WO2013132679A1

WO2013132679A1 - Heat exchanger and refrigeration cycle device

Info

Publication number: WO2013132679A1
Application number: PCT/JP2012/072132
Authority: WO
Inventors: 宗史池田; 寿守務吉村; 瑞朗酒井; 裕之森本; 傑鳩村; 進一内野
Original assignee: 三菱電機株式会社
Priority date: 2012-03-07
Filing date: 2012-08-31
Publication date: 2013-09-12
Also published as: JPWO2013132679A1; JP5784215B2; EP2840342A1; EP2840342A4; EP2840342B1

Abstract

An objective of the present invention is to obtain a heat exchanger with which, even when connecting a plurality of fluid flow paths, to allow minimizing pressure loss, to implement uniform distribution among each flow path, and to allow alleviating performance declines in the heat exchanger. A heat exchanger (10a) comprises: a plurality of rows of first fluid flow paths (1) which pass through a heat transfer block (4); a plurality of rows of second fluid flow paths (2a) which are formed in parallel with the first fluid flow paths (1) and which pass through the heat transfer block (4); and a lateral hole (3a) which is formed in the heat transfer block (4) and which communicates with all of the second fluid flow paths (2a). The lateral hole (3a) is perpendicular to the second fluid flow paths (2a), and, with the flow path cross-section area of the second fluid flow paths designated A, the equivalent diameter thereof designated d, and the length thereof designated L, as well as the flow path cross-section area of the lateral hole designated A_y, the equivalent diameter thereof designated d_y, and the equivalent length designated L_y, is formed in a diameter and in numbers such that L/A²d > L_y/A_y ²d_y. The lateral hole connects all of the second fluid flow paths, and does not protrude into the portion of the heat transfer block between the first fluid flow paths and the second fluid flow paths which are adjacent thereto.

Description

Heat exchanger and refrigeration cycle equipment

The present invention relates to a heat exchanger and a refrigeration cycle apparatus, and in particular, a heat exchanger having a first fluid channel through which a high-temperature fluid flows and a second fluid channel through which a low-temperature fluid flows in a heat transfer block, and the heat exchanger. Relates to the refrigeration cycle apparatus.

Conventionally, a heat pump refrigeration / air-conditioning system including a vapor compression refrigeration circuit has been used. A heat exchanger for exchanging heat between the first fluid and the second fluid is provided in the refrigeration circuit.
In the heat exchanger, the first fluid channel through which the first fluid flows and the second fluid channel through which the second fluid flows are arranged substantially in parallel in the same block (solid), and the respective fluids are in the same direction with each other. (Hereinafter referred to as “parallel” or “parallel flow”) or in opposite directions (hereinafter referred to as “opposite” or “opposite flow”), and heat exchange is performed between the two.
For example, the first fluid is “water” and the second fluid is “R410a”, and heat is exchanged between the low-temperature and low-pressure water and the high-temperature and high-pressure R410a to heat the water (at this time, R410a is Cooled).
As one of means for improving the performance and downsizing of the heat exchanger, the first fluid channel or the second fluid channel has a small diameter. By reducing the diameter, the heat transfer area per unit volume of the heat exchanger can be increased, and high heat transfer can be realized.
In addition, the first fluid channel and the second fluid are not included in the same block (solid), only one channel is formed in the block, and the block is disposed in the other channel. A tube for heat exchange in which a flow path formed in a block is reduced in diameter is formed by integrally extruding a row of a plurality of flow paths through which a fluid flows in a flat cross section (for example, , See Patent Document 1).

JP 2000-234881 (page 3-4, FIG. 2)

In the invention disclosed in Patent Document 1, since the block is arranged in the other channel, the block is located on the upstream side of the other channel and the downstream side of the other channel. Since there is a temperature difference (difference in heat exchange amount) with the flow path in the block, a horizontal hole is provided to communicate the flow path in the block located on the downstream side from the flow path in the block located on the upstream side, The difference in fluid temperature between the flow paths in the block is reduced.
For this reason, in order to distribute and mix a fluid into each flow path, it is necessary to open a horizontal hole. Since the diameter of the horizontal hole is limited by the height of the flow path, there is a problem that the cross-sectional area of the flow path is reduced in the horizontal hole 3a, and the pressure loss is increased by repeatedly expanding and reducing the flow path in the block. It was. That is, since the flow path cross-sectional areas are different (the header cross-sectional area is small), the flow velocity of the fluid increases in the header portion, so that the pressure loss increases, and the pressure loss of the heat exchanger increases due to repetition thereof.
When the invention disclosed in Patent Document 1 is applied to a heat exchanger having a first fluid channel and a second fluid in the same block (solid), there is a similar problem. In particular, in the invention disclosed in Patent Document 1, the combination of the first fluid channel and the second fluid channel is one stage, but when the heat exchanger is configured in multiple stages, the one stage is changed to the other. Since the fluid flows into the stage, the number of times of passing through the header portion increases. For this reason, as a result, the flow path cross-sectional area repeatedly expands and contracts, and the pressure loss of the heat exchanger increases.
In addition, when distributing the fluid to each flow path, the ratio of the flow rate of gas and liquid for each flow path in the condition of the fluid flowing into the heat exchanger, particularly in the gas-liquid two-phase state where gas and liquid are mixed, is Different or non-uniform distribution occurs and the performance of the heat exchanger deteriorates.

The present invention solves the above problem, and even if a plurality of fluid flow paths are communicated with each other, pressure loss can be reduced, and even distribution to each flow path can be realized. It is possible to obtain a heat exchanger capable of suppressing performance degradation and a refrigeration cycle apparatus equipped with the heat exchanger.

A heat exchanger according to the present invention is formed in parallel to each other on a first surface, which is a plane in a heat transfer block, and a plurality of rows of first fluid flow paths penetrating the heat transfer block, and in the heat transfer block A second surface parallel to the first surface is formed in parallel to the first fluid flow path, a plurality of rows of second fluid flow paths penetrating the heat transfer block, and formed in the heat transfer block, A horizontal hole communicating with all of the second fluid flow path, wherein the horizontal hole is perpendicular to the second fluid flow path, and the horizontal hole is a flow path cross-sectional area A of the second fluid flow path, an equivalent diameter d. , length L, a flow path cross-sectional area _{a y} of the lateral hole, the equivalent diameter _{d y,} when the equivalent length _{L y,} in ^{_{_{L / a 2 d> L y}}} / a y 2 d y become such diameter and number The lateral hole communicates with the second fluid flow path, and the second fluid flow path is adjacent to the first fluid flow path. Characterized in that it does not protrude to the heat block portion.

Since the heat exchanger according to the present invention has the above-described configuration, the cross-sectional area of the horizontal hole can be optimally designed, so that pressure loss can be suppressed, and performance degradation of the heat exchanger can be suppressed by even distribution. be able to.

Sectional drawing explaining the A type heat exchanger which concerns on Embodiment 1 of this invention. Sectional drawing explaining the B type and C type heat exchanger which concern on Embodiment 1 of this invention, respectively. Sectional drawing explaining the D type heat exchanger which concerns on Embodiment 2 of this invention. Sectional drawing explaining the E type heat exchanger which concerns on Embodiment 2 of this invention. Sectional drawing explaining each F type heat exchanger which concerns on Embodiment 2 of invention. Sectional drawing explaining the H type and I type heat exchanger which concern on Embodiment 3 of this invention. Sectional drawing explaining the J type heat exchanger which concerns on Embodiment 4 of this invention. Sectional drawing explaining the K type, L type, and M type heat exchanger which concern on Embodiment 5 of this invention. The block diagram of the apparatus which shows the heat pump type heating system explaining the refrigerating-cycle apparatus which concerns on Embodiment 7 of this invention. The block diagram of the apparatus which shows the heat pump type hot-water supply system explaining the refrigerating-cycle apparatus which concerns on Embodiment 8 of this invention. Baker diagram referred to for explaining a refrigeration cycle apparatus according to Embodiment 6 of the present invention.

[Embodiment 1]
1 and 2 schematically illustrate a heat exchanger according to Embodiment 1 of the present invention. FIG. 1A is a cross-sectional view of a cross section perpendicular to the longitudinal direction of the A type, and FIG. 1 (b) is a cross-sectional view of a cross section parallel to the longitudinal direction of the A type, FIG. 2 (a) is a cross sectional view of the B type, and FIG. 2 (b) is a cross section of the cross section of the B type parallel to the longitudinal direction. 2C is a cross-sectional view of the C type, and FIG. 2D is a cross-sectional view of a cross section parallel to the longitudinal direction of the C type. In each drawing, the same or corresponding parts are denoted by the same reference numerals (numeric parts), and a part of the description is omitted. In addition, in the description of common contents, reference numerals (a, b...) May be omitted (the same applies to Embodiments 2 to 5).

(A type)
1A and 1B, an A type heat exchanger 10a includes a plurality of (for example, four) first fluid channels 1 and a first fluid channel arranged in a heat transfer block 4. 1 and a plurality of (for example, 45) second fluid flow paths 2a arranged in parallel with each other in a flowing direction, and perpendicular to the second fluid flow paths 2a, and all the second fluid flow paths 2a communicate with each other. And one row of horizontal holes 3a formed to do so.

(First fluid channel, second fluid channel)
The first fluid channel 1 is disposed on a first surface 41 that is a flat surface, a plurality of rows are disposed in parallel to each other, and has a circular cross section.
Further, the second fluid flow path 2a is parallel to the first fluid flow path 1 and has a plurality of rows (for example, 15 rows) arranged in the second surface 42a which is a plane substantially parallel to the first surface 41. Two fluid channels 21a, a plurality of rows (for example, 15 rows) of second fluid channels 21b arranged on a second surface 42b substantially parallel to the first surface 41, and a second surface substantially parallel to the first surface 41 A plurality of rows (for example, 15 rows) of second fluid flow paths 21c arranged in 42c are collectively referred to. That is, the second fluid flow paths 2a are arranged in 15 rows each in three layers and have a rectangular cross section.
The axial direction of the first fluid channel 1 and the second fluid channel 2a is referred to as the “longitudinal direction”.
Further, the above description shows that the first fluid channel 1 has a circular cross-sectional shape and the second fluid channel 2a has a rectangular cross-sectional shape, but the present invention is not limited to this. The shape can be arbitrarily set.

(Horizontal hole)
The horizontal hole 3a is perpendicular to the second fluid channel and communicates a plurality of rows (for example, 45 rows) of the second fluid channels with each other, but the second fluid channel adjacent to the first fluid channel 1 It does not protrude into the heat transfer block 4 formed between 21a. Further, the pressure loss can be reduced by determining the diameter and number of the horizontal holes 3a according to the mass velocity of the fluid flowing in, the length of the horizontal holes, the size and the number of the second fluid flow paths. . When the second fluid passes in the longitudinal direction of the heat transfer block, the refrigerant density ρ, flow velocity v (“v = G / ρ × 1 / A”, G: mass velocity, A: flow path cross-sectional area), pressure loss When the coefficient λ, the equivalent diameter d of the second fluid flow path (“d = 4 S / L ′”, S: total cross-sectional area, L ′: wet wetting length), and the length L of the second fluid flow path, the pressure loss ΔP is "ΔP = λ × L / d × v 2/2 × ρ ".
Passes through the likewise transverse hole 3a, the pressure loss [Delta] P _y is the flow velocity _{v y} in the transverse hole 3a part, the _{_{_{"ΔP y = λ y × L y}}} / d y × v y 2/2 × ρ ". It is desirable to select the diameter and the number of the horizontal holes so that the pressure loss in the horizontal hole 3a portion is smaller than the pressure loss generated when passing in the longitudinal direction of the heat transfer block. It is desirable to select the diameter and the number of the horizontal holes 3a that satisfy “ΔP> ΔP _y ”, that is, “L / A ² d> L _y / A _y ² d _y ”.
As a specific example, when the second fluid flow path as shown in FIG. 1 is arranged in three layers, 15 rows with dimensions of 1 mm × 1 mm, the length of the heat transfer block is 300 mm, and the length of the lateral hole is 25 mm, The diameter of the side hole 3a satisfying “L / A ² d = 0.3 / (4.5 × 10 ⁻⁵ ) ² × 0.001 = 1.48 × 10 ¹¹ > L _y / A _y ² d _y ” and It is preferable to use a number, and “d _y > 0.003”, that is, a lateral hole 3 a having a diameter of 3 mm or more is desirable. In addition, when it is a flow-path cross-sectional area other than said range, since the pressure loss in a side hole part increases and causes the performance deterioration of a heat exchanger, it is unpreferable.
The horizontal hole 3a is drilled from one side surface 44 of the heat transfer block 4 by machining (drilling) or plastic working (punching). However, the present invention does not limit the formation method. Absent.

(Function and effect)
In the heat exchanger 10a configured as described above, the following operational effects are obtained.
Since the horizontal hole 3a having a channel cross-sectional area within the above range is larger than the horizontal hole having a diameter of one layer as in the conventional heat exchanger (see Patent Document 1), the fluid passes through the heat exchanger 10a. In doing so, the influence of the enlargement / reduction of the flow path in the horizontal hole 3a is reduced. That is, since the horizontal hole 3a functions as a header portion, the pressure loss in the horizontal hole 3a, that is, the pressure loss in the heat exchanger 10a is reduced.
Therefore, the heat transfer area of the second fluid channel 2a is increased by configuring the second fluid channel 2a so as to extend over a plurality of layers in order to increase the diameter Da of the lateral hole 3a. Accordingly, it is possible to improve the heat exchange performance.
In particular, when the heat exchanger is configured in multiple stages, there is a flow of the second fluid from one stage to the other, and the number of times of passing through the side hole 3a (corresponding to the header portion) increases. Although the flow path cross-sectional area repeatedly expands and contracts, in the heat exchanger 10a, the flow path cross-sectional area of the horizontal hole 3a is large, so the effect of reducing the pressure loss becomes remarkable.
Compared with the case where the thickness of the heat transfer block is increased so that the horizontal hole 3a having the diameter Da of the channel cross-sectional area within the above range has the same diameter in one layer as in the conventional heat exchanger, Since the distance with the 1 fluid flow path 1 can be shortened, it becomes possible to improve heat exchange performance.
The horizontal hole 3a having the channel cross-sectional area diameter Da within the above range does not protrude from the heat transfer block 4 formed between the first fluid channel 1 and the second fluid channel 21a. Therefore, since the distance between the first fluid channel 1 and the second fluid channel 21a can be shortened, the heat exchange performance can be improved.
Further, the lateral hole 3 a is configured not to protrude from the second fluid flow path 21 c located farthest from the first fluid flow path 1 to the portion of the heat transfer block 4 outside. That is, the height of the horizontal hole 3a is set to fall within the range from the lowest layer to the uppermost layer of the second fluid channel 2a with respect to the second fluid channel 2a arranged to form a plurality of layers. By doing in this way, the thickness of the heat-transfer block 4 can be made thin. Further, when the first fluid channel 1 layer, the second fluid channel 2a layer, and the first fluid channel 1 layer are stacked, the layer of the second fluid channel 2a sandwiched between them is The heat exchange performance can be improved because it can be disposed close to the upper and lower layers of the first fluid flow path 1.
In addition, although the formation method of the heat-transfer block 4 is not limited, For example, if it forms by integral extrusion processing, increase / decrease in the number of the lines of the 1st fluid flow path 1, the number of the 1st surfaces 41, or 2nd fluid. Since it is easy to increase or decrease the number of rows of the flow paths and the number of the second surfaces 42, the flow path cross-sectional area of the horizontal hole 3a can be optimally designed.

In the heat exchanger 10a, on one side surface 44 of the heat transfer block 4, a pipe joint (for example, a tube, not shown) for pipe connection is attached to the lateral hole 3a by brazing. Therefore, the heat exchanger 10a can be used by connecting a pipe of a system (for example, a hot water supply system) to the pipe joint. At this time, both ends in the longitudinal direction of the second fluid flow path 2a are closed.
Further, a lid may be installed in the horizontal hole 3a on the one side surface 44 of the heat transfer block 4 to close the opening. At this time, both ends of the second fluid flow path 2a in the longitudinal direction are connected to piping of a system (for example, a hot water supply system) (directly via a pipe joint or indirectly via an external header section). Connected).

The fluid flowing through the first fluid channel 1 (first fluid) and the fluid flowing through the second fluid channel 2a (second fluid) are not limited, and tap water, distilled water, and brine are used as the first fluid. In addition to R410a, natural refrigerants such as chlorofluorocarbon refrigerants and hydrocarbons, and mixtures thereof may be used as the second fluid.
Furthermore, the flow direction of the fluid flowing through the first fluid flow path 1 and the flow direction of the fluid flowing through the second fluid flow path 2a may be parallel or opposed.

(B type)
2 (a) and 2 (b), the B type heat exchanger 10b includes four rows of the first fluid flow paths 1 arranged in the heat transfer block 4, and 15 rows of 5 layers (75 rows in total). The second fluid flow path 2b and a row of horizontal holes 3b that are perpendicular to the second fluid flow path 2b and are formed so as to communicate with each other.
At this time, the heat exchanger 10b includes a plurality of rows (for example, 15 rows) of the second

fluid flow paths

21d and 21e disposed on the

second surfaces

42d and 42e substantially parallel to the first surface 41, respectively. This is the same as that added to the heat exchanger 10a. At this time, the inner diameter Db of the horizontal hole 3b is large because it extends over the five layers of the second fluid flow path 2b.

(C type)
2 (c) and 2 (d), the C-type heat exchanger 10c includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4, and 15 layers in two layers (30 rows in total). Second fluid flow path 2c, and a row of horizontal holes 3c formed perpendicular to the second fluid flow path 2c and communicating with each other. At this time, the inner diameter Dc of the horizontal hole 3c only needs to straddle the two layers of the second fluid flow path 2c, and thus has a small value.

When the fluid flowing through the heat exchanger undergoes a phase change, the velocity of the fluid increases in the order of liquid, gas-liquid two-phase, and gas at the same mass velocity. In order to reduce the pressure loss, it is necessary to design the diameter of the horizontal hole according to the state of the refrigerant, that is, the speed of the refrigerant. The configuration is such that the diameter of the horizontal hole 3 is increased according to the speed change accompanying the fluid state (the A type to the C type are properly used).
Moreover, the pressure loss in the 2nd fluid flow path 2 can be reduced by using each type properly.
The above is referred to as A type to C type for convenience of explanation, and the number of rows of the first fluid flow channel 1, the number of layers of the second fluid flow channel 2, and the number of rows in each layer are limited. It is not a thing.
In the above, for convenience of explanation, the diameter of the horizontal hole 3 is the diameter Da that can straddle the second fluid channel 21a and the second fluid channel 21c, but the second fluid channel 21a and the second fluid As long as it can straddle the flow path 21c, the diameter may be smaller than the diameter Da.

[Embodiment 2]
FIGS. 3 to 5 schematically illustrate a heat exchanger according to Embodiment 2 of the present invention. FIG. 3A is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the D type. 3 (b) is a cross-sectional view of the D type in a cross section parallel to the longitudinal direction, FIG. 4 (a) is a cross section of the E type, and FIG. 4 (b) is a cross section of the E type in a cross section parallel to the longitudinal direction. 5A is a cross-sectional view of the F type, and FIG. 5B is a cross-sectional view of a cross section parallel to the longitudinal direction of the F type. In addition, the same code | symbol is attached | subjected to the part which is the same as that of Embodiment 1, or an equivalent part, and one part description is abbreviate | omitted.

(D type)
3 (a) and 3 (b), the D-type heat exchanger 10d includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4 and two layers of 15 rows of second fluid flow. It has a channel 2d and a rectangular lateral hole 3d that allows the second fluid channel 2d to communicate with each other.
At this time, the horizontal hole 3d has the height of the second fluid channel 2d, has a long side in the longitudinal direction, and is provided perpendicular to the second fluid channel 2d. Other configurations and operations are the same as those in the first embodiment.
In the heat exchanger 10d configured as described above, the following operational effects are obtained.
That is, in the heat exchanger 10d having the rectangular horizontal hole 3d, the flow path cross-sectional area in the horizontal hole 3d is increased as compared with a circular shape, so that the influence of the expansion / reduction of the flow path is reduced. Therefore, the pressure loss in the horizontal hole 3d, that is, the pressure loss in the heat exchanger 10d is reduced.
The length of the long side is designed such that the refrigerant distribution performance is good. Therefore, the performance deterioration of the heat exchanger accompanying the deterioration of distribution performance can be suppressed.
Moreover, since the thickness of the heat transfer block 4 is suppressed (not increased) by providing the lateral holes 3d in a rectangular shape, it is possible to reduce the material cost by reducing the thickness of the heat exchanger.
Since the cross-sectional area of the rectangular lateral hole 3d is larger than that in the case where the horizontal hole 3d is formed in a circular shape, the use member filled therein is compared with the case in which the horizontal hole 3d is formed in a circular shape. The material cost can be reduced.
In the above description, the long side of the horizontal hole 3d is the longitudinal direction, but a configuration having a short side in the longitudinal direction may be used.

(E type)
4 (a) and 4 (b), an E-type heat exchanger 10e includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4 and two layers of second fluid flow of 15 rows. It has a channel 2e and an elliptical lateral hole 3e that allows the second fluid channel 2e to communicate with each other.
At this time, the horizontal hole 3e has the height of the second fluid channel 2e, has a long side in the longitudinal direction, and is provided perpendicular to the second fluid channel 2e. Other configurations and operations are the same as those in the first embodiment.
In the heat exchanger 10e configured as described above, the following operational effects are obtained.
That is, in the heat exchanger 10e having the elliptical lateral hole 3e, the flow passage cross-sectional area in the lateral hole 3e is increased as compared with a circular shape, so that the influence of expansion / reduction of the flow path is reduced. Therefore, the pressure loss in the horizontal hole 3e, that is, the pressure loss in the heat exchanger 10e is reduced.
The length of the long side is designed such that the refrigerant distribution performance is good. Therefore, the performance deterioration of the heat exchanger accompanying the deterioration of distribution performance can be suppressed.
Moreover, since the thickness of the heat transfer block 4 is suppressed (not increased) by providing the horizontal hole 3e in an elliptical shape, it is possible to reduce the material cost by reducing the thickness of the heat exchanger.
Since the cross-sectional area of the elliptical lateral hole 3e is larger than that in the case where the horizontal hole 3d is formed in a circular shape, the use member filled therein is compared with the case in which the horizontal hole 3d is formed in a circular shape. The material cost can be reduced.
Further, the E type heat exchanger 10e is obtained by making one row of rectangular horizontal holes 3d in the D type heat exchanger 10d into an elliptical shape. It becomes easy to form the horizontal hole 3e by machining such as an end mill.
In the above description, the long side of the horizontal hole 3e is the longitudinal direction, but a configuration having a short side in the longitudinal direction may be used.

(F type)
5 (a) and 5 (b), the F type heat exchanger 10f includes four rows of first fluid flow paths 1 arranged in the heat transfer block 4 and 15 layers of second fluid flow in two layers. The passage 2f and a plurality of lateral holes 3f communicating with the second fluid passage 2f are provided.
At this time, the horizontal hole 3f has a diameter that is the height of the second fluid channel 2f, and is provided in a plurality of rows (for example, two rows) perpendicular to the second fluid channel 2f and in the direction of the channel. Other configurations and operations are the same as those in the first embodiment.
In the heat exchanger 10f configured as described above, the following operational effects are obtained.
That is, in the heat exchanger 10f having a plurality of horizontal holes 3f, the flow path cross-sectional area in the horizontal hole 3f is increased as compared with the case where there is one, so that the influence of the expansion / reduction of the flow path is reduced. Therefore, the pressure loss in the horizontal hole 3f, that is, the pressure loss in the heat exchanger 10f is reduced.
Further, by providing a plurality of rows of the horizontal holes 3f, the thickness of the heat transfer block 4 is suppressed (not increased), so that it is possible to reduce the material cost by reducing the thickness of the heat exchanger.
The length of the long side is designed such that the refrigerant distribution performance is good. Therefore, the performance deterioration of the heat exchanger accompanying the deterioration of distribution performance can be suppressed.
Further, by providing a plurality of rows of the horizontal holes 3f, the thickness of the heat transfer block 4 is suppressed (not increased), so that it is possible to reduce the material cost by reducing the thickness of the heat exchanger.
Since the cross-sectional area of the horizontal holes 3f in the plurality of rows is larger than that in the case where the horizontal holes 3f are formed in a single circle, the cross holes are filled in compared to the case where the horizontal holes 3f are configured in a single circle. It becomes possible to reduce the material cost of the used members.
In addition, the F type heat exchanger 10f is configured such that one row of rectangular lateral holes 3d in the D type heat exchanger 10d is formed in a plurality of rows of circles. It becomes easy to form the horizontal hole 3f by machining such as an end mill.
Furthermore, by configuring the horizontal holes 3f in a plurality of rows, it is possible to improve the pressure resistance performance as compared with the case of configuring the rectangular holes and the ellipse.
In the above, the horizontal holes 3f are configured in two rows, but the number of rows is not limited.

[Embodiment 3]
FIG. 6 schematically illustrates a heat exchanger according to Embodiment 3 of the present invention. FIG. 6A is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the H type, and FIG. b) is a cross-sectional view in a cross section parallel to the longitudinal direction of the H type, FIG. 6C is a cross sectional view in a cross section perpendicular to the longitudinal direction of the I type, and FIG. 6D is parallel to the longitudinal direction of the I type. It is sectional drawing in a simple cross section. In addition, the same code | symbol is attached | subjected to the part which is the same as that of Embodiment 1, or an equivalent part, and one part description is abbreviate | omitted.

(H type)
6 (a) and 6 (b), an H type heat exchanger 10h includes four layers of first fluid flow paths 1 in one layer and two layers of second fluid flow in one layer in the heat transfer block 4. It has a passage 21a, a horizontal hole 3h, and a slit-like space 5h that is arranged on the opposite side of the first fluid passage 1 in parallel with the second fluid passage 21a. That is, the second fluid flow path 21a has a form sandwiched between the first fluid flow path 1 and the slit-shaped space 5h.
At this time, the slit-shaped space 5h is disposed on the third surface 43 parallel to the second surface 42a, and the lateral hole 3h is formed so as to straddle the second fluid flow path 21a and the slit-shaped space 5h. Sealing is applied to the slit-shaped space 5h in the portion where the horizontal hole 3h is opened so that the second fluid does not flow from the flow path 21a into the slit-shaped space 5h via the horizontal hole 3h.
That is, the sealing block 81 is liquid-tightly installed in a predetermined range of the slit-shaped space 5 h, and the horizontal hole 3 h penetrates a part of the sealing block 81. Note that the sealing process is not limited to the sealing block 81.
Accordingly, in the side view, the side hole 3h is substantially half (semicircle) of a circle having a diameter Dh that covers the second fluid channel 21a and the slit-shaped space 5h in the side view, and the first fluid channel 1 and the second fluid channel. It functions as a flow path communicating with 21a. Other configurations and operations are the same as those in the first embodiment.

In the heat exchanger 1 configured as described above, the following effects can be obtained.
In the heat exchanger 10h in which the diameter of the horizontal hole 3h is increased by the slit-shaped space 5h, the flow path cross-sectional area (the area of the semicircular communication portion) at the horizontal hole 3h increases, so the flow path is enlarged or reduced. The effect of.
Therefore, the pressure loss in the horizontal hole 3h, that is, the heat exchanger 10h is reduced. In addition, by providing the slit-shaped space 5h, the slit-shaped space 5h portion becomes a heat insulating layer, and the heat exchange performance is improved by preventing heat radiation from the second fluid flow path 21a to the outside of the heat transfer block 4. Is possible.
In the above description, the horizontal hole 3h has a circular cross section, but the shape is not limited.

(I type)
6 (c) and 6 (d), an I type heat exchanger 10i is obtained by dividing the slit-shaped space 5h in the H-type heat exchanger 10h into a plurality of slit-shaped spaces 5i. Although the slit-shaped space 5i having a rectangular cross section is shown, the present invention is not limited to this, and may be a rectangle such as a circle, an ellipse, or a square.
At this time, the sealing block 82 is liquid-tightly installed in a predetermined range in the slit-shaped space 5i having a rectangular cross section.
Therefore, the heat exchanger 10i can obtain the same effect as the heat exchanger 10h, and the rigidity of the side surface 45 close to the slit-like space 5i of the heat transfer block 4 is increased, so that heat transfer is performed as compared with the heat exchanger 10h. The block 4 is more difficult to deform.
In addition, although the formation method of the heat-transfer block 4 is not limited, For example, if it forms by integral extrusion processing, increase / decrease in the number of the lines of the 1st fluid flow path 1, the number of the 1st surfaces 41, or 2nd fluid. As the number of flow paths and the number of second surfaces 42 increase or decrease, the degree of freedom in selecting the form of the slit-shaped space 5 i increases.

[Embodiment 4]
7 schematically illustrates a heat exchanger according to Embodiment 4 of the present invention, in which (a) is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the J type, and (b) is a J type. It is sectional drawing in a cross section parallel to a longitudinal direction. In addition, the same code | symbol is attached | subjected to the part which is the same as that of Embodiment 1, or an equivalent part, and one part description is abbreviate | omitted.

(J type)
7 (a) and 7 (b), the heat exchanger 10j is a two-layered slit-like space 5i in the I-type heat exchanger 10i.
That is, the slit-shaped space 5j includes a plurality of lower-layer slit-shaped spaces 51a disposed intermittently on the third surface 43a parallel to the second surface 42a, and a plurality disposed intermittently on the third surface 43b parallel to the third surface 43a. Upper-layer slit-like space 51b. Each of the lower layer slit-like space 51a and the upper layer slit-like space 51b has a substantially square cross section, and the upper layer slit-like space 51b is disposed above the range sandwiched between the pair of lower-layer slit-like spaces 51a (a pair of upper-layer slit-like spaces 51a). The lower slit-like space 51a is arranged below the area sandwiched by 51b), and has a checkered pattern.
A sealing block 83a and a sealing block 83b are liquid-tightly installed in predetermined ranges of the lower layer slit-like space 51a and the upper layer slit-like space 51b, respectively.
Accordingly, the slit-shaped space 5j is the same as the H-type heat exchanger 10h except that the slit-shaped space 5j is constituted by the lower-layer slit-shaped space 51a and the upper-layer slit-shaped space 51a that are fine flow paths. 10j has the same effect as the heat exchanger 10h.
In addition, although the formation method of the heat-transfer block 4 is not limited, For example, if it forms by integral extrusion processing, increase / decrease in the number of the lines of the 1st fluid flow path 1, the number of the 1st surfaces 41, or 2nd fluid. As the number of flow paths and the number of second surfaces 42 increase or decrease, the degree of freedom in selecting the shape of the slit-shaped space 5j increases.

[Embodiment 5]
FIG. 8 schematically illustrates a heat exchanger according to Embodiment 5 of the present invention, in which (a) is a cross-sectional view in a cross section perpendicular to the longitudinal direction of the K type, and (b) is a K type. Sectional view in a cross section parallel to the longitudinal direction, (c) is a sectional view in a section perpendicular to the longitudinal direction of the L type, (d) is a sectional view in a section parallel to the longitudinal direction of the L type, (e) is an M type Sectional drawing in a cross section perpendicular | vertical to the longitudinal direction of FIG. 1, (f) is sectional drawing in a cross section parallel to the longitudinal direction of M type | mold. In addition, the same code | symbol is attached | subjected to the part which is the same as that of Embodiment 1, or an equivalent part, and one part description is abbreviate | omitted.

(K type)
8 (a) and 8 (b), the K-type heat exchanger 10k includes four rows of the first fluid flow paths 1 arranged in the heat transfer block 4, and six layers of 15 rows (total of 90 rows). Second fluid flow path 2k and a row of horizontal holes 3k that are perpendicular to the second fluid flow path 2k and are formed to communicate with each other.
That is, in the heat exchanger 10k, a plurality of rows (for example, 15 rows) of second fluid flow paths 21f arranged on the second surface 42f substantially parallel to the first surface 41 are added to the B type heat exchanger 10b. Is the same. At this time, the inner diameter Dk of the horizontal hole 3k is a large value because it extends over the six layers of the second fluid flow path 2k.

(L type)
In FIGS. 8C and 8D, an L-type heat exchanger 10l (10 ell) is obtained by dividing the lateral hole 3k in the K-type heat exchanger 10k into two strips. That is, the three layers of the second fluid flow paths 21a to 21c are a lower layer group, and the three layers of the small-diameter lateral hole 33a that communicates all the second fluid flow paths 21a to 21c of the lower layer group and the second fluid flow paths 21d to 21f. Is formed as an upper layer group, and a horizontal hole 3l (3 ell) is formed which includes a small-diameter horizontal hole 33b that communicates all the second fluid flow paths 21d to 21f of the upper layer group.
Therefore, the inner diameter of the horizontal hole 3l (3 ell) is approximately ½ of the inner diameter of the horizontal hole 3k.
When the fluid flowing through the heat exchanger undergoes a phase change, the fluid velocity increases in the order of liquid, gas-liquid two-phase, and gas at the same mass velocity. In order to reduce the pressure loss, it is necessary to set the inner diameter of the horizontal hole according to the state of the refrigerant, that is, the speed of the refrigerant.
Therefore, when the K type heat exchanger 10k (inner diameter Dk) cannot respond to the change in speed associated with the fluid state, the L type heat exchanger 10l (10 ell, inner diameter Dl (D ell)) is selected. be able to.

(M type)
8 (e) and 8 (f), an M type heat exchanger 10m is obtained by dividing the horizontal hole 3k in the K type heat exchanger 10k into three strips. That is, the two layers of the second

fluid flow paths

21a and 21b are set as a lower layer group, and the two layers of the small-diameter lateral hole 32a that communicates all the second

fluid flow paths

21a and 21b of the lower layer group and the second

fluid flow paths

21c and 21d. Is the middle layer group, and the two layers of the small-diameter lateral hole 32b and the second

fluid flow channels

21e and 21f communicating with all the second

fluid flow paths

21c and 21d of the middle layer group are the upper layer group, and the second fluid flow of the upper layer group A horizontal hole 3m is formed, which includes a small-diameter horizontal hole 32c that allows the

passages

21e and 21f to communicate with each other.
Therefore, the inner diameter of the horizontal hole 3m is approximately 1/3 of the inner diameter of the horizontal hole 3k.
Therefore, in the K-type heat exchanger 10k or the L-type heat exchanger 10l (10 ell), the M-type heat exchanger 10m can be selected when it is not possible to respond to the speed change associated with the fluid state. .

In addition, although the above demonstrated the 2nd fluid flow path which consists of 6 layers as an example, this invention is not limited to this, The number of layers of a 2nd fluid flow path may be arbitrary. . Further, any one of the slit-like spaces 5h to 5j described in the third and fourth embodiments may be provided. At this time, the sealing block 81 or the like is installed in any of the provided slit-shaped spaces 5h to 5j, and a part of the installed sealing block 81 or the like is penetrated to provide the provided slit-shaped spaces 5h to 5j. The second fluid flow paths 21d to 21f (or 21e, 21f) of the group closest to any of the above are formed.

[Embodiment 6]
The horizontal hole described in the first to fifth embodiments may be an ellipse or a rectangle. In particular, the width of the horizontal hole can be expanded in the flow direction of the second fluid flow path for the ellipse or the rectangle. That is, the pressure loss can be reduced by determining the cross-sectional area of the horizontal hole in accordance with the mass velocity of the refrigerant flowing in, the ratio of the vapor and liquid mass velocity (hereinafter, dryness).
Furthermore, by optimally designing the channel cross-sectional area, it is possible to allow the two-phase refrigerant to flow into the plurality of second fluid channels in a manner of flow (hereinafter referred to as a flow mode). Thereby, the effect which suppresses the performance fall of the heat exchanger by distribution deterioration is acquired. The flows that are easily distributed equally are an annular flow, an annular spray flow, a bubbling flow, a slag flow, and a spiral flow, and it is desirable to flow into the side holes in these flow modes. The appearance of the fluid flow in the two-phase state can be confirmed by a flow pattern diagram (for example, the Baker diagram (see FIG. 11)).
The refrigeration cycle apparatus according to Embodiment 6 of the present invention described below takes into consideration the flow mode.
The mass velocity of the refrigerant flowing into the side hole is “G”,
The mass velocities of the gas phase and liquid phase are "Gg and Gl",
The density of the gas phase and the liquid phase is “ρg and ρl”,
Viscosity coefficient of gas phase and liquid phase is “μg and μl”,
The surface tension is σ,
The density of air and water at an atmospheric temperature of 20 ° C. is “ρa and ρw”,
The viscosity coefficient of water at an atmospheric temperature of 20 ° C. is “μw”,
The surface tension of air-water at an atmospheric temperature of 20 ° C is “σw”,
The correction coefficient is “λ (= ((ρg / ρa) × (ρl / ρw)) ^1/2 )”
And “ψ (= (σw / σ) × ((μl / μw) × (ρw / ρl) ² ) ^1/3 )”,
The relationship of “Gl / Gg × λ × ψ” and “Gg / λ” exists in the region of annular flow, annular jet, slag flow, bubble flow and spiral flow on the flow pattern diagram.
That is, it is desirable to select the cross-sectional area of the horizontal hole so that “Gg / λ> 84544 × (Gl / Gg × λ × ψ) ^−0.676 ”.
As a specific example, if the mass rate is 200 kg / m ² s, the inlet dryness is 0.2, and the pressure is 2 MPa, “Gl / Gg × λ × ψ = 266” is obtained, and “84544 × (Gl / Gg × λ × ψ) ^{− 0.676} = 1952 ".
That is, it is preferable to use a horizontal hole having a channel cross-sectional area that satisfies “Gg / λ> 1952”, and the range is “Ah <2.78 × 10 8 ⁻³ m ² ”. In addition, when it is a flow-path cross-sectional area other than said range, since a flow style deteriorates and causes the performance deterioration of a heat exchanger, it is unpreferable.

[Embodiment 7: Heat pump heating system]
FIG. 9 illustrates a refrigeration cycle apparatus according to Embodiment 7 of the present invention, and is a configuration diagram of equipment showing a heat pump heating system that uses warm heat. In addition, the same code | symbol is attached | subjected to the same part as Embodiment 1, and one part description is abbreviate | omitted.
In FIG. 9, the heat pump heating system 60 is a heat exchange that performs heat exchange between the use side fluid pipe 61 through which the first fluid flows, the heat source side fluid pipe 62 through which the second fluid flows, and the first fluid and the second fluid. A container 10a. That is, the first fluid channel 1 forms a part of the use side fluid pipe 61, and the second fluid channel 2 forms a part of the heat source side fluid pipe 62.

In the heat pump heating system 60, “water” is used as the first fluid, and “R410a” is used as the second fluid.
The usage-side fluid pipe 61 sequentially connects the heat exchanger 10a (first fluid flow path 1), the pump 61a, and the usage-side heat exchanger 61b to enable circulation of the first fluid.
The heat source side fluid pipe 62 sequentially connects the compressor 62a, the heat exchanger 10a (second fluid flow path 2), the expansion valve 62b, the heat source side heat exchanger 62c, and the fan 62d to enable circulation of the second fluid. ing.

The first fluid in the use side fluid pipe 61 is heated in the heat exchanger 10a (receives heat from the second fluid), is sent out by the pump 61a, and radiates heat in the use side heat exchanger 61b (to the use side fluid or the like). Hand over the heat). As the use-side heat exchanger 61b, for example, a radiator or a floor heater is applied and used as a heating system.
In the heat source side fluid piping 62, the second fluid that has become high temperature and pressure in the compressor 62a exchanges heat with the first fluid in the heat exchanger 10a (delivering the heat). Thereafter, the second fluid, which has been decompressed at the expansion valve 62b and becomes low temperature and pressure, undergoes heat exchange (cold heat release) with the air blown by the fan 62d in the heat source side heat exchanger 62c, evaporates, and then the compressor Return to 62a.
As shown in FIG. 9, the heat pump type heating system 60 using the heat exchanger 10 a of the present invention is used as a heat source to heat or hot water in the use side heat exchanger 61 b, thereby comparing with a heating system using a conventional boiler as a heat source. Energy saving effect.
Although the above shows a type equipped with an A type heat exchanger 10a, the present invention is not limited to this, and any of the B type to M type may be used. Thus, the number of rows of the first fluid channel 1, the number of layers of the second fluid channel 2, and the number of rows in each layer are not limited.

[Embodiment 8: Heat pump hot water supply system]
FIG. 10 illustrates a refrigeration cycle apparatus according to Embodiment 8 of the present invention, and is a configuration diagram of equipment showing a heat pump type hot water supply system using warm heat. In addition, the same code | symbol is attached | subjected to the same part as

Embodiment

1, 2, and one part description is abbreviate | omitted.
In FIG. 10, a heat pump hot water supply system 70 is a hot water supply system in which the use-side heat exchanger 61 b in the heat pump hot water supply system 60 is installed in the tank 63 and the water supplied to the tank 63 is heated to take water. is there.
As shown in FIG. 10, the heat pump hot water supply system 70 (same as the heat pump hot water supply / heating system) using the heat exchanger 10a of the present invention is used as a heat source for heating or hot water supply by the use side heat exchanger 61b. Compared to a hot water supply system using a boiler as a heat source, there is an energy saving effect.

1 1st fluid flow path, 2nd fluid flow path, 3 side hole, 4 heat transfer block, 5 slit-shaped space, 10a heat exchanger (A type), 10b heat exchanger (B type), 10c heat exchanger ( C type), 10d heat exchanger (D type), 10e heat exchanger (E type), 10f heat exchanger (F type), 10h heat exchanger (H type), 10i heat exchanger (I type), 10j Heat exchanger (J type), 10k heat exchanger (K type), 10l heat exchanger (L type), 10m heat exchanger (M type), 21a to 21f second fluid flow path, 32a small diameter side hole, 32b small diameter Horizontal hole, 32c Small diameter horizontal hole, 33a Small diameter horizontal hole, 33b Small diameter horizontal hole, 41 1st surface, 42a-42c 2nd surface, 43 3rd surface, 44 side surface, 45 side surface, 51a Lower slit-shaped sky 51b, upper-layer slit-like space, 60 heat pump heating system (sixth embodiment), 61 usage side fluid piping, 61a pump, 61b usage side heat exchanger, 62 heat source side fluid piping, 62a compressor, 62b expansion valve, 62c Heat source side heat exchanger, 62d fan, 63 tank, 70 heat pump hot water supply system (seventh embodiment), 81 sealing block, 82 sealing block, 83a sealing block, 83b sealing block.

Claims

A plurality of rows of first fluid passages formed in parallel to each other on a first surface, which is a plane in the heat transfer block, and penetrating the heat transfer block;
A plurality of rows of second fluid flow paths formed in parallel to the first fluid flow path on a second surface parallel to the first surface in the heat transfer block, and penetrating the heat transfer block;
A lateral hole formed in the heat transfer block and communicating with all of the second fluid flow path;
Have
The lateral hole is perpendicular to the second fluid flow path;
L / A 2 when the horizontal hole has a cross-sectional area A of the second fluid flow path, an equivalent diameter d, a length L, and a cross-sectional area A y of the horizontal hole, an equivalent diameter d y , and an equivalent length L y. d> are formed by L y / a y 2 d y become such diameter and number,
The horizontal hole communicates all the second fluid flow paths, and does not protrude from the heat transfer block portion between the first fluid flow path and the adjacent second fluid flow path. .
The second surfaces are a plurality of layers parallel to each other;
2. The heat exchanger according to claim 1, wherein the lateral hole communicates with the second fluid flow path formed in all layers of the plurality of layers.
The second surfaces are a plurality of layers parallel to each other;
The lateral hole is formed in a rectangular shape;
The heat exchanger according to claim 1, wherein the second fluid flow paths formed in all of the plurality of layers are communicated.
The second surfaces are a plurality of layers parallel to each other;
The lateral hole is formed in an oval shape;
The heat exchanger according to claim 1, wherein the second fluid flow paths formed in all of the plurality of layers are communicated.
The second surfaces are a plurality of layers parallel to each other;
The second fluid flow paths are divided into a plurality of groups;
The heat exchanger according to claim 1, wherein the horizontal hole is formed for each of the second fluid flow paths divided into the plurality of groups.
The second surface is a plurality of layers,
The heat exchanger according to claim 1, wherein the horizontal holes are formed in a plurality of rows at predetermined intervals.
The heat exchanger according to claim 1, wherein the heat exchanger has a slit-like space having a predetermined thickness, which is formed on the opposite side of the first fluid channel with the second fluid channel interposed therebetween.
The heat exchanger according to claim 7, wherein the slit-like spaces are formed by a plurality of rows of narrow slit-like spaces formed in parallel to each other.
A sealing block is liquid-tightly installed in a predetermined range of the slit-shaped space,
The lateral hole is formed by machining or plastic working from one side surface of the heat transfer block through a part of the sealing block, and the opening formed in the side surface is closed. The heat exchanger according to claim 7.
G represents the mass velocity of the refrigerant flowing into the side hole,
Gg and Gl for mass velocities of the gas phase and liquid phase,
The density of the gas phase and the liquid phase is ρg and ρl,
The viscosity coefficients of the gas phase and liquid phase are μg and μl,
The surface tension is σ,
The density of air and water at an atmospheric temperature of 20 ° C. is expressed as ρa and ρw,
The viscosity coefficient of water at an atmospheric temperature of 20 ° C. is μw,
Σw is the surface tension of air-water at an atmospheric temperature of 20 ° C,
The correction coefficient is λ (= ((ρg / ρa) × (ρl / ρw)) 1/2 )
And ψ (= (σw / σ) × ((μl / μw) × (ρw / ρl) 2 ) 1/3 ),
In the flow pattern diagram showing the relationship between Gg / λ and Gl / Gg × λ × ψ, Gg / λ> is a relationship existing in the region of annular flow, annular spray flow, slag flow, bubble flow, and spiral flow. 84544 × (Gl / Gg × λ × ψ) −0.676
The heat exchanger according to any one of claims 1 to 9, wherein a cross-sectional area of the horizontal hole is selected so that
The heat exchange is performed between the use side fluid piping through which the first fluid flows, the heat source side fluid piping through which the second fluid flows, and the first fluid and the second fluid. A heat exchanger,
The usage-side fluid piping sequentially connects the first fluid flow path of the heat exchanger, the pump that sends out the first fluid, and the usage-side heat exchanger, and enables circulation of the first fluid.
The heat source side fluid piping sequentially connects the compressor that compresses the second fluid of the heat exchanger, the second fluid flow path, the expansion valve, and the heat source side heat exchanger to enable circulation of the second fluid. A refrigeration cycle apparatus characterized by comprising: