 26, 27, 28 and 29.
[0004]
As shown in FIGS. 24 and 25, the heat exchanger 101 has a large number of heat exchange members 102 stacked, and the end of each of the stacked heat exchange members 102 other than the air passage entrance and exit is a sealing member having a structure as shown in FIG. 103, 104, 105 or a sealing structure as shown in FIG. 27, the heat exchange member 102 has a corrugated portion 106 of a predetermined size formed in the width direction and headers at both ends in the longitudinal direction. A partition 107 is provided. The corrugated portion 106 of the heat exchange member 102 is formed by a corrugating machine or the like, and the header partitioning portion 107 crushes both ends of the corrugated portion 106 or joins the header partitioning portion 107 formed as a separate member to both ends of the corrugated portion 106. The sealing members 103, 104, and 105 are obtained by applying a hot melt or the like to the header section 107 after the formation of the corrugated portions 106. The sealing structure shown in FIG. It is obtained by bending the end of the header section 107 after the molding of 106.
[0005]
In the heat exchanger 101 configured as described above, one end of the heat exchange air passage formed in the first stage is provided on the header portion 108 which opens in the direction indicated by the arrow b in FIG. d, and one end of the heat exchange air passage formed in the second stage is connected to the header portion 110 which opens in the direction indicated by the arrow a in the figure, and the other end is connected to the header portion 110. L-shaped heat exchange air passages are respectively formed in communication with the header portions 111 that open in the direction indicated by the arrow c, and the remaining heat exchange air passages are arranged by repeating the above-described configuration sequentially and alternately. I have. The fluid A sent from the direction of arrow a in the drawing via each header portion 110 and the fluid B sent from the direction of arrow b in the drawing via each header portion 108 alternately face each heat exchange air path. The heat exchange is performed by the flow, and the heat is sent out through the header portions 111 and 109 from the directions indicated by arrows c and d, respectively.
[0006]
Also, the cross section of the corrugated portion 106 at the time of lamination has a shape as shown in FIGS. 28 and 29. When the lamination as shown in FIG. 28 is formed, the heat exchange member 102 is interposed via the partition member 112. Are laminated.
[0007]
[Patent Document 1]
JP-A-10-89879
[0008]
[Problems to be solved by the invention]
In such a conventional heat exchanger, a molding process of the corrugated portion 106 and a molding process of the sealing members 103, 104, and 105 using a corrugating machine or the like or a molding process of a sealing structure that bends the end of the header partition 107 is performed. There is a problem that they cannot be performed in the same process, and a reduction in the number of molding steps is required.
[0009]
Further, since the header portions 108 to 111 and the header partition portion 107 are supported only at the ends, there is a problem that the center portion is bent, the height of the heat exchange air passage is reduced, and the ventilation resistance is increased. There is a demand for a structure that ensures the height of the heat exchange wind path.
[0010]
Further, since the heat exchange member 102 has the corrugated portion 106, the heat exchange member 102 is deformed in the wave direction, and the heat exchange member 102 or the header partitioning portion 107 and the sealing members 103, 104, 105 or the sealing structure at the time of lamination. However, there is a problem that it is difficult to secure the contact between the members, and a structure for suppressing the deformation is required.
[0011]
Further, when the heat exchange member 102 is deformed in the wave direction, there is a problem that the shape of each heat exchange air passage is deformed and the airflow resistance is increased, and a reduction in airflow resistance is required.
[0012]
Further, since each heat exchange air passage is formed in an L-shape, the ratio of the fluid sent from each header portion passing through the inside of the L-shaped air passage where the air passage length is short increases, and the heat exchange air passage becomes large. There is a problem that a part of the member 102 does not function effectively for heat exchange, and improvement in heat exchange efficiency is required.
[0013]
Further, in the case of the sealing structure in which the end of the header section 107 is bent, when a load is applied to the end of the heat exchanger 101 in the stacking direction, the end is easily crushed. There is a demand for improved strength in the direction.
[0014]
In addition, the configuration of each element part and the air path configuration of the air conditioner such as a heat exchange ventilator equipped with the heat exchanger 101 are also diversified, and a structure in which the air path configuration of the heat exchanger can be set according to the product design is required. Have been.
[0015]
In addition, from the viewpoint of energy saving for environmental protection in recent years, there is a demand for improvement of heat exchange efficiency and reduction of ventilation resistance for reducing power consumption of fluid conveying means such as a blower.
[0016]
The present invention solves such a conventional problem, and can improve the production efficiency, improve the performance such as the heat exchange efficiency and reduce the airflow resistance, and improve the degree of freedom in designing the main body. It is an object of the present invention to provide a heat exchanger capable of improving the heat exchanger.
[0017]
[Means for Solving the Problems]
In order to achieve the above object, the heat exchanger of the present invention has a corrugated heat transfer surface A, a header portion, an outer peripheral rib A, an outer peripheral rib B, an air path rib A, an air path entrance / exit, a heat transfer surface B, an air path. The heat transfer plate A and the heat transfer plate B are simultaneously and integrally formed using one sheet as a material so that the heat transfer plate A and the heat transfer plate B are provided so as to include the end face, the protrusion A, and the air path end face cover. When the layers are alternately stacked, the upper surfaces of the air path ribs A, the protrusions A, and the outer peripheral ribs B are in contact with the heat transfer plates stacked upward.
[0018]
ADVANTAGE OF THE INVENTION According to this invention, a shaping | molding man-hour can be reduced and the heat exchanger which can ensure the heat-exchange wind path height and can reduce ventilation resistance can be obtained.
[0019]
Further, another means is provided with an inclined portion inclined from the vertex of the waveform to the header portion at both ends in the longitudinal direction of the wave-shaped heat transfer surface A, and the angle between the inclined portion and the header portion is such that the fluid A and the fluid B are The angle is designed to be along the inner surface and the outer surface of the inclined portion.
[0020]
And according to this invention, the heat exchanger which can improve heat exchange efficiency and can reduce ventilation resistance can be obtained.
[0021]
Another means is that the cross-sectional shape of the heat transfer surface A is a substantially triangular continuous wave shape, and when the heat transfer plates A and B are alternately stacked, the substantially triangular peaks of the adjacent heat transfer plates are formed. And the valleys face each other.
[0022]
According to the present invention, it is possible to obtain a heat exchanger capable of improving production efficiency and improving heat exchange efficiency.
[0023]
Another means is to provide at least one projection B on the heat transfer plate A when the heat transfer plate A and the heat transfer plate B are alternately stacked on the substantially triangular crest of the heat transfer surface A. The projections B and the projections B provided on the heat transfer plate B are provided in a positional relationship such that they do not overlap.
[0024]
And according to this invention, the heat exchanger which can reduce ventilation resistance can be obtained.
[0025]
Another means is characterized in that, when the heat transfer plates A and B are alternately stacked, the substantially triangular peaks and valleys of adjacent heat transfer plates face each other.
[0026]
And according to this invention, the heat exchanger which can improve heat exchange efficiency can be obtained.
[0027]
Further, another means is to provide a flat portion at the top of a substantially triangular crest and valley forming the corrugated shape of the heat transfer surface A, and when the heat transfer plates A and B are alternately stacked, they are adjacent to each other. The flat portion provided in the peak portion of the heat transfer plate and the flat portion provided in the valley portion are in contact with each other.
[0028]
And according to this invention, the heat exchanger which can reduce ventilation resistance can be obtained.
[0029]
Further, other means include a top of at least one or more peaks of a substantially triangular shape forming a wave shape of the heat transfer surface A and a valley of at least one or more portions of a substantially triangle forming a wave shape of the heat transfer surface A When a heat transfer plate A and a heat transfer plate B are alternately stacked on the top of the heat transfer plate A, the flat portion provided on the crest portion of the adjacent heat transfer plate and the flat portion provided on the valley portion contact each other. It is characterized by the following.
[0030]
According to the present invention, it is possible to obtain a heat exchanger capable of reducing the ventilation resistance and improving the heat exchange efficiency.
[0031]
Further, another means is characterized in that a flat portion is provided intermittently at the top of the substantially triangular peaks and valleys forming the corrugated shape of the heat transfer surface A.
[0032]
According to the present invention, it is possible to obtain a heat exchanger capable of reducing the ventilation resistance and improving the heat exchange efficiency.
[0033]
Another means is characterized in that a flat portion is provided only on one of the substantially triangular peaks or valleys forming the corrugated shape of the heat transfer surface A.
[0034]
According to the present invention, it is possible to obtain a heat exchanger capable of reducing the ventilation resistance and improving the heat exchange efficiency.
[0035]
Another means is characterized in that the cross-sectional shape of the heat transfer surface A is a wave shape in which a substantially semicircular curved surface is continuous.
[0036]
And according to this invention, the heat exchanger which can improve heat exchange efficiency can be obtained.
[0037]
Another means is to provide a division on the heat transfer surface A, which divides the wave shape into a plurality of parts in the longitudinal direction, and the division part is substantially orthogonal or substantially oblique to the longitudinal direction of the wave shape formed on the heat transfer surface A. It is characterized by being formed to intersect.
[0038]
According to the present invention, it is possible to obtain a heat exchanger capable of improving heat exchange efficiency and suppressing deformation of the heat transfer plate in the wave direction.
[0039]
Another means is that the wave shape formed on the heat transfer surface A having a plurality of wave shapes divided into a plurality in the longitudinal direction is substantially half the wave shape formed on the adjacent heat transfer surface A via the division portion. The wavelength phase is shifted.
[0040]
According to the present invention, it is possible to obtain a heat exchanger capable of improving heat exchange efficiency and suppressing deformation of the heat transfer plate in the wave direction.
[0041]
Further, another means is characterized in that a deformation suppressing rib is provided in a divided portion that divides the heat transfer surface A formed in a wavy shape into a plurality in the longitudinal direction.
[0042]
According to the present invention, it is possible to obtain a heat exchanger capable of suppressing deformation of the heat transfer plate in the wave direction.
[0043]
Further, another means is provided at each longitudinal end of each of the plurality of divided wave-shaped heat transfer surfaces A with an inclined portion inclined from a vertex of a waveform to a divided portion, and an angle formed between the inclined portion and the divided portion. Is an angle designed so that the fluid A and the fluid B are along the inner surface and the outer surface of the inclined portion.
[0044]
And according to this invention, the heat exchanger which can improve heat exchange efficiency and can reduce ventilation resistance can be obtained.
[0045]
Another means is that the width dimension of the outer peripheral rib A formed on the heat transfer plate A is smaller than the width dimension of the outer peripheral rib A formed on the heat transfer plate B, The convex height of the outer peripheral rib A is set to be larger than the convex height of the outer peripheral rib A formed on the heat transfer plate B, and the corrugated heat transfer surface A formed on the heat transfer plate A and the heat transfer surface An outer peripheral rib A formed on the heat plate A is provided with a flat portion on the adjacent heat transfer surface A, and is formed on the heat transfer plate A when the heat transfer plate A and the heat transfer plate B are alternately stacked. The upper surface of the outer circumferential rib A is in contact with the back surface of the outer circumferential rib A formed on the heat transfer plate B, and the upper surface of the outer circumferential rib A formed on the heat transfer plate B is provided on the heat transfer plate A. And contacting the back surface of the flat portion.
[0046]
And according to this invention, the heat exchanger which can improve the intensity | strength of the heat exchanger end part in the lamination direction can be obtained.
[0047]
Another means is that the air path rib A is formed on the corrugated heat transfer surface A and is continuously formed with a waveform protruding in the same direction as the convex direction of the air path rib A with respect to the header portion, The number of air path ribs A is smaller than the number of waveforms protruding from the header in the same direction as the convex direction of the air path ribs A.
[0048]
According to the present invention, it is possible to obtain a heat exchanger capable of reducing the ventilation resistance and improving the heat exchange efficiency.
[0049]
Another means is to provide a plurality of air path ribs A and a plurality of air path ribs B formed in the header portion in a hollow convex shape in a direction opposite to the convex direction of the air path ribs A substantially in parallel with the air path entrance and exit. When the heat transfer plates A and the heat transfer plates B are alternately stacked, the upper surface of the air passage rib A formed on the adjacent heat transfer plate and the lower surface of the air passage rib B are in contact with each other.
[0050]
According to the present invention, it is possible to obtain a heat exchanger capable of suppressing deformation of the heat transfer plate in the wave direction.
[0051]
Further, another means is provided with an outer circumferential rib B continuously at both ends of one outer circumferential rib A, and provided with an air path entrance between both ends of the other outer circumferential rib A and one end of the outer circumferential rib B, A and heat transfer plates B are alternately laminated, and a substantially U-shaped air path A and an air path B are alternately formed.
[0052]
According to the present invention, it is possible to obtain a heat exchanger capable of improving the degree of freedom in designing the main body.
[0053]
Another means is to adjust the air path rib A so that the width of the air path located inside the substantially U-shaped air path A and the air path B is narrow and the width of the air path located outside is wide. It is characterized by being formed at equal intervals.
[0054]
And according to this invention, the heat exchange air which can improve heat exchange efficiency can be obtained.
[0055]
BEST MODE FOR CARRYING OUT THE INVENTION
The present invention includes a heat transfer plate A and a heat transfer plate B, wherein the heat transfer plate A includes a wave-shaped heat transfer surface A and header portions at both longitudinal ends of the waveform of the heat transfer surface A, The surface A includes a pair of outer peripheral edges that are substantially parallel to the longitudinal direction of the waveform. The outer peripheral ribs A are formed in a hollow convex shape on the pair of outer peripheral edges. An outer peripheral rib B formed in a hollow convex shape in the same direction as the convex direction of the outer peripheral rib B and an air path rib A formed in a hollow convex shape in the same direction as the convex direction of the outer peripheral rib A are substantially equally spaced in parallel with the outer peripheral rib B. One end of the outer peripheral rib A is formed continuously with one end of the outer peripheral rib B, and the other end of the outer peripheral rib A and the other end of the outer peripheral rib B on the outer peripheral edge of the header portion are provided. A plurality of air passages and a heat transfer surface B are formed in the header portion by the air passage rib A. An air path end face is provided at an entrance and exit of the air path, and the air path end face is provided by bending the header portion in a direction opposite to a convex direction of the air path rib A, on an extension of the plurality of air path ribs A. A plurality of hollow convex protrusions A are provided in the same direction as the convex direction of the air path rib A in the vicinity of the air path end face, and a central portion of an outer side surface of the outer peripheral rib B is flush with the header section. At both ends of the outer side surface of the outer peripheral rib B, an air path end face cover is provided that is turned up to the same position as the turn position of the air path end face, and the heat transfer plate B has a mirror image relationship with the heat transfer plate A. None, the heat transfer plate A and the heat transfer plate B are alternately stacked so that the outer circumferential rib A of the heat transfer plate A and the outer circumferential rib A of the heat transfer plate B overlap each other. The air path A and the air path B are alternately formed by laminating the heat transfer plate B with the heat transfer plate A. When the heat transfer plates B are alternately stacked, the upper surfaces of the air path ribs A, the protrusions A, and the outer peripheral ribs B are in contact with the heat transfer plates stacked upward, and the outer side surface of the protrusion A is The outer circumferential rib provided on the heat transfer plate located on the air path end face and below the air path end face, in contact with the inner side surface of the outer circumferential rib B provided on the heat transfer plate stacked above the protrusion A B, the outer side surfaces of the heat transfer plate A and the side surfaces of the outer peripheral ribs A provided on the heat transfer plate B are in contact with each other, and are located below the air path end face cover and the air path end face cover. A heat exchanger in which end faces of the outer peripheral ribs A and the outer peripheral ribs B provided on the heat transfer plate to be abutted, wherein the heat transfer plate A and the heat transfer plate B are each made of one sheet, A wave-shaped heat transfer surface A, the header portion, the outer peripheral rib A, the outer peripheral rib B, The air path rib A, the heat transfer surface B, the air path end face, the plurality of protrusions A, and the air path end face cover are molded simultaneously and integrally, and the heat transfer plate A and the heat transfer plate B are formed. When alternately stacking, the upper surface of the air passage rib A and the upper surface of the outer peripheral rib B abut against the back surface of the header portion of the heat transfer plate stacked upward, thereby increasing the air passage height in the header portion. And the upper surface of the projection A is in contact with the rear surface of the outer peripheral rib B of the heat transfer plate laminated on the upper side, so that the opening height of the air path entrance / exit can be ensured.
[0056]
Further, the outer side surface of the protrusion A is in contact with the inner side surface of the outer peripheral rib B provided on the heat transfer plate laminated above the protrusion A, and is located below the air path end surface and the air path end surface. The outer side surfaces of the outer peripheral ribs B provided on the heat transfer plate abut, the side surfaces of the outer peripheral ribs A provided on the heat transfer plate A and the outer peripheral ribs A provided on the heat transfer plate B respectively abut, and the wind path end surface cover When the end faces of the outer peripheral ribs A and B provided on the heat transfer plate located below the air path end face cover are in contact with each other, the outer peripheral portions of the air paths A and B are sealed. Done.
[0057]
Further, the heat transfer plate A and the heat transfer plate B are each made of one sheet, and the corrugated heat transfer surface A, the header portion, the outer peripheral rib A, the outer peripheral rib B, and the air path rib are used. A, the heat transfer surface B, the air path end surface, the plurality of projections A, and the air path end surface cover are formed simultaneously and integrally, thereby reducing the number of molding steps.
[0058]
In addition, at both ends in the longitudinal direction of the wave-shaped heat transfer surface A, an inclined portion is provided which is inclined from the vertex of the waveform to the header portion, and the angle between the inclined portion and the header portion is formed by the fluid A and the fluid B. The fluid A and the fluid B that have passed through the header portion are designed to be along the inner surface and the outer surface of the heat transfer surface A when the fluid A and the fluid B flow into the corrugated heat transfer surface A without being separated from the heat transfer plate. Since the fluid flows along the inclined portion, heat exchange is performed between the fluid A and the fluid B also in the inclined portion, so that the heat exchange efficiency is improved and the air flow resistance can be reduced.
[0059]
Further, the wave shape of the heat transfer surface A is a wave shape in which substantially triangles are continuous, and when the heat transfer plate A and the heat transfer plate B are alternately stacked, the heat transfer surface A formed on the adjacent heat transfer plate is formed. And the substantially triangular valleys of the heat transfer surface A formed on the heat transfer plate A and the heat transfer plate B face each other. Since the air path height of the path B is ensured by the upper surface of the air path rib A and the upper surface of the outer peripheral rib B abutting against the back surface of the header portion of the heat transfer plate laminated above, the heat transfer plate A When stacking the heat transfer plate B, it is not necessary to interpose a partitioning member between the heat transfer plate A and the heat transfer plate B, so that the number of production steps can be reduced, and the heat transfer surface A This has the effect of improving the heat transfer performance at the top of the substantially triangular wavy shape.
[0060]
Further, at least one protrusion B is provided on a substantially triangular crest of the heat transfer surface A formed on the heat transfer plate A and the heat transfer plate B, and the protrusion B is provided on the heat transfer plate A and the heat transfer plate. When the layers B are alternately stacked, the protrusions B provided on the heat transfer plate A and the protrusions B provided on the heat transfer plate B are provided in a positional relationship such that they do not overlap, and the upper surface of the protrusion B is located above the protrusion B. The heat transfer surface A formed on the heat transfer plate located at the bottom is in contact with the back surface of the substantially triangular crest, and the upper surface of the protrusion B is formed on the heat transfer plate located above the protrusion B. By contacting the rear surface of the substantially triangular crest of the heat transfer surface A, the wavy air path height of the heat transfer surface A is ensured, and the airflow resistance due to the deformation of the air path shape is reduced. It has the effect of preventing an increase.
[0061]
When the heat transfer plates A and B are alternately stacked, the substantially triangular peaks and valleys of the heat transfer surface A formed on the adjacent heat transfer plates are opposed to each other. Since the air path A and the air path B are divided into a plurality of substantially rhombic air paths on the surface A, the fluid A and the fluid B which have passed through one header portion and flowed into the heat transfer surface A are the heat transfer surfaces. When passing through the air path formed on the surface A, the heat flows along the longitudinal direction of the wave shape of the heat transfer surface A without moving in the wave direction, and flows into the other header portion. In addition, the heat transfer surface A and the heat transfer surface B of the heat transfer plate B have an effect of effectively functioning for heat transfer.
[0062]
In addition, when a flat portion is provided at the top of a substantially triangular crest and valley that forms the corrugated shape of the heat transfer surface A, and when the heat transfer plates A and B are alternately stacked, the adjacent heat transfer plates The flat portion provided in the peak portion and the flat portion provided in the valley portion are in contact with each other, and the flat portion provided in the peak portion of the adjacent heat transfer plate and the flat portion provided in the valley portion are in contact with each other, whereby The heat transfer surface A has an effect that the wavy air path height is secured, and an increase in airflow resistance due to deformation of the air path shape can be prevented.
[0063]
In addition, a flat surface is formed on the top of at least one or more peaks of a substantially triangular shape forming the wave shape of the heat transfer surface A, and on the top of at least one or more valleys of the substantially triangle forming the wave shape of the heat transfer surface A. When the heat transfer plate A and the heat transfer plate B are alternately stacked, the flat portion provided on the peak portion of the adjacent heat transfer plate and the flat portion provided on the valley portion are in contact with each other. The flat portion of the adjacent heat transfer plate abuts on the heat transfer surface A, thereby ensuring a corrugated air path height, preventing an increase in airflow resistance due to deformation of the air path shape, By reducing the area of the flat part, the effective area contributing to the heat transfer on the heat transfer surface A is increased, and the heat exchange efficiency is improved.
[0064]
In addition, a flat portion is provided intermittently at the top of the substantially triangular peaks and valleys forming the corrugated shape of the heat transfer surface A, and when the heat transfer plates A and B are alternately stacked. When the flat portions of the adjacent heat transfer plates abut, the corrugated air path height of the heat transfer surface A is secured, and an increase in airflow resistance due to deformation of the air path shape can be prevented. Providing the portions intermittently has the effect of increasing the effective area contributing to the heat transfer on the heat transfer surface A and improving the heat exchange efficiency.
[0065]
Further, a flat portion is provided at one of the tops of the substantially triangular peaks or valleys forming the corrugated shape of the heat transfer surface A of the heat transfer plate A and the heat transfer plate B. When the heat plates B are alternately stacked, the flat portion of the adjacent heat transfer plate and the top of the peak portion or the valley portion are in contact with each other, so that the wave-shaped wind path height of the heat transfer surface A is ensured. In addition, it is possible to prevent an increase in airflow resistance due to deformation of the air path shape, and when the flat portion and the top of the peak portion or the valley portion are in contact with each other, heat exchange is also performed in the flat portion, so that transmission is performed. This has the effect of increasing the effective area contributing to the heat transfer on the hot surface A and improving the heat exchange efficiency.
[0066]
The wave shape of the heat transfer surface A is a wave shape in which a substantially semicircular curved surface is continuous, and the area of the heat transfer surface A can be increased as compared with the substantially triangular wave shape. This has the effect of improving the exchange efficiency.
[0067]
Further, the heat transfer plate A and the heat transfer plate B each include a dividing portion that divides the heat transfer surface A formed in a wave shape into a plurality of portions in the longitudinal direction, and the split portion has a wave shape formed on the heat transfer surface A. The heat transfer surface A is formed so as to be substantially orthogonal or substantially oblique to the longitudinal direction of the heat transfer surface A. The heat transfer plate A and the heat transfer plate B are formed by increasing the temperature boundary layer and promoting heat transfer by forming the divided portion so as to be substantially orthogonal or substantially oblique to the longitudinal direction of the wave shape. Has the effect of suppressing deformation in the wave direction.
[0068]
In addition, the wave shape formed on the heat transfer surface A having a plurality of wave shapes divided into a plurality in the longitudinal direction is substantially out of phase with the wave shape formed on the adjacent heat transfer surface A via the split portion. The fluid A and the fluid B that have passed through the wave-shaped heat transfer surface A formed on the upstream side with respect to the division portion are provided with the wave-shaped heat transfer surface formed on the downstream side with respect to the division portion. When flowing into the surface A, it collides with the wave-shaped front edge formed on the downstream side, and thus has the effect of promoting heat transfer.
[0069]
Further, a deformation suppressing rib is provided in a divided portion that divides the heat transfer surface A formed in a wavy shape into a plurality in the longitudinal direction, and the deformation suppressing rib is substantially orthogonal to or oblique to the longitudinal direction of the wave shape. As a result, the heat transfer plate A and the heat transfer plate B have an effect of suppressing deformation in the wave direction.
[0070]
In addition, an inclined portion which is inclined from a vertex of a waveform to a divided portion is provided at both ends in the longitudinal direction of each of the plurality of divided wave-shaped heat transfer surfaces A, and the angle formed by the inclined portion and the divided portion is the fluid A And the fluid B is designed so as to be along the inner surface and the outer surface of the inclined portion, and flows into the divided portion through the wave-shaped heat transfer surface A formed on the upstream side with respect to the divided portion. And when flowing into the heat-transfer surface A in a wave shape formed on the downstream side with respect to the divided portion after passing through the divided portion, flows along the inclined portion without peeling off from the heat transfer plate. In this case, heat exchange is performed between the fluid A and the fluid B, the heat exchange efficiency is improved, and the air flow resistance can be reduced.
[0071]
Further, the width of the outer peripheral ribs A formed on the heat transfer plate A is made smaller than the width of the outer peripheral ribs A formed on the heat transfer plate B, and the outer peripheral ribs A formed on the heat transfer plate A are formed. The convex height of the heat transfer plate B is set to a dimension higher than the convex height of the outer peripheral rib A formed on the heat transfer plate B, and the corrugated heat transfer surface A formed on the heat transfer plate A and the heat transfer plate A A flat portion is provided on the heat transfer surface A adjacent to the formed outer circumferential rib A, and when the heat transfer plate A and the heat transfer plate B are alternately stacked, the outer circumferential rib formed on the heat transfer plate A is provided. A upper surface of the outer peripheral rib A formed on the heat transfer plate B is in contact with the back surface of the outer peripheral rib A, and the upper surface of the outer peripheral rib A formed on the heat transfer plate B is provided on the heat transfer plate A. The heat transfer plate A and the heat transfer plate B are alternately stacked when the heat transfer plate A and the heat transfer plate B are alternately stacked. The upper surface of the peripheral rib A was in contact with the back surface of the outer peripheral rib A formed on the heat transfer plate B, and the upper surface of the outer peripheral rib A formed on the heat transfer plate B was provided on the heat transfer plate A. The contact with the rear surface of the flat portion has an effect of improving the strength of the outer peripheral rib A against a load in the stacking direction.
[0072]
A plurality of air path ribs A provided on the header portions of the heat transfer plate A and the heat transfer plate B are formed on the corrugated heat transfer surface A and are in the same direction as the convex direction of the air path ribs A with respect to the header portion. The number of the air path ribs A is smaller than the number of waveforms projecting in the same direction as the convex direction of the air path ribs A with respect to the header portion. By continuously forming the wave shape of the air path rib A and the heat transfer surface A, a plurality of continuous air paths are formed between one of the air path entrances and the other entrance, and each air path is formed. Since the average lengths of the passages are substantially equal, the fluid A and the fluid B flowing from one of the air passage entrances and exits flow substantially uniformly through the air passages A and B, and the heat transfer surface A and the heat transfer surface B functions effectively for heat transfer, and the fluid A and the fluid B B flows almost uniformly, and the number of the air path ribs A is provided to be smaller than the number of waveforms protruding in the same direction as the convex direction of the air path ribs A with respect to the header portion, whereby the airflow resistance can be reduced. It has the action of:
[0073]
Further, the heat transfer plate A and the heat transfer plate B are formed such that the air passage rib A and the air passage rib B formed in a hollow convex shape in a direction opposite to the convex direction of the air passage rib A are substantially parallel to the air passage entrance and exit. When a plurality of the heat transfer plates A and the heat transfer plates B are alternately stacked, the upper surface of the air passage rib A formed on the adjacent heat transfer plate and the lower surface of the air passage rib B contact each other. Since the air path rib A and the air path rib B are formed so as to intersect vertically in the header portion, the heat transfer plate A and the heat transfer surface A of the heat transfer plate B are formed in a wave direction. It has the effect of suppressing deformation.
[0074]
Further, the heat transfer plate A and the heat transfer plate B are provided with an outer circumferential rib B continuously at both ends of one outer circumferential rib A of a pair of outer circumferential ribs A facing each other, and both ends of the other outer circumferential rib A and the outer circumferential rib B are formed. An air passage entrance and exit is provided between the heat transfer plate A and the heat transfer plate B. The heat transfer plate A has an outer peripheral rib A overlapping the outer peripheral rib A of the heat transfer plate B. The heat transfer plate A and the heat transfer plate B are formed such that an air passage entrance and exit of the heat plate B is formed, and an air passage entrance and exit of the heat transfer plate A is formed above the outer peripheral rib B of the heat transfer plate B. A substantially U-shaped air path A and an air path B are alternately formed by laminating the heat transfer plate A and the heat transfer plate B alternately. Are formed in the same direction with respect to the outer peripheral rib A, so that there is an effect that the degree of freedom in designing the main body is improved.
[0075]
In addition, a plurality of winds are provided at unequal intervals in the header portion so that the width of the air passages located inside the substantially U-shaped air passages A and B is narrow and the width of the air passages located outside is wide. A path rib A is formed, and a plurality of air paths formed in the air path A and the air path B have a shorter air path length on the inner side, and an outer air path length on the outer side has a longer air path length. By increasing the width of the air passage, the ventilation resistance of each of the plurality of air passages formed in the air passage A and the air passage B becomes equal, and the fluid A and the fluid B flowing in from one of the air passage entrances and exits are separated by the wind. The heat transfer surface A and the heat transfer surface B flow almost uniformly, and the entire surface of the heat transfer surface A and the heat transfer surface B functions effectively for heat transfer.
[0076]
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0077]
【Example】
(Example 1)
Hereinafter, Embodiment 1 of the present invention will be described with reference to FIGS. 1, 2, 3, 4, 5, and 6.
[0078]
FIG. 1 is a schematic exploded perspective view of a heat exchanger used in the present embodiment, FIG. 2 is a schematic perspective view of a heat transfer plate when stacked, FIG. FIG. 4 is a schematic sectional view of an airway entrance / exit portion, FIG. 5 is a schematic sectional view of a corner portion where the airway entrance / exit is adjacent, and FIG. 6 is a top perspective view thereof.
[0079]
In FIGS. 1 and 2, a heat exchanger configured by alternately stacking heat transfer plates A1 and B2 has air passages A3 and B4 above and below each heat transfer plate, Fluids flowing through the air passages A3 and B4 exchange heat through the respective heat transfer plates, and flow obliquely in a header portion of each air passage and flow in a direction facing each other in a central portion. This is a counter-flow heat exchanger.
[0080]
Actually, many heat transfer plates A1 and heat transfer plates B2 are alternately stacked, but four heat transfer plates are shown for simplicity.
[0081]
As shown in FIG. 3, the heat transfer plate A1 has a heat transfer surface A6 having a trapezoidal cross section with a flat portion 5 at the apex of a triangle, and a trapezoidal wave-like continuous surface A6. Triangular header portions 7 are provided at both ends in a direction orthogonal to the cross-sectional direction.
[0082]
The trapezoidal flat portion 5 of the heat transfer surface A6 is formed so as to have a height of, for example, 1.3 mm with respect to the upper surface and the lower surface of the header portion 7, respectively, and the width of the flat portion 5 is formed, for example, to be 1 mm. ing.
[0083]
A pair of outer peripheral ribs A8 are formed in a hollow convex shape on the outer peripheral edge parallel to the wavy longitudinal direction of the heat transfer surface A6 so as to have, for example, a width of 3 mm and a height of 5.2 mm with respect to the upper surface of the header portion 7. The outer side surface is folded in a direction opposite to the convex direction, for example, to a position of 2.8 mm with respect to the upper surface of the header portion 7.
[0084]
A pair of outer peripheral ribs B9 are formed on the pair of outer peripheral edges of the header portion 7 so as to be continuous with the outer peripheral rib A8, for example, 5 mm in width, and the same as the convex direction of the outer peripheral rib A8 so as to have a height of 2.6 mm above the upper surface of the header portion 7. The central portion of the outer side surface is bent to the same position as the back surface of the header portion 7 to form an air passage opening portion 10, and both end portions, for example, a portion 5 mm from both ends, of the outer peripheral rib A are formed. The air path end surface cover 11 is bent to the same position as the outer side surface.
[0085]
At the outer peripheral edge of the header 7 where the outer peripheral rib B9 is not formed, the air path end face 12 is folded in a direction opposite to the convex direction of the outer peripheral rib B9 to, for example, a position of 2.8 mm with respect to the upper surface of the header 7. On the upper surface of the header section 7, five air path ribs A13 are arranged at equal intervals in parallel with the outer peripheral rib B9, for example, the width is 2 mm on the bottom side, 1 mm on the upper side, and 2.6 mm with respect to the upper surface of the header section 7. Is formed so that the end in the heat transfer surface A direction is smoothly continuous with the trapezoidal shape of the heat transfer surface A6. For example, a protrusion A14 having the same surface and having a height of 5.2 mm with respect to the header portion 7 is formed, and the other end of the air passage rib A13 is continuous with a surface facing the same surface as the air passage end surface of the protrusion A14. The header portion 7 is formed with the outer peripheral rib B9. The road rib A13 so that the plurality of air paths and heat transfer surface B15 is formed.
[0086]
A trapezoidal length having convex portions in both ends of the trapezoidal shape of the heat transfer surface A6 that is not continuous with the airflow rib A14 having a convex portion in the same direction as the convex direction of the airflow rib 14 and a convex portion in the back direction of the header portion. At both ends in the direction, inclined portions 16 forming an angle of, for example, 7 ° with the header portion 7 are formed.
[0087]
On the upper surface of the end of the outer circumferential rib B9 in the direction of the wind path end surface, a corner support protrusion 17 having the same width as the outer circumferential rib B9 and a shorter side smaller than the width of the outer circumferential rib B, for example, 3 mm, is provided on the upper surface of the outer circumferential rib B9. On the other hand, it is provided at a convex height of 2.6 mm.
[0088]
Further, a flat portion 18 is provided on the heat transfer surface A6 adjacent to the outer peripheral rib A8.
[0089]
The heat transfer plate B2 has a mirror image relationship with the heat transfer plate A1, and the convex height of the outer peripheral rib A8 of the heat transfer plate B2 in the shape of the heat transfer plate B2 is equal to the height of the air path rib A13. Is formed in a shape wider than the width of the outer peripheral rib A8 of the heat transfer plate A1 so as to be, for example, 5 mm.
[0090]
As a method of manufacturing the heat transfer plate A1 and the heat transfer plate B, for example, a vacuum forming method of a polystyrene sheet having a thickness of 0.2 mm can be mentioned. The components of the heat transfer plate A1 and the heat transfer plate B2 are simultaneously molded integrally by a vacuum molding method, and after the molding, the heat transfer plate A1 and the heat transfer plate B2 are obtained by trimming using, for example, a Thompson mold. Then, after a predetermined number of the heat transfer plates B2 are alternately stacked, the side surfaces are subjected to heat welding using, for example, a heater or the like, whereby a heat exchanger can be obtained.
[0091]
In the above configuration, when the heat transfer plate A1 and the heat transfer plate B2 are alternately stacked, as shown in FIG. 3, the upper surface of the outer peripheral rib A8 of the heat transfer plate A1 contacts the rear surface of the outer peripheral rib A8 of the heat transfer plate B2. When a part of the upper surface of the outer peripheral rib A8 of the heat transfer plate B2 comes into contact with the back surface of the flat portion 18 and the flat portion 5 formed on the heat transfer surface A6 of the adjacent heat transfer plates comes into contact, the wind is generated. The height of the air passage at the heat transfer surface A6 of the passage A3 and the air passage B4 is maintained, and the header portion of the heat transfer plate in which the upper surface of the outer peripheral rib B9 and the upper surface of the air passage rib A13 are stacked at the header portion 7 The air path A3 and the air path B4 maintain the air path height at the header section 7 by being in contact with the back surface of the air path 7, and at the air path entrance 19, as shown in FIG. The air path A3 and the air path B are brought into contact with the back surface of the outer peripheral rib B9 of the heat transfer plate. Holding the air duct opening height.
[0092]
The air path height of the air path A3 and the air path B4 is designed in view of the performance of the heat exchanger such as air flow resistance and the formability.
[0093]
The upper surface of the outer rib A8 of the heat transfer plate A1 is in contact with the back surface of the outer rib A8 of the heat transfer plate B2, and the upper surface of the outer rib A8 of the heat transfer plate B2 is in contact with the back surface of the flat portion 18. The contact between the upper surface of the projection A14 and the rear surface of the outer peripheral rib B9 of the heat transfer plate laminated above, and the corner support at the corner where the air path entrance 18 is adjacent as shown in FIGS. The strength of the heat exchanger in the stacking direction is maintained by the contact between the upper surface of the projection 17 and the back surface of the outer peripheral rib B9 stacked thereon.
[0094]
Also, as shown in FIGS. 3, 4 and 5, the outer side ribs A13 of the adjacent heat transfer plates are in contact with the outer side surface and the inner side, the air path end surface 12 is in contact with the outer peripheral rib B9, and the air path end face cover 11 is in contact. The outer peripheral rib B9 abuts against the outer peripheral rib B9 to seal the outer peripheral portions of the air passages A3 and B4.
[0095]
In addition, when the fluid flowing through the air passages A3 and B4 passes through the header portion 7 and flows into the heat transfer surface A6, or flows through the heat transfer surface A6 and flows into the header portion 7, the fluid is separated from the heat transfer plate. Since the air flows along the outer and inner surfaces of the inclined portion 16 without heat, heat is exchanged also in the inclined portion 16, and the air passage height changes smoothly, so that the ventilation resistance can be reduced.
[0096]
The angle between the inclined portion 16 and the header portion 7 is designed based on the amount of air, the shape of the air path, and the like so that the flow does not separate.
[0097]
Further, by providing five air path ribs A13 at regular intervals so that the trapezoidal shape of the heat transfer surface A6 is smoothly continuous, six air paths are formed in the header portion 7, and in the heat transfer surface A, The flat portion 5 formed on the heat transfer surface A6 of the adjacent heat transfer plates abuts to define a plurality of hexagonal air passages, thereby forming one of the air passages A3 and B4. Since the average length of a plurality of air paths formed from 19 to the other air path entrance 19 is equal, the fluid flowing through the air paths A3 and B4 flows almost uniformly through the air paths A3 and B4. Thus, the airflow resistance is reduced, and the entire surfaces of the heat transfer surface A6 and the heat transfer surface B15 function effectively for heat transfer.
[0098]
In the present embodiment, a polystyrene sheet was used as the material of the heat transfer plate and was integrally formed by vacuum forming. However, as a material, other thermoplastic resin films such as ABS, polypropylene, and polyethylene, and a thin metal plate such as aluminum were used. Or, a paper material having heat conductivity and moisture permeability, a microporous resin film, a paper material mixed with a resin, or the like may be used. The heat transfer plate may be integrally formed by a construction method, and the same operation and effect can be obtained by fixing each heat transfer plate by bonding or the like for heat welding.
[0099]
In addition, the dimensions and the number of each part are examples, and are not particularly limited to the values, even when appropriately designed in terms of heat resistance such as airflow resistance, heat exchange efficiency and molding workability, Similar functions and effects can be obtained.
[0100]
Further, a polystyrene sheet is used as the sheet material, and the thickness thereof is set to 0.2 mm. However, it is preferable to use a sheet having a thickness of 0.05 to 0.5 mm.
[0101]
The reason is that if the thickness is 0.05 mm or less, the sheet material is likely to be damaged at the time of forming the uneven shape, and at the time of handling the heat transfer plate after forming, such as tearing, and the formed heat transfer plate is stiff. In addition, the handleability deteriorates, and when it exceeds 0.5 mm, the heat conductivity decreases.
[0102]
As the sheet thickness decreases, the heat conductivity tends to increase and the formability tends to decrease. Conversely, as the sheet thickness increases, the heat conductivity tends to decrease.
[0103]
Therefore, in order to satisfy the formability and the heat transfer property, it is preferable to use a sheet having a thickness of 0.05 to 0.5 mm, more preferably 0.15 to 0.25 mm. Is most desirable.
[0104]
(Example 2)
Next, a second embodiment of the present invention will be described with reference to FIG.
[0105]
The same parts as those in the first embodiment are denoted by the same reference numerals, have the same functions and effects, and detailed description is omitted.
[0106]
FIG. 7 is a schematic cross-sectional view of the side surface of the heat exchanger used in the present embodiment and the air passage of the heat transfer surface A portion.
[0107]
As shown in FIG. 7, the heat transfer surface A6 of the heat transfer plate A1 and the heat transfer plate B2 has a wave shape in which triangles are continuous, and the heights of the vertexes 20 and 21 of the heat transfer surface are, for example, on the upper surface of the header portion 7. On the other hand, it is formed at the same height as the airflow rib A13, and the positions of the vertices 22 and 23 are formed at the same height as the back surface of the header 7, and the angle of each ridge and valley is It is formed so as to form 90 °.
[0108]
When the heat transfer plates A1 and B2 are alternately stacked, the peaks 20 of the peaks formed on the heat transfer plate A1 and the peaks 21 of the peaks formed on the heat transfer plate B are positioned on the same plane in the vertical direction. The vertices 22 of the valley formed on the heat transfer surface A1 and the vertices 23 of the valley formed on the heat transfer surface B2 are formed so as to be located on the same plane in the vertical direction.
[0109]
In the above-described configuration, the heat transfer surfaces constituting the air passage A3 and the heat transfer plates constituting the air passage B4 abut on the heat transfer surface A6, and the flat portion 5 which does not contribute to the heat transfer is not formed. , The heat transfer area increases, and the heat exchange efficiency improves.
[0110]
The dimensional values of the respective parts in the present embodiment are examples, and are not particularly limited to those values, and are appropriately designed in view of the performance of the heat exchanger such as airflow resistance, heat exchange efficiency, moldability, and the like. However, the same operation and effect can be obtained.
[0111]
(Example 3)
Next, a third embodiment of the present invention will be described with reference to FIGS.
[0112]
The same parts as those in the first and second embodiments are denoted by the same reference numerals, have the same function and effect, and detailed description is omitted.
[0113]
FIG. 8 is a schematic exploded perspective view of the heat transfer surface A of the heat exchanger used in the present embodiment, and FIG. 9 is a schematic cross-sectional view of the side surface and the air passage of the heat transfer surface A at the time of stacking.
[0114]
As shown in FIGS. 8 and 9, the heat transfer surface A6 of the heat transfer plate A1 and the heat transfer plate B2 has a wavy shape in which triangles are continuous, and a flat surface is formed on a part of the wavy portion, for example, the upper surface of seven wavy portions. The heat transfer plate A1 and the heat transfer plate B2 are intermittently provided with a plurality of, for example, four projections B24 on the flat portion 5 of the heat transfer plate A1 and the heat transfer plate B2. When alternately stacking the heat transfer plates B2, the protrusions B24 provided on the respective heat transfer plates have a positional relationship in which they do not overlap, and are formed at a height of 2.6 mm with respect to the peaks 21 and 22 of the peaks.
[0115]
In the above configuration, when the heat transfer plate A1 and the heat transfer plate B2 are alternately stacked, the upper surface of the projection B24 abuts on the back surface of the flat portion 5 formed on the heat transfer plate stacked above, so that heat transfer is performed. The air path height of the air path A3 and the air path B4 on the surface A6 can be maintained to reduce the ventilation resistance, and the heat transfer area can be reduced by intermittently contacting the upper surface of the projection B24 and the flat part 5. Can be reduced.
[0116]
In addition, the dimension value and the number of each part in the present embodiment are an example, and are not particularly limited to the values, and are appropriately designed in view of the performance of the heat exchanger such as ventilation resistance and heat exchange efficiency and the formability. In this case, the same operation and effect can be obtained.
[0117]
(Example 4)
Next, a fourth embodiment of the present invention will be described with reference to FIG.
[0118]
The same parts as those in the first, second and third embodiments are denoted by the same reference numerals, have the same operation and effect, and detailed description is omitted.
[0119]
FIG. 10 is a schematic cross-sectional view of the side and the heat transfer surface A at the time of lamination of the heat exchanger used in the present embodiment.
[0120]
As shown in FIG. 10, the heat transfer surface A6 of the heat transfer plate A1 and the heat transfer plate B2 has a wave shape in which triangles are continuous, and the heights of the vertexes 20 and 21 of the triangle are, for example, the upper surface of the header 7. The height of the air path rib A13 is 1.3 mm, which is half the height of the air path rib A13. When the heat transfer plates A1 and B2 are alternately laminated, the vertices 20, 21 of the triangular peaks formed on the adjacent heat transfer plates and the triangular valleys are formed. Are formed so that the vertices 22 and 23 of the above contact.
[0121]
In the above configuration, when the heat transfer plates A1 and B2 are alternately stacked, the vertices 20 and 21 of the triangular ridges and the vertices 22 and 23 of the triangular valleys formed on the adjacent heat transfer plates correspond to each other. By the contact, the air path A3 and the air path B4 are divided into a plurality of rhombic air paths on the heat transfer surface A6, and the fluid that has passed through one header portion 7 and flowed into the heat transfer surface A6 is transferred. The heat transfer surface A6 flows along the longitudinal direction of the triangle of the heat transfer surface A6 without moving in the waveform direction of the triangle and flows into the other header portion 7, so that the heat transfer surfaces of the heat transfer plate A1 and the heat transfer plate B2. A6 and the heat transfer surface B15 function effectively for heat transfer.
[0122]
The dimensional values of the respective parts in the present embodiment are examples, and are not particularly limited to those values, and are appropriately designed in view of the performance of the heat exchanger such as airflow resistance, heat exchange efficiency, moldability, and the like. However, the same operation and effect can be obtained.
[0123]
(Example 5)
Next, a fifth embodiment of the present invention will be described with reference to FIG.
[0124]
The same parts as those of the first, second, third and fourth embodiments are denoted by the same reference numerals, have the same operation and effect, and detailed description is omitted.
[0125]
FIG. 11 is a schematic cross-sectional view of the side and the heat transfer surface A at the time of lamination of the heat exchanger used in the present embodiment.
[0126]
As shown in FIG. 11, the heat transfer surface A6 of the heat transfer plate A1 and the heat transfer plate B2 has a wavy shape in which semicircular arcs are continuous, and the heat transfer surface A6 has an arc shape that is convex in the same direction as the convex direction of the outer peripheral rib A8. The height of the vertices 20 and 21 is, for example, 1.3 mm, which is half the height of the air path rib A13 with respect to the upper surface of the header portion 7, and is a circular arc that is convex in the direction opposite to the convex direction of the outer peripheral rib A8. The positions of the vertices 22 and 23 are formed so as to be 1.3 mm which is half the size of the air path rib A13 with respect to the back surface of the header portion 7, and when the heat transfer plates A1 and B2 are alternately stacked. The vertices 20 and 21 of the arcs convex in the same direction as the convex direction of the peripheral rib A8 formed on the adjacent heat transfer plate and the vertices 22 and 23 of the arc convex in the opposite direction to the convex direction of the peripheral rib A8 are formed. It is formed so as to abut.
[0127]
In the above configuration, when the heat transfer plates A1 and the heat transfer plates B2 are alternately stacked, the vertexes 20 and 21 of the arcs that are convex in the same direction as the convex direction of the outer peripheral ribs A8 formed on the adjacent heat transfer plates and the outer periphery. By contacting the vertices 22 and 23 of the arc that is convex in the direction opposite to the convex direction of the rib A8, the height of the air passages A3 and B4 on the heat transfer surface A6 can be maintained, and the airflow resistance can be reduced. The heat transfer area of the heat transfer surface A6 can be increased as compared with the case where the heat transfer surface A6 is formed into a wave shape in which semicircular arcs are continuous, thereby forming a wave shape linearly.
[0128]
The dimensional values of the respective parts in the present embodiment are examples, and are not particularly limited to those values, and are appropriately designed in view of the performance of the heat exchanger such as airflow resistance, heat exchange efficiency, moldability, and the like. However, the same operation and effect can be obtained.
[0129]
(Example 6)
Next, a sixth embodiment of the present invention will be described with reference to FIGS. 12, 13, 14, and 15. FIG.
[0130]
The same parts as those in the first, second, third, fourth and fifth embodiments are denoted by the same reference numerals, have the same operation and effect, and detailed description is omitted.
[0131]
FIG. 12 is a schematic exploded perspective view of the heat exchanger used in the present embodiment, FIG. 13 is a schematic cross-sectional view of the side surface and the air passage of the heat transfer surface A portion when the heat exchanger is stacked, and FIG. 15 is a schematic exploded perspective view showing a modified example of FIG.
[0132]
As shown in FIGS. 12 and 13, the heat transfer surface A6 of the heat transfer plate A1 and the heat transfer plate B2 has a wave shape in which triangles are continuous, and some of the wave-shaped portions, for example, the heat transfer surface A6 are continuous with the air path rib A13. It has a trapezoidal shape in which the flat portion 5 is formed only on the upper surface of the wavy portion, and the flat portion 5 has a width of 1 mm, which is equal to the upper surface of the airflow rib 13.
[0133]
In the above configuration, when the heat transfer plate A1 and the heat transfer plate B2 are alternately stacked, the upper surface of the flat portion 5 and the apexes 22 and 23 of the valleys of the triangular wavy portion are in contact with each other, so that the air path in the heat transfer surface A6 Since the air path height of A3 and the air path B4 is maintained, the airflow resistance can be reduced, and the flat section 5 and the tops 22 and 23 of the valleys come into contact with each other. The heat transfer area of A6 can be increased.
[0134]
In the present embodiment, the flat portion 5 is provided at the triangular peak portion, but may be provided at the triangular valley portion, or the flat portion 5 may be provided intermittently as shown in FIGS. The effect of (1) can be obtained.
[0135]
Further, the dimensional values and the numbers of the respective parts in the present embodiment are examples, and are not particularly limited to those values, and are appropriately designed in view of the performance aspects of the heat exchanger such as airflow resistance, heat exchange efficiency, molding workability, and the like. In this case, the same operation and effect can be obtained.
[0136]
(Example 7)
Next, a seventh embodiment of the present invention will be described with reference to FIGS.
[0137]
The same parts as those in the first, second, third, fourth, fifth and sixth embodiments are designated by the same reference numerals, have the same operation and effect, and detailed description is omitted.
[0138]
FIG. 16 is a schematic exploded perspective view of a heat exchanger used in the present embodiment, and FIG. 17 is an enlarged cross-sectional view of a main part thereof.
[0139]
As shown in FIG. 16, the wave-shaped heat transfer surface A6 of the heat transfer plate A1 and the heat transfer plate B2 is divided into a plurality of portions in the longitudinal direction by the divided portion 25. For example, the heat transfer plate A1 is transferred by the divided portions 25a and 25b. The surfaces A6a to A6c and the heat transfer plate B are each divided into three heat transfer surfaces A6d to F by divided portions 25c and 25d, and inclined portions 16 are provided at both ends in the longitudinal direction of each wave shape. The angle between the header 16 and the header 7 is formed at 7 °. As shown in FIG. 17, the split portions 25a to 25d face the rear surface of the header 7 in the direction opposite to the convex direction of the outer peripheral rib A8. A deformation suppressing rib 26 formed at a convex height of 0.5 mm is provided.
[0140]
In the above configuration, the fluid flowing from the heat transfer surface A6a to the heat transfer surface A6c on the upper surface of the heat transfer plate A1 flows toward the heat transfer surface A6b from the heat transfer surface A6a. However, since the heat transfer surface A is divided in the longitudinal direction, a new temperature boundary layer is formed by the inclined portion 16 formed on the upstream side of the heat transfer surface A6b, and heat transfer is promoted. Further, also when flowing from the heat transfer surface A6b to the heat transfer surface A6c and when flowing on the upper surface of the heat transfer plate B2, a new temperature boundary layer is similarly formed in the inclined portion 16 provided downstream of the divided portion. The heat transfer performance of the heat transfer surface A6 is improved.
[0141]
Further, by providing the deformation suppressing ribs 26 in the divided portions 25a to 25d, the deformation of the heat transfer plate A1 and the heat transfer plate B2 in the waveform direction is suppressed.
[0142]
In the present embodiment, the deformation suppressing rib 26 is provided so as to be convex in the direction opposite to the convex direction of the outer peripheral rib A8, but may be provided so as to be convex in the same direction as the convex direction of the outer peripheral rib A8. Similar functions and effects can be obtained.
[0143]
Further, the dimensional values and the numbers of the respective parts in the present embodiment are examples, and are not particularly limited to those values, and are appropriately designed in view of the performance aspects of the heat exchanger such as airflow resistance, heat exchange efficiency, molding workability, and the like. In this case, the same operation and effect can be obtained.
[0144]
(Example 8)
Next, an eighth embodiment of the present invention will be described with reference to FIGS.
[0145]
The same parts as those in the first, second, third, fourth, fifth, sixth and seventh embodiments are designated by the same reference numerals and have the same functions and effects, and detailed description is omitted.
[0146]
FIG. 18 is a schematic exploded perspective view of a heat exchanger used in this embodiment, and FIG. 19 is an enlarged view of a main part thereof.
[0147]
As shown in FIGS. 18 and 19, the wave shape formed on the adjacent heat transfer surface A6 via the divided portion is shifted in phase by approximately half the wavelength of the wave shape. The pitches of the trapezoids formed on the heat transfer surface A6a, the heat transfer surface A6c, and the heat transfer surface 6b are shifted by a half pitch, and in the heat transfer plate B2, the heat transfer surface A6d, the heat transfer surface A6f, and the heat transfer surface 6e are shifted. The pitch of the formed trapezoid is shifted by half a pitch.
[0148]
In the above configuration, as shown in FIG. 19, the fluid flowing on the upper surface of the heat transfer plate A1 from the direction of the arrow A flows into the heat transfer surface A6a along the inclined portion 16a into the divided portion 25a, and then flows to the heat transfer surface A6b. It collides with the formed inclined portion 16b, flows into the air path of the heat transfer surface A6b formed on the left and right sides of the inclined portion 16b (in the directions of arrows B and C in the figure), and similarly from the heat transfer surface A6b to the heat transfer surface A6c. Also flows into the inclined portion 16d, flows in the directions of arrows D and E, and the fluid flowing on the upper surface of the heat transfer plate B2 also flows in the same manner, and the heat transfer is further promoted by the collision with the inclined portion 16. Become.
[0149]
Further, the deformation of the heat transfer plate A1 and the heat transfer plate B2 in the waveform direction is suppressed by the divided portion 25.
[0150]
In addition, the dimension value and the number of each part in the present embodiment are an example, and are not particularly limited to the values, and are appropriately designed in view of the performance of the heat exchanger such as ventilation resistance and heat exchange efficiency and the formability. In this case, the same operation and effect can be obtained.
[0151]
(Example 9)
Next, a ninth embodiment of the present invention will be described with reference to FIGS.
[0152]
The same parts as those in the first, second, third, fourth, fifth, sixth, seventh and eighth embodiments are denoted by the same reference numerals, have the same operation and effect, and detailed description is omitted.
[0153]
FIG. 20 is a schematic exploded perspective view of a heat exchanger used in the present embodiment, FIG. 21 is a schematic perspective view when heat transfer plates are stacked, and FIG. 22 is a cross-section showing the contact between air path ribs A and B. It is an enlarged view.
[0154]
As shown in FIG. 20 and FIG. 21, the header ribs 7 of the heat transfer plates A1 and B2 are provided with air passage ribs A13 and B27, and the air passage rib A13 is in the same direction as the convex direction of the outer peripheral rib B9. Is formed in a hollow convex shape at a height of 1.3 mm with respect to the upper surface of the header portion 7, and the air path rib B27 has a height of 1.3 mm with respect to the back surface of the header section 7 in the direction opposite to the air path rib A13. As described above, the upper surface of the air passage rib A13 and the lower surface of the air passage rib B27 are formed to have the same width, for example, 1 mm, and have the same number, for example, five winds. When the heat transfer plate A1 and the heat transfer plate B2 are alternately laminated, the air passage rib A13 formed on the adjacent heat transfer plate is formed as shown in FIG. So that the lower surface of the air path rib B27 and the upper surface of It is formed.
[0155]
In the above configuration, since the air path ribs A13 and B27 provided on the heat transfer plate A1 and the heat transfer plate B2 intersect vertically at the respective header portions 7, the waveform direction of the heat transfer plate A1 and the heat transfer plate B2. Is suppressed.
[0156]
Further, when the heat transfer plates A1 and B2 are alternately stacked, the upper surface of the air passage rib A13 and the lower surface of the air passage rib B27 abut on the header portion 7 so that the air passage A3 and the air passage The air path height of B4 is maintained.
[0157]
In addition, the dimension value and the number of each part in the present embodiment are an example, and are not particularly limited to the values, and are appropriately designed in view of the performance of the heat exchanger such as ventilation resistance and heat exchange efficiency and the formability. In this case, the same operation and effect can be obtained.
[0158]
(Example 10)
Next, a tenth embodiment of the present invention will be described with reference to FIG.
[0159]
The same parts as those in the first, second, third, fourth, fifth, sixth, seventh, eighth and ninth embodiments are designated by the same reference numerals, have the same operation and effect, and detailed description is omitted.
[0160]
FIG. 23 is a schematic exploded perspective view of the heat exchanger used in this embodiment.
[0161]
As shown in FIG. 23, the heat transfer plate A1 and the heat transfer plate B2 are provided with an outer circumferential rib B9 continuously at both ends of one outer circumferential rib A8, and between the two ends of the other outer circumferential rib A8 and one end of the outer circumferential rib B9. Is provided with an air path entrance 19, and a heat transfer plate A1 and a heat transfer plate B2 are alternately laminated to form a U-shaped air path A3 and an air path B4, and an air path rib A13 formed in the header portion 7. The width of the air path inside the U-shaped air path having a short air path length is narrow so that the airflow resistance in each of the plurality of U-shaped air paths formed by the air path rib A13 is equal, A plurality of, for example, four, air passages are provided at irregular intervals so as to be continuous with the corrugated portion on which the heat transfer surface A6 is formed so that the outside air passage width having a long path length is widened.
[0162]
In the above configuration, since the U-shaped air path is formed, the air path entrances 19 of the air path A3 and the air path B4 are formed in the same direction with respect to the outer peripheral rib A8, so that the product body on which the heat exchanger is mounted. Therefore, the degree of freedom in designing the wind path is improved.
[0163]
Further, the width of the inside air path of the U-shaped air path having a short air path length is reduced so that the ventilation resistance in each air path of the U-shaped air path is equal, and the width of the outer air path having a long air path length is reduced. , The fluid A and the fluid B flowing from one of the air passage entrances 19 of the air passages A3 and B4 flow almost uniformly through the air passages A3 and B4, and the heat transfer surface A6 and the heat transfer surface The entire surface of the surface B15 functions effectively for heat transfer.
[0164]
In addition, the dimension value and the number of each part in the present embodiment are an example, and are not particularly limited to the values, and are appropriately designed in view of the performance of the heat exchanger such as ventilation resistance and heat exchange efficiency and the formability. In this case, the same operation and effect can be obtained.
[0165]
【The invention's effect】
(1) As is clear from the above embodiments, according to the present invention, the corrugated heat transfer surface A, the header portion, the outer peripheral rib A, the outer peripheral rib B, the air path rib A, the air path entrance / exit, the heat transfer surface B By simultaneously and integrally forming the heat transfer plate A and the heat transfer plate B using one sheet as a material so as to include the air path end surface, the projection A, and the air path end surface cover, the number of molding steps can be reduced. You can get a bowl.
[0166]
(2) In addition, inclined portions are provided at both ends in the longitudinal direction of the corrugated heat transfer surface A, and the angle between the inclined portion and the header portion is designed so that the fluid A and the fluid B are along the inner surface and the outer surface of the inclined portion. Thereby, a heat exchanger that can improve the heat exchange efficiency and reduce the ventilation resistance can be obtained.
[0167]
(3) In addition, when the cross-sectional shape of the heat transfer surface A is a corrugated shape in which substantially triangles are continuous, and the heat transfer plates A and the heat transfer plates B are alternately stacked, the adjacent heat transfer plates are not interposed via the partition member. By making the substantially triangular peaks and valleys face each other, it is possible to obtain a heat exchanger that can reduce the number of production steps and improve the heat exchange efficiency.
[0168]
(4) Also, at least one projection B is provided on the heat transfer plate A when the heat transfer plate A and the heat transfer plate B are alternately stacked on the substantially triangular crest of the heat transfer surface A. By providing B and the projections B provided on the heat transfer plate B in a positional relationship where they do not overlap, the wavy air path height of the heat transfer surface A is secured, and the airflow resistance increases due to the deformation of the air path shape. Can be obtained, and a heat exchanger that can reduce the ventilation resistance can be obtained.
[0169]
(5) Further, when the heat transfer plates A and B are alternately stacked, the substantially triangular peaks and valleys of the adjacent heat transfer plates are opposed to each other, so that the air paths A and Since the air passage B is divided into a plurality of substantially rhombic air passages, the fluid that has passed through one header portion and flowed into the heat transfer surface A does not move in the wave direction on the heat transfer surface A. A flows along the longitudinal direction of the wave shape of A, and flows into the other header portion, so that the heat transfer surfaces A and B of the heat transfer plates A and B function effectively for heat transfer, A heat exchanger that can improve exchange efficiency can be obtained.
[0170]
(6) Flat portions are provided at the tops of the substantially triangular peaks and valleys that form the wave shape of the heat transfer surface A, and when the heat transfer plates A and B are alternately stacked, the adjacent transfer portions The flat portion provided at the peak portion of the hot plate and the flat portion provided at the valley portion are in contact with each other, so that the wavy air path height of the heat transfer surface A is secured, and the air flow resistance caused by the deformation of the air path shape is ensured. Can be obtained, and a heat exchanger that can reduce the ventilation resistance can be obtained.
[0171]
(7) In addition, at least one or more peaks of a substantially triangular portion forming a wave shape of the heat transfer surface A and at least one or more valley portions of a substantially triangle forming a wave shape of the heat transfer surface A. When a flat portion is provided on the top portion and the heat transfer plates A and B are alternately stacked, the flat portion provided on the mountain portion of the adjacent heat transfer plate and the flat portion provided on the valley portion are in contact with each other. Thereby, the wavy air path height of the heat transfer surface A is ensured, the air flow resistance due to the deformation of the air path shape can be prevented from increasing, the air flow resistance can be reduced, and the area of the flat portion can be reduced. It is possible to obtain a heat exchanger capable of increasing the effective area of the heat transfer surface A that contributes to heat transfer and improving the heat exchange efficiency.
[0172]
(8) In addition, when a flat portion is provided intermittently at the tops of the substantially triangular peaks and valleys forming the corrugated shape of the heat transfer surface A, and the heat transfer plates A and B are alternately stacked, By the flat portions of the adjacent heat transfer plates abutting on each other, a corrugated air path height of the heat transfer surface A is secured, and an increase in air flow resistance due to deformation of the air path shape can be prevented, thereby reducing air flow resistance. Further, by providing the flat portion intermittently, it is possible to obtain a heat exchanger capable of increasing the effective area contributing to the heat transfer of the heat transfer surface A and improving the heat exchange efficiency.
[0173]
(9) Further, a flat portion is provided only on one of the substantially triangular peaks or valleys forming the corrugated shape of the heat transfer surface A, and when the heat transfer plates A and B are alternately stacked, they are adjacent to each other. The flat portion of the heat transfer plate and the top of the peak or the valley abut against each other to secure the wavy air path height of the heat transfer surface A, thereby preventing an increase in airflow resistance due to the deformation of the air path shape. The ventilation resistance can be reduced, and the flat portion and the top of the peak or the valley come into contact with each other, so that heat is exchanged also in the flat portion, and the effective area contributing to the heat transfer on the heat transfer surface A increases. As a result, a heat exchanger that can improve the heat exchange efficiency can be obtained.
[0174]
(10) Further, by making the cross-sectional shape of the heat transfer surface A into a wave shape in which a substantially semicircular curved surface is continuous, the area of the heat transfer surface A is increased with respect to the substantially triangular wave shape, and heat exchange is performed. A heat exchanger that can improve the efficiency can be obtained.
[0175]
(11) The heat transfer surface A is provided with a dividing portion for dividing the wave shape into a plurality of pieces in the longitudinal direction, and the split portion is substantially orthogonal to or oblique to the longitudinal direction of the wave shape formed on the heat transfer surface A. With such a configuration, the leading edge of the heat transfer surface A is increased, a new temperature boundary layer is formed, heat transfer is promoted, and the heat exchange efficiency can be improved. A heat exchanger capable of suppressing deformation of the heat transfer plate A and the heat transfer plate B in the wave direction can be obtained by forming the heat transfer plate A and the heat transfer plate B so as to be substantially orthogonal or substantially oblique to the longitudinal direction.
[0176]
(12) Further, the wave shape formed on the plurality of wave-shaped heat transfer surfaces A divided into a plurality in the longitudinal direction is substantially half wavelength with the wave shape formed on the adjacent heat transfer surface A via the division portion. By shifting the phase and causing the fluid to collide with the wave-shaped leading edge, heat transfer can be promoted and heat exchange efficiency can be improved, and deformation of the heat transfer plate in the wave direction can be suppressed. A heat exchanger can be obtained.
[0177]
(13) Further, by providing the deformation suppressing ribs at the divided portions that divide the heat transfer surface A formed into a wavy shape into a plurality of portions in the longitudinal direction, heat that can suppress the deformation of the heat transfer plate in the wave direction can be suppressed. An exchanger can be obtained.
[0178]
(14) In addition, inclined portions are provided at both ends in the longitudinal direction of each of the plurality of divided heat transfer surfaces A, and the angle between the inclined portion and the header portion is formed by the fluid A and the fluid B on the inner surface of the inclined portion. By designing the heat exchanger along the outer surface, heat exchange is performed between the fluid A and the fluid B even in the inclined portion, the heat exchange efficiency is improved, and a heat exchanger that can reduce the ventilation resistance can be obtained.
[0179]
(15) Further, the width of the outer peripheral rib A formed on the heat transfer plate A is made smaller than the width of the outer peripheral rib A formed on the heat transfer plate B, and the outer peripheral rib formed on the heat transfer plate A is formed. The convex height of A is set to be larger than the convex height of the peripheral rib A formed on the heat transfer plate B, and the wave-shaped heat transfer surface A formed on the heat transfer plate A and the heat transfer plate A are formed on the heat transfer plate A. When a flat portion is provided on the heat transfer surface A adjacent to the outer circumferential rib A and the heat transfer plate A and the heat transfer plate B are alternately laminated, the upper surface of the outer circumferential rib A formed on the heat transfer plate A The upper surface of the outer peripheral rib A formed on the heat transfer plate B is in contact with the rear surface of the flat portion provided on the heat transfer plate A, so that the end of the heat exchanger ends. The heat exchanger which can improve the intensity | strength of the lamination direction of can be obtained.
[0180]
(16) Further, the air path rib A is formed on the corrugated heat transfer surface A and is formed continuously with a waveform protruding in the same direction as the convex direction of the air path rib A with respect to the header portion. The number is provided less than the number of waveforms that protrude in the same direction as the convex direction of the air path rib A with respect to the header portion, and the fluid A and the fluid B flow almost uniformly through the air path A and the air path B, It is possible to obtain a heat exchanger that can reduce the ventilation resistance and improve the heat exchange efficiency.
[0181]
(17) A plurality of air path ribs A and a plurality of air path ribs B formed in a hollow convex shape in a direction opposite to the convex direction of the air path ribs A are provided in the header portion substantially in parallel with the air path entrance and exit. And the air passage rib B intersect at the top and bottom in the header portion, so that it is possible to obtain a heat exchanger capable of suppressing deformation of the heat transfer surface A of the heat transfer plate A and the heat transfer surface A in the wave direction. .
[0182]
(18) Further, an outer circumferential rib B is provided continuously at both ends of one outer circumferential rib A, and an air path entrance is provided between both ends of the other outer circumferential rib A and one end of the outer circumferential rib B. And the heat transfer plate B are alternately laminated to form a substantially U-shaped air path A and an air path B alternately, and the entrances and exits of the air path A and the air path B are formed in the same direction with respect to the outer circumferential rib A. Thus, a heat exchanger capable of improving the degree of freedom in designing the main body can be obtained.
[0183]
(19) Further, the air path ribs A are unequal so that the air path widths located inside the air paths A and B formed in a substantially U shape are narrow and the air path widths located outside are wide. By forming at intervals, equalizing the ventilation resistance of each of the plurality of air passages formed in the air passage A and the air passage B, and flowing the fluid A and the fluid B almost uniformly through the air passage A and the air passage B, Heat exchange air that can improve the heat exchange efficiency can be obtained.
[Brief description of the drawings]
FIG. 1 is a schematic exploded perspective view of a heat exchanger according to a first embodiment of the present invention.
FIG. 2 is a schematic perspective view of the laminated state.
FIG. 3 is a schematic cross-sectional view of an air passage of a side surface and a heat transfer surface A in the stacked state.
FIG. 4 is a schematic cross-sectional view of an airway entrance / exit portion in the same laminated state.
FIG. 5 is a schematic cross-sectional view of a corner portion where the air passage entrance and exit in the same laminated state are adjacent to each other.
FIG. 6 is a top perspective view of a corner portion where the air passage entrances and exits in the laminated state are adjacent to each other.
FIG. 7 is a schematic cross-sectional view of a side surface of a heat exchanger according to a second embodiment of the present invention and an air path of a heat transfer surface A portion.
FIG. 8 is a schematic exploded perspective view of a heat transfer surface A of a heat exchanger according to a third embodiment of the present invention.
FIG. 9 is a schematic cross-sectional view of an air passage of a side surface and a heat transfer surface A in the stacked state.
FIG. 10 is a schematic cross-sectional view of a side surface of a heat exchanger according to a fourth embodiment of the present invention and an air path of a heat transfer surface A portion.
FIG. 11 is a schematic cross-sectional view of a side surface of a heat exchanger according to a fifth embodiment of the present invention and an air path of a heat transfer surface A portion.
FIG. 12 is a schematic exploded perspective view of a heat exchanger according to a sixth embodiment of the present invention.
FIG. 13 is a schematic cross-sectional view of an air passage of a side surface and a heat transfer surface A in the stacked state.
FIG. 14 is a schematic exploded perspective view showing a modification of the heat transfer surface A.
FIG. 15 is an enlarged view of a main part of a modification of the heat transfer surface A.
FIG. 16 is a schematic exploded perspective view of a heat exchanger according to a seventh embodiment of the present invention.
FIG. 17 is an enlarged cross-sectional view of the main part.
FIG. 18 is a schematic exploded perspective view of a heat exchanger according to an eighth embodiment of the present invention.
FIG. 19 is an enlarged view of the main part.
FIG. 20 is a schematic exploded perspective view of a heat exchanger according to a ninth embodiment of the present invention.
FIG. 21 is a schematic perspective view of the same laminated state.
FIG. 22 is an enlarged cross-sectional view showing the contact between the air path ribs A and B in the same laminated state.
FIG. 23 is a schematic exploded perspective view of a heat exchanger according to a tenth embodiment of the present invention.
FIG. 24 is a schematic perspective view of a conventional heat exchanger when stacked.
FIG. 25 is a schematic perspective view of a heat exchange member of the heat exchanger.
FIG. 26 is an enlarged view of a sealing member of the heat exchanger.
FIG. 27 is an enlarged view of a sealing structure of the heat exchanger.
FIG. 28 is a sectional view showing an example of a corrugated portion of the heat exchanger.
FIG. 29 is a sectional view showing an example of a corrugated portion of the heat exchanger.
[Explanation of symbols]
1 Heat transfer plate A
2 Heat transfer plate B
3 Airway A
4 Airway B
5 flat part
6 Heat transfer surface A
6a Heat transfer surface A
6b Heat transfer surface A
6c Heat transfer surface A
6d Heat transfer surface A
6e Heat transfer surface A
6f Heat transfer surface A
7 Header
8 Outer rib A
9 Outer rib B
10 Airway opening
11 Airway end face cover
12 Wind end
13 Airway rib A
14 Projection A
15 Heat transfer surface B
16 Inclined part
16a Inclined part
16b Inclined part
16c Inclined part
16d slope
17 Corner support projection
18 flat part
19 Airway entrance
20 Top of heat transfer plate A
21 Top of heat transfer plate B
22 Top of valley of heat transfer plate A
23 Top of valley of heat transfer plate B
24 Projection B
25 Division
25a division
25b division
25c division
25d division
26 Deformation suppression rib
27 Airway Rib B

Claims (19)

The heat transfer plate A includes a heat transfer plate A and a heat transfer plate B. The heat transfer plate A includes a wave-shaped heat transfer surface A and header portions at both ends in the longitudinal direction of the waveform of the heat transfer surface A. A pair of outer peripheral edges that are substantially parallel to the longitudinal direction of the outer peripheral rib A formed in a hollow convex shape at a pair of outer peripheral edges, and the header portion is provided with a convex direction of the outer peripheral rib A at a position substantially opposing a part of the outer peripheral edge. A plurality of outer peripheral ribs B formed in a hollow convex shape in the same direction and a plurality of air path ribs A formed in a hollow convex shape in the same direction as the convex direction of the outer peripheral rib A at substantially equal intervals substantially in parallel with the outer peripheral rib B; One end of the outer peripheral rib A is formed continuously with one end of the outer peripheral rib B, and an air passage is provided between the other end of the outer peripheral rib A and the other end of the outer peripheral rib B on the outer peripheral edge of the header portion. An entrance / exit is formed, and a plurality of air passages and a heat transfer surface B are formed in the header portion by the air passage rib A. An air path end face is provided at an entrance, and the air path end face is provided by bending the header portion in a direction opposite to a convex direction of the air path rib A, and is on an extension of the plurality of air path ribs A. A plurality of hollow convex protrusions A are provided near the end face in the same direction as the convex direction of the air path rib A, and the central portion of the outer side surface of the outer peripheral rib B is folded back to the same surface as the header portion, At both ends of the outer side surface of the outer peripheral rib B, an air path end face cover folded back up to the same position as the air path end face is provided, and the heat transfer plate B has a mirror image relationship with the heat transfer plate A, and The heat transfer plate A and the heat transfer plate B are alternately stacked so that the outer circumferential rib A of the heat plate A and the outer circumferential rib A of the heat transfer plate B overlap each other, and the heat transfer plate A and the heat transfer plate The air path A and the air path B are alternately formed by laminating the plates B, and the heat transfer plate A and the heat transfer When B is alternately stacked, the upper surfaces of the air path ribs A, the protrusions A, and the outer peripheral ribs B are in contact with the heat transfer plate stacked thereon, and the outer side surfaces of the protrusions A are located above the protrusions A. An outer side surface of the outer peripheral rib B provided on a heat transfer plate that is in contact with an inner side surface of the outer peripheral rib B provided on the heat transfer plate laminated on the heat transfer plate and is located below the air path end surface. And the side surfaces of the outer peripheral ribs A provided on the heat transfer plate A and the heat transfer plate B contact each other, and the air path end face cover and the heat transfer plate located below the air path end face cover A heat exchanger in which end faces of the outer peripheral ribs A and the outer peripheral ribs B provided on the heat transfer plate A and the heat transfer plate B are each made of a single sheet. Hot surface A, the header portion, the outer peripheral rib A, the outer peripheral rib B, the air path A heat exchanger, wherein a heat transfer surface B, the heat transfer surface B, the air path end face, the plurality of protrusions A, and the air path end face cover are formed simultaneously and integrally. At both ends in the longitudinal direction of the wave-shaped heat transfer surface A, an inclined portion is provided which is inclined from the vertex of the waveform to the header portion. The angle between the inclined portion and the header portion is such that the fluid A and the fluid B are formed on the inner surface of the inclined portion. The heat exchanger according to claim 1, wherein the angle is designed to be along the outer surface. The wave shape of the heat transfer surface A is a wave shape in which substantially triangular shapes are continuous, and when the heat transfer plates A and the heat transfer plates B are alternately laminated, the heat transfer surface A formed on the adjacent heat transfer plate is substantially shaped. The triangular ridges face each other, and the substantially triangular valleys of the heat transfer surface A formed on the heat transfer plate A and the heat transfer plate B face each other. Heat exchanger. At least one protrusion B is provided on a substantially triangular crest of the heat transfer surface A formed on the heat transfer plate A and the heat transfer plate B, and the protrusion B connects the heat transfer plate A and the heat transfer plate B. When alternately stacking, the protrusions B provided on the heat transfer plate A and the protrusions B provided on the heat transfer plate B are provided in a positional relationship such that they do not overlap, and the upper surface of the protrusion B is positioned above the protrusion B. The heat exchanger according to claim 3, wherein the heat exchanger contacts the rear surface of the substantially triangular crest of the heat transfer surface A formed on the heat transfer plate. The heat transfer plate (A) and the heat transfer plate (B) are alternately stacked, and the substantially triangular peaks and valleys of the heat transfer surface (A) formed on adjacent heat transfer plates face each other. Or the heat exchanger according to 2. When flat portions are provided at the tops of the substantially triangular peaks and valleys forming the wave shape of the heat transfer surface A, and when the heat transfer plates A and B are alternately stacked, the peaks of the adjacent heat transfer plates are provided. 6. The heat exchanger according to claim 5, wherein the flat portion provided in the first portion and the flat portion provided in the valley contact each other. Flat portions are formed at the tops of at least one or more peaks of a substantially triangular shape that forms the wave shape of the heat transfer surface A and at the tops of at least one or more troughs of the substantially triangle that form the wave shape of the heat transfer surface A. When the heat transfer plate A and the heat transfer plate B are alternately stacked, the flat portion provided at the peak portion of the adjacent heat transfer plate and the flat portion provided at the valley portion are in contact with each other. Item 6. The heat exchanger according to Item 5. 8. The heat exchanger according to claim 6, wherein a flat portion is provided intermittently at the top of the substantially triangular peaks and valleys forming the corrugated shape of the heat transfer surface A. 9. A flat portion is provided on one of the tops of substantially triangular peaks or valleys forming the corrugations of the heat transfer surfaces A of the heat transfer plates A and B. The heat exchanger as described. 6. The heat exchanger according to claim 3, wherein the wave shape of the heat transfer surface A is a wave shape in which a substantially semicircular curved surface is continuous. The heat transfer plate A and the heat transfer plate B each include a dividing portion that divides the wave-shaped heat transfer surface A into a plurality of pieces in the longitudinal direction. The heat exchanger according to any one of claims 1, 2, 3, 4, 5, 6, 7, 8, 9 and 10, wherein the heat exchanger is formed so as to be substantially orthogonal to or oblique to the direction. The wave shape formed on the heat transfer surface A having a plurality of wave shapes divided into a plurality in the longitudinal direction is substantially out of phase with the wave shape formed on the adjacent heat transfer surface A via the split portion. The heat exchanger according to claim 11, wherein: The heat exchanger according to claim 11 or 12, wherein a deformation suppressing rib is provided at a divided portion that divides the heat transfer surface A formed into a wavy shape into a plurality of portions in the longitudinal direction. At both ends in the longitudinal direction of each of the plurality of wave-shaped heat transfer surfaces A, an inclined portion is provided which is inclined from a vertex of a waveform to a divided portion, and an angle formed by the inclined portion and the divided portion is the fluid A and the fluid 14. The heat exchanger according to claim 11, 12 or 13, wherein the fluid B has an angle designed to be along the inner surface and the outer surface of the inclined portion. The width dimension of the outer peripheral rib A formed on the heat transfer plate A is smaller than the width dimension of the outer peripheral rib A formed on the heat transfer plate B, and the protrusion of the outer peripheral rib A formed on the heat transfer plate A is formed. The height is set to be higher than the convex height of the outer peripheral rib A formed on the heat transfer plate B, and the wavy heat transfer surface A formed on the heat transfer plate A and the heat transfer plate A are formed on the heat transfer plate A. When the heat transfer plate A and the heat transfer plate B are alternately stacked on the heat transfer surface A adjacent to the heat transfer plate A, the outer peripheral rib A is formed on the heat transfer plate A. The upper surface is in contact with the back surface of the outer peripheral rib A formed on the heat transfer plate B, and the upper surface of the outer peripheral rib A formed on the heat transfer plate B The method according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, or 14, wherein the abutment is in contact with the back surface. Heat exchanger. The plurality of air path ribs A provided on the header portions of the heat transfer plate A and the heat transfer plate B are formed on the corrugated heat transfer surface A and protrude from the header portion in the same direction as the convex direction of the air path ribs A. And the number of the air path ribs A is smaller than the number of waveforms protruding in the same direction as the convex direction of the air path ribs A with respect to the header section. The heat exchanger according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, or 15. The heat transfer plate A and the heat transfer plate B are provided with a plurality of air path ribs A and a plurality of air path ribs B formed in the header portion in a hollow convex shape in a direction opposite to the convex direction of the air path ribs A substantially in parallel with the air path entrance and exit. When the heat transfer plate A and the heat transfer plate B are alternately stacked, the upper surface of the air passage rib A formed on the adjacent heat transfer plate and the lower surface of the air passage rib B are in contact with each other. The heat exchanger according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, or 16. The heat transfer plate A and the heat transfer plate B are provided with an outer circumferential rib B continuously at both ends of one outer circumferential rib A of a pair of opposed outer circumferential ribs A, and both ends of the other outer circumferential rib A and one end of the outer circumferential rib B are provided. The outer circumferential rib A of the heat transfer plate A and the outer circumferential rib A of the heat transfer plate B overlap each other, and the heat transfer plate is located above the outer circumferential rib B of the heat transfer plate A. B, the heat transfer plate A and the heat transfer plate B are alternately arranged so that the heat transfer plate A has an air passage entrance above the outer peripheral rib B of the heat transfer plate B. The heat transfer plate A and the heat transfer plate B are stacked, and substantially U-shaped air passages A and B are alternately formed by stacking the heat transfer plates A and B. The heat exchanger according to 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, or 17. A plurality of air path ribs are provided at irregular intervals in the header portion so that the width of the air path located inside the air path A and the air path B formed in a substantially U-shape is narrow and the width of the air path located outside is wide. The heat exchanger according to claim 18, wherein A is formed.

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