WO2012017681A1

WO2012017681A1 - Heat exchanger and refrigeration and air conditioning device

Info

Publication number: WO2012017681A1
Application number: PCT/JP2011/004459
Authority: WO
Inventors: 寿守務吉村; 浩昭中宗; 瑞朗酒井; 宗史池田
Original assignee: 三菱電機株式会社
Priority date: 2010-08-05
Filing date: 2011-08-05
Publication date: 2012-02-09
Also published as: EP2602578A1; US20130126127A1; JP5777622B2; EP2602578B1; JPWO2012017681A1; EP2602578A4; CN103069245A

Abstract

A heat exchanger (10) is provided with first flat tubes (1) having multiple through-holes through which a high-temperature fluid flows, second flat tubes (2) having multiple through-holes (21) through which a low-temperature fluid flows, a tube-shape first inlet header (3) connected to one end of the first flat tubes (1), a tube-shape first outlet header (4) connected to the other end of the first flat tubes (1), a tube-shape second inlet header (5) connected to one end of the second flat tubes (2), and a tube-shape second outlet header (6) connected to the other end of the second flat tubes (2), wherein the first flat tubes (1) and the second flat tubes (2) are stacked so as be in contact with another on the flat surface. The low-temperature fluid flowing from the second inlet header (5) into the through-holes (21) of the second flat tubes (2) is in a gas-liquid two-phase state, and the direction of flow of the low-temperature fluid from the second inlet header (5) into the through-holes (21) of the second flat tubes (2) is either substantially horizontal or more upwards than substantially horizontal.

Description

Heat exchanger and refrigeration air conditioner

The present invention relates to a heat exchanger for transferring heat from a high temperature fluid to a low temperature fluid by exchanging heat between the low temperature fluid and the high temperature fluid. The present invention also relates to a refrigeration air conditioner using this heat exchanger.

A conventional heat exchanger is connected to both ends of a first flow path portion having a plurality of through-holes through which a low-temperature fluid flows, a second flow path portion having a plurality of through-holes through which a high-temperature fluid flows. The first header and the second header connected to both ends of the second flow path section are provided, and the first flow path section and the second flow path section are parallel to each other in the longitudinal direction (fluid flow direction). In this manner, the respective surfaces are contact-laminated, and at least one of the high-temperature fluid and the low-temperature fluid is a gas-liquid two-phase fluid, and the inner diameter of the inlet header through which the gas-liquid two-phase fluid flows is By making it smaller than the inner diameter of the other headers, by mixing the gas and liquid in the pipe by increasing the gas flow rate, the gas and liquid are made uniform, and by distributing the cryogenic fluid to each through hole with the same gas-liquid ratio, Maximizes the temperature efficiency of the fluid and achieves high heat exchange performance Are (e.g., see Patent Document 1.).

JP 2008-101852 (paragraph 0036, FIG. 1)

A refrigeration air conditioner using a conventional heat exchanger as described above has a refrigerant circuit in which a compressor, a radiator, a flow rate control means, and an evaporator are connected by a refrigerant pipe, and an HFC (hydrofluorocarbon) refrigerant, A refrigerant such as hydrocarbon or oxygen dioxide is configured to circulate in the refrigerant circuit. In order to increase the efficiency of the refrigeration air conditioner, it is important to improve the heat exchange performance of the heat exchanger.

However, in the conventional heat exchanger as described above, when the gas-liquid two-phase refrigerant flows through the inlet header in a low flow rate region, the gas-liquid mixing becomes insufficient and the gas-liquid is separated. And the ratio of the gas-liquid distributed to each through-hole of a flow-path part will become non-uniform | heterogenous. For this reason, excess and deficiency arises in the flow rate of the fluid which can exchange heat effectively for every through hole of a channel part. Therefore, the conventional heat exchanger as described above has a problem that the temperature efficiency is remarkably lowered and the heat exchange performance is lowered. In addition, there is a problem that the heat exchanger must be made larger than necessary to compensate for the deterioration of the heat exchange performance. On the other hand, if the header diameter is made too thin in accordance with the low flow rate region, when the gas-liquid two-phase refrigerant flows through the inlet header in the high flow rate region, the pressure loss increases, and the drive device sends the fluid to the heat exchanger There was a problem of causing an increase in power. As described above, the conventional heat exchanger as described above realizes an even distribution of gas and liquid in a wide operation range, and it is difficult to operate the heat exchanger efficiently.

The present invention has been made to solve the above-described problems, and aims to obtain a compact and high-performance heat exchanger and refrigeration air conditioner.

The heat exchanger of the present invention includes a first flow path portion having a plurality of through holes through which a high temperature fluid flows, a second flow path portion having a plurality of through holes through which a low temperature fluid flows, and one end of the first flow path portion. A tubular first inlet header connected to the first flow path portion, a tubular first outlet header connected to the other end portion of the first flow path portion, and a tubular shape connected to one end portion of the second flow path portion. A second inlet header and a tubular second outlet header connected to the other end of the second flow path portion, wherein the first flow path portion and the second flow path portion are provided between each other. A high-temperature fluid that is arranged to be capable of exchanging heat through the partition wall and flows into the through hole of the first flow path portion from the first inlet header and a low-temperature fluid that flows into the through hole of the second flow path portion from the second inlet header Is a gas-liquid two-phase fluid, and the flow direction of the gas-liquid two-phase fluid from the inlet header to the flow path portion is In which it has an upper direction than the substantially horizontal direction or a substantially horizontal direction.

Further, the refrigeration air conditioner of the present invention is equipped with the heat exchanger of the present invention.

According to the present invention, a compact and high-performance heat exchanger can be provided. Further, according to the present invention, a compact and high-performance refrigeration air conditioner can be provided.

It is a figure which shows the heat exchanger by Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows another example of the 2nd flat tube by Embodiment 1 of this invention. It is a figure which shows the heat-transfer characteristic of the heat exchanger by Embodiment 1 of this invention. It is a figure which shows another heat transfer characteristic of the heat exchanger by Embodiment 1 of this invention. It is a figure which shows another heat transfer characteristic of the heat exchanger by Embodiment 1 of this invention. It is a side view which shows an example of the heat exchanger by Embodiment 2 of this invention. It is a refrigerant circuit figure which shows an example of the refrigerating air conditioning apparatus by Embodiment 3 of this invention. It is a refrigerant circuit figure which shows another example of the refrigerating air conditioning apparatus by Embodiment 3 of this invention. It is a refrigerant circuit figure which shows another example of the refrigerating air conditioning apparatus by Embodiment 3 of this invention. It is a structural diagram of the heat exchanger by Embodiment 4 of this invention. It is a structural diagram which shows another example of the heat exchanger by Embodiment 4 of this invention.

Embodiment 1 FIG.
FIG. 1 is a view showing a heat exchanger according to Embodiment 1 of the present invention. FIG. 1 (a) is a perspective view, FIG. 1 (b) is a side view, and FIG. Sectional drawing of the connection part vicinity with 2 flat tubes is shown. In addition, FH shown to Fig.1 (a) shows the flow of a high temperature fluid, and FC shown to Fig.1 (a) shows the flow of a low temperature fluid. Moreover, in this Embodiment 1, the case where a low-temperature fluid flows in into a 2nd header in a gas-liquid two-phase state is demonstrated. Moreover, in the following drawings, what attached | subjected the same code | symbol is the same or it corresponds, This is common in the whole text of a specification.

In Embodiment 1, the second flatness shown in FIG. 1 is based on the knowledge obtained by the experiments shown in FIGS. 3 to 5, that is, the range of posture angles α, β, and γ, which will be described later, excellent in heat transfer characteristics. By providing the inflow part 2a which becomes substantially horizontal at the end part of the pipe 2, the heat exchanger 10 having excellent heat transfer characteristics is realized. That is, in FIG. 1, the second flat tube 2 is connected to the second inlet header 5 at a posture angle α = 90 °.

Each of the first flat tubes 1 has a plurality of through holes through which a high-temperature fluid flows along the longitudinal direction (the left-right direction in FIG. 1B). This through hole is provided side by side in the width direction of the first flat tube 1 (in the direction orthogonal to the plane of FIG. 1B). Each of the second flat tubes 2 has a plurality of through holes 21 through which a low-temperature fluid flows along the longitudinal direction (the left-right direction in FIG. 1B). The through hole 21 is provided side by side in the width direction of the second flat tube 2 (the direction perpendicular to the paper surface of FIG. 1B). The 1st flat tube 1 and the 2nd flat tube 2 are laminated | stacked so that the flat surface of the 1st flat tube 1 and the flat surface of the heat exchange part 2c in the 2nd flat tube 2 may mutually contact. The first flat tube 1 and the second flat tube 2 are laminated so that the flow directions of the fluid flowing in the

flat tubes

1 and 2 are parallel to each other. The 1st flat tube 1 and the 2nd flat tube 2 are joined by brazing, adhesion | attachment, etc., for example. For example, when the first flat tube 1 and the second flat tube 2 are both aluminum or an aluminum alloy, the brazing material and flux used for brazing are those of aluminum / silicon or fluoride. Also, for example, when one of the first flat tube 1 or the second flat tube 2 is aluminum or an aluminum alloy and the other of the first flat tube 1 or the second flat tube 2 is copper, a brazing material or flux used for brazing Zinc / aluminum and aluminum / cesium / fluoride materials are used. In addition, the combination of brazing material and flux is more suitable as the former melting point and the latter activation temperature are closer, because the brazing property is improved by improving the flowability of the brazing material.

The first flat tube 1 has one end portion in the longitudinal direction connected to the side surface of the tubular first inlet header 3 and the other end portion connected to the side surface of the tubular first outlet header 4. That is, the through holes formed in the first flat tube 1 constitute a parallel flow path through which a high-temperature fluid flows. An inflow portion 2 a that is one end portion in the longitudinal direction of the second flat tube 2 is connected to a side surface of the tubular second inlet header 5. An outflow portion 2 d that is the other end portion in the longitudinal direction of the second flat tube 2 is connected to a side surface of the tubular second outlet header 6. Moreover, the inflow part 2a and the outflow part 2d are connected with the heat exchange part 2c through the bending part 2b. That is, the through hole 21 formed in the second flat tube 2 constitutes a parallel flow path through which a low-temperature fluid flows.

The first inlet header 3, the first outlet header 4, the second inlet header 5, and the second outlet header 6 are respectively in the tube axis direction and the flat surfaces of the flat tubes 1 and 2 (that is, the

flat tubes

1 and 2. Are arranged in parallel with each other.
Further, the inflow portion 2a of the second flat tube 2 connected to the second inlet header 5 in which the low-temperature fluid flows in a gas-liquid two-phase state is substantially horizontal. That is, the flow path of the low-temperature fluid in a gas-liquid two-phase state flowing into the second flat tube 2 from the second inlet header 5 (in other words, the through hole 21 of the inflow portion 2a) is substantially horizontal.
The first flat tube 1 corresponds to the “first flow channel portion” of the present invention, and the second flat tube 2 corresponds to the “second flow channel portion” of the present invention.

The high-temperature fluid flows in the order of the first inlet header 3, the first flat tube 1, and the first outlet header 4, and the low-temperature fluid flows in the order of the second inlet header 5, the second flat tube 2, and the second outlet header 6, Both fluids exchange heat through a contact portion between the flat tube 1 and the second flat tube 2 (more specifically, the heat exchanging portion 2c). That is, the high-temperature fluid flowing through the through hole of the first flat tube 1 and the low-temperature fluid flowing through the through hole of the second flat tube 2 are the first flat tube 1 and the second flat tube 2 that serve as a partition wall between the two through holes. Heat is exchanged through the outer shell.

In the first embodiment, the heat exchanger 10 is configured by several first flat tubes 1 and second flat tubes 2, but the number of the

flat tubes

1 and 2 is the number of the first embodiment. Not limited to. One first flat tube 1 and one second flat tube 2 may be alternately arranged along the flat surface to form a parallel flow path. Further, in the first embodiment, the first flat tube 1 and the second flat tube 2 are in contact with each other so that the flow directions of the fluids flowing in the respective tubes are parallel to each other. You may let them. Moreover, the 1st flat tube 1 and the 2nd flat tube 2 may be folded, and the 1st flat tube 1 and the 2nd flat tube 2 may be laminated | stacked. Moreover, in FIG.1 (c), although the edge part of the inflow part 2a of the 2nd flat tube 2 has substantially corresponded to the inner surface of the 2nd inlet header 5, the edge part of the inflow part 2a of the 2nd flat tube 2 is the 1st. The two inlet headers 5 may be protruded inside.

In the heat exchanger 10 shown in the first embodiment, the end of the second flat tube 2 connected to the second inlet header 5 through which the gas-liquid two-phase fluid flows is substantially horizontal. That is, the outflow direction of the gas-liquid two-phase fluid flowing out from the second inlet header 5 to each through hole 21 (in other words, the inflow direction of the gas-liquid two-phase fluid flowing into each through hole 21) is substantially horizontal. . More specifically, in the case of the first embodiment, even if the flow rate of the refrigerant is reduced in the second inlet header 5 and the gas and liquid are separated vertically, the second flattening from the bottom of the second inlet header 5 occurs. Since the liquid is accumulated up to the vicinity of the inflow portion to the tube 2 and the gas-liquid boundary surface is formed in the vicinity of the inflow portion to the second flat tube 2, the gas-liquid distribution is improved. That is, for example, when the refrigerant flows vertically downward from the second inlet header 5 to each second flat tube 2, before the liquid level is formed in the second inlet header 5, the upstream side Since only the liquid tends to selectively flow out to the second flat tube 2, the gas-liquid distribution is deteriorated. However, in the heat exchanger 10 according to the first embodiment, the end of the second flat tube 2 connected to the second inlet header 5 is substantially horizontal, so that has never been said. For this reason, it is possible to distribute the low-temperature fluid to each through hole 21 of the second flat tube 2 so that the gas-liquid ratio is uniform, to maximize the temperature efficiency of the fluid, and to minimize the pressure loss. Therefore, the heat exchange performance of the heat exchanger 10 can be improved. Therefore, in the heat exchanger 10 shown in this Embodiment 1, a compact and high-performance heat exchanger can be obtained.

In addition, about the edge part of the flat tube connected to

other headers

3, 4, and 6 as long as a gas-liquid two-phase fluid does not flow in, it does not need to be horizontal especially.
In the first embodiment, the second flat tube 2 is bent outside the second inlet header 5 to form the inflow portion 2a. However, as shown in FIG. 2, the gas-liquid in the second inlet header 5 is formed. The inflow portion 2a may be formed by bending the second flat tube 2 inside the second inlet header 5 to such an extent that the flow of the air is not disturbed.

In the heat exchanger 10 of the first embodiment, the inflow portion 2a of the second flat tube 2 connected to the second inlet header 5 is kept substantially horizontal even when the direction of the heat exchanger 10 is reversed upside down. . For this reason, the distribution of gas and liquid does not deteriorate. Therefore, the heat exchanger 10 according to the first embodiment also has an effect that the degree of freedom in installation and the degree of freedom in connection and connection of piping are increased.

In general, the distribution characteristics of a gas-liquid two-phase fluid to each through hole of a flat tube vary greatly depending on the outflow direction of the fluid flowing from the header to each through hole (in other words, the inflow direction of the fluid flowing into each through hole). To do. Therefore, the effect of this direction on the heat transfer characteristics of the heat exchanger 10 (that is, the distribution characteristics of the gas-liquid two-phase fluid) was examined by experiments (FIGS. 3 to 5). In the experiments shown in FIG. 3 to FIG. 5, warm water was allowed to flow through the first flat tube 1 as a high-temperature fluid, and low-temperature chlorofluorocarbon refrigerant in a gas-liquid two-phase state was flowed through the second flat tube 2 as a low-temperature fluid. And the heat-transfer characteristic KA (W / K) of the heat exchanger 10 was measured using the inlet-and-outlet temperature of each fluid, Formula 1 and Formula 2.

Here, M _h : Mass flow rate of high-temperature fluid (kg / h), Cp _h : Constant pressure specific heat of high-temperature fluid (J / kgK), T _hi : High-temperature fluid inlet temperature, T _ho : High-temperature fluid outlet temperature, T _{CO 2 is} the outlet temperature of the cryogenic fluid, and T _Ci is the inlet temperature of the cryogenic fluid.

In the experiments shown in FIGS. 3 to 5, the configuration of the heat exchanger 10 was set as follows.
The inner diameter D of the second inlet header 5 was 6 mm. The through holes formed in the first flat tubes 1 were rectangular holes of about 1 mm square, and the total number of through holes formed in each first flat tube 1 was 60. The through holes are formed side by side in the width direction of the first flat tube 1. The through holes 21 formed in the second flat tube 2 were also rectangular holes of about 1 mm square, and the total number of through holes 21 formed in each second flat tube 2 was 60. The through holes 21 are formed side by side in the width direction of the second flat tube 2.
The protruding length of the end portion of the first flat tube 1 from the inner surface of the header was 2 mm.

In the experiments shown in FIGS. 3 to 5, the heat transfer characteristic KA (W / K) was measured under the following conditions.
The mass flow rate M _h of the high-temperature fluid was 600 kg / h. Mass flow rate _{M c} of the cryogen is in the range of 80 ~ 100kg / h. The ratio of the mass flow rate of the gas to the total mass flow rate of the gas-liquid (ie, dryness X) of the cryogenic fluid was adjusted to 0.1 to 0.2. The range of the dryness X is a general use range as the dryness of the inlet of the heat exchanger 10 used in a general refrigeration air conditioner.
In addition, the triangle, square, and circle shown in FIG. 3C, FIG. 4C, and FIG. 5C below represent heat transfer characteristics under the following conditions. Squares, the mass flow rate M _c of the cryogen represents the heat transfer characteristics in the case of 80 kg / h. Triangles, the mass flow rate M _c of the cryogen represents the heat transfer characteristics in the case of 90 kg / h. Circles, the mass flow rate M _c of the cryogen represents the heat transfer characteristics in the case of 100 kg / h.

3 to 5, in the state where the second inlet header 5 is almost horizontal, the refrigerant flow in the second inlet header 5 tends to be a flow in which the gas and liquid are vertically separated by the mass velocity. Further, in the state where the second inlet header 5 is nearly vertical, the flow of the refrigerant in the second inlet header 5 tends to cause the gas-liquid to be separated into an annular shape due to the mass velocity. For example, such a difference in properties between the horizontal and vertical headers occurs when the attitude angle γ or β is around 45 °.

3 shows that the second inlet header 5 is arranged in the horizontal direction, and the low-temperature fluid in the gas-liquid two-phase state flows out into the through hole 21 of the second flat tube 2 (in other words, flows into the through hole 21). The heat transfer characteristics when the posture angle α, which is the inflow direction of the low-temperature fluid to be changed, is changed. Here, FIG. 3A is an explanatory diagram of the posture angle α. FIG. 3B is a layout diagram of the heat exchanger 10 at the main posture angle α. FIG. 3C shows the experimental results and shows the relationship between the posture angle α and the heat transfer characteristic (relative value). The heat transfer characteristic (relative value) of the heat exchanger 10 shown on the vertical axis of FIG. 3 (c) distributes the low-temperature fluid to each through hole 21 of the second flat tube 2 so that the gas-liquid ratio becomes uniform. The heat transfer characteristics under the conditions were expressed as relative values with the value of 1.

Note that, unlike the heat exchanger 10 shown in FIG. 1, the end of the second flat tube 2 shown in FIG. 3 has one bent portion. That is, the 2nd flat tube 2 shown in FIG. 3 becomes a structure by which the inflow part 2a and the outflow part 2d are directly connected to the heat exchange part 2c (not via the bending part 2b). Further, when the posture angle α = 0 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is a vertically upward direction. When 0 ° <attitude angle α <90 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is upward from the horizontal direction. When the posture angle α = 90 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is the horizontal direction. When 90 ° <attitude angle α <180 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out into the through hole 21 of the second flat tube 2 is lower than the horizontal direction. When the posture angle α = 180 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is a vertically downward direction.

As shown in FIG. 3C, when −110 ° <attitude angle α <110 ° (more preferably, at 80 ° <attitude angle α <100 ° or −80 ° <attitude angle α <−100 °). It was found that the heat transfer characteristics can be maintained high. In particular, the heat transfer characteristics were found to be highest when the posture angle α was around 90 ° (85 ° <posture angle α <95 ° or −85 ° <posture angle α <−95 °). Further, it has been found that when the posture angle α is 110 ° or less, the heat transfer characteristics are drastically lowered. That is, from this result, it was found that when −110 ° <attitude angle α <110 °, the gas-liquid ratio of the low-temperature fluid distributed to each through hole 21 is substantially equal. Further, it has been found that when the posture angle α is set to approximately −90 ° or approximately 90 °, the gas-liquid ratio of the low-temperature fluid distributed to each through hole 21 can be made more equal. As described above, when the attitude angle α is set to approximately −90 ° or approximately 90 °, even if the flow velocity decreases in the second inlet header 5 and the gas-liquid is separated vertically, the second inlet header 5 The inflow portion into the second flat tube 2 is not always filled with the liquid phase, and only the liquid selectively flows out into the second flat tube 2 on the upstream side, and the distribution of gas and liquid is deteriorated. Absent. When the attitude angle α is around 0 °, the liquid tends to flow into the second flat tube 2 on the back side as viewed from the inlet side of the second header 5 due to the inertia of the liquid, but the flow is caused by gravity acting on the liquid. This suppresses the deterioration of distribution to some extent.

FIG. 4 shows the transmission when the orientation angle γ of the second inlet header 5 is changed with the outflow direction when the low-temperature fluid in the gas-liquid two-phase state flows out into the through hole 21 of the second flat tube 2. Shows thermal properties. Here, FIG. 4A is an explanatory diagram of the posture angle γ. FIG. 4B is a layout diagram of the heat exchanger 10 at main posture angles γ. FIG. 4C shows the experimental results and shows the relationship between the posture angle γ and the heat transfer characteristic (relative value). The heat transfer characteristic (relative value) of the heat exchanger 10 shown on the vertical axis in FIG. 4 (c) distributes the low-temperature fluid to each through hole 21 of the second flat tube 2 so that the gas-liquid ratio is uniform. The heat transfer characteristics under the conditions were expressed as relative values with the value of 1.

In addition, unlike the heat exchanger 10 shown in FIG. 1, the edge part of the 2nd flat tube 2 shown in FIG. 4 becomes a structure without a bending part. That is, the 2nd flat tube 2 shown in FIG. 4 becomes the structure by which the inflow part 2a and the outflow part 2d, and the heat exchange part 2c became parallel. Further, when the posture angle γ = 0 °, the inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the second inlet header 5 is the horizontal direction. When 0 ° <attitude angle γ <90 °, the inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the second inlet header 5 is downward from the horizontal direction. When the attitude angle γ is 90 °, the inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the second inlet header 5 is a vertically downward direction. When −90 ° <attitude angle γ <0 °, the inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the second inlet header 5 is upward from the horizontal direction. When the attitude angle γ = −90 °, the inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the second inlet header 5 is a vertically upward direction.

As shown in FIG. 4C, the heat transfer characteristics of the heat exchanger 10 tend to be slightly higher when the second inlet header 5 is vertical, but the posture angle γ is relative to the posture of the second inlet header 5. It was found that the impact was relatively small.

FIG. 5 shows the heat transfer characteristics when both the attitude of the second inlet header 5 and the outflow direction when the low-temperature fluid in the gas-liquid two-phase state flows out to the through hole 21 of the second flat tube 2 are changed. Show. Here, FIG. 5A is an explanatory diagram of the posture angle β. FIG. 5B is a layout diagram of the heat exchanger 10 at the main posture angle β. FIG. 5C shows the experimental results and shows the relationship between the posture angle β and the heat transfer characteristic (relative value). The heat transfer characteristic (relative value) of the heat exchanger 10 shown on the vertical axis in FIG. 5 (c) distributes the low-temperature fluid to each through hole 21 of the second flat tube 2 so that the gas-liquid ratio becomes uniform. The heat transfer characteristics under the conditions were expressed as relative values with the value of 1.

Note that, unlike the heat exchanger 10 shown in FIG. 1, the end of the second flat tube 2 shown in FIG. 5 has one bent portion. That is, the 2nd flat tube 2 shown in FIG. 5 becomes a structure by which the inflow part 2a and the outflow part 2d are directly connected to the heat exchange part 2c (not via the bending part 2b).

Further, when the posture angle β = 0 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 becomes the horizontal direction, and the low-temperature fluid flowing into the second inlet header 5 The inflow direction of (gas-liquid two-phase state) is a vertically downward direction. When 0 ° <attitude angle β <90 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is upward from the horizontal direction, and to the second inlet header 5 The inflow direction of the inflowing low-temperature fluid (gas-liquid two-phase state) is downward from the horizontal direction. When the attitude angle β = 90 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is a vertically upward direction and flows into the second inlet header 5 The inflow direction of the low-temperature fluid (gas-liquid two-phase state) is horizontal. When 90 ° <attitude angle β <180 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is upward from the horizontal direction, and the second inlet The inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the header 5 is upward from the horizontal direction. When the attitude angle β = 180 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 becomes the horizontal direction, and the low-temperature fluid (air) flowing into the second inlet header 5 The inflow direction of the liquid two-phase state is a vertically upward direction.

When −90 ° <attitude angle β <0 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 is lower than the horizontal direction, and the second inlet The inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the header 5 is downward from the horizontal direction. When the attitude angle β = −90 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out into the through hole 21 of the second flat tube 2 is a vertically downward direction, and the second inlet header 5 The inflow direction of the inflowing low-temperature fluid (gas-liquid two-phase state) is the horizontal direction. When −180 ° <attitude angle β <−90 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out into the through hole 21 of the second flat tube 2 is lower than the horizontal direction. The inflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing into the two inlet header 5 is downward from the horizontal direction. When the attitude angle β = −180 °, the outflow direction of the low-temperature fluid (gas-liquid two-phase state) flowing out to the through hole 21 of the second flat tube 2 becomes the horizontal direction, and the low-temperature fluid flowing into the second inlet header 5 ( The inflow direction of the gas-liquid two-phase state is a vertically downward direction.

As shown in FIG. 5C, it was found that the heat transfer characteristics can be maintained high when 0 ° ≦ attitude angle β ≦ 180 °. In particular, the heat transfer characteristics were found to be highest when the posture angle β was around 90 ° and around 180 °. Further, it has been found that when the posture angle β is smaller than 0 °, the heat transfer characteristics are rapidly deteriorated. That is, from this result, it was found that when 0 ° ≦ attitude angle β ≦ 180 °, the gas-liquid ratio of the low-temperature fluid distributed to each through hole 21 is substantially equal. Further, it has been found that when the posture angle β is around 90 ° and around 180 °, the gas-liquid ratio of the low-temperature fluid distributed to each through hole 21 can be made more equal.

(effect)
As described above, the heat exchanger 10 shown in Embodiment 1 of the present invention includes the high-temperature fluid flowing from the first inlet header 3 into the through hole of the first flat tube 1 and the second flat tube from the second inlet header 4. At least one of the low-temperature fluids flowing into the two through holes 21 is a gas-liquid two-phase fluid. The inflow direction of the fluid in the gas-liquid two-phase state from the inlet header to the flat tube is substantially horizontal or upward from the substantially horizontal direction. For this reason, even if the flow velocity decreases in the second inlet header 5 and the gas-liquid is separated into upper and lower parts, the inflow portion from the second inlet header 5 to the second flat tube 2 is always filled with the liquid phase. Therefore, only the liquid will selectively flow out to the second flat tube 2 on the upstream side, and the distribution of gas and liquid will not deteriorate. Therefore, the gas-liquid two-phase fluid can be distributed to each through hole so that the gas-liquid ratio is uniform, the temperature efficiency of the fluid can be maximized, and the pressure loss can be minimized. That is, the heat exchange performance of the heat exchanger 10 can be improved.
Thus, in the heat exchanger 10 shown in this Embodiment 1, a compact and high-performance heat exchanger can be obtained.

In addition, in this Embodiment 1, the case where the low temperature fluid which flows through the 2nd inlet header 5 will be in a gas-liquid two-phase state was demonstrated. When the high-temperature fluid flowing through the first inlet header 3 is in a gas-liquid two-phase state, the inflow direction of the high-temperature fluid flowing from the first inlet header 3 into the through hole of the first flat tube 1 is made substantially horizontal. The same effect can be obtained.

Embodiment 2. FIG.
The configuration of the heat exchanger 10 shown in the first embodiment is merely an example. For example, the heat exchanger 10 may be configured as follows. In the following description, differences from the heat exchanger 10 according to Embodiment 1 will be mainly described.

FIG. 6 is a side view showing an example of a heat exchanger according to Embodiment 2 of the present invention.
In the heat exchanger 10 shown in FIG. 6A, the bent portion 2b of the second flat tube 2 has a substantially U-shaped cross section. That is, the bending part 2b which connects the inflow part 2a of the 2nd flat tube 2 and the heat exchange part 2c is arrange | positioned so that it may get over the 1st exit header 4 into which a high temperature fluid flows. Moreover, the bending part 2b which connects the heat exchange part 2c and the outflow part 2d of the 2nd flat tube 2 is arrange | positioned so that it may get over the 1st inlet header 3 into which a high temperature fluid flows.

The heat exchanger 10 configured in this manner is compact because the height in the stacking direction of the

flat tubes

1 and 2 can be suppressed in addition to the effects of the first embodiment.

In addition, the second flat tube 2 of the heat exchanger 10 shown in FIG. 6B is reverse in the bending direction between the end on the second inlet header 5 side and the end on the second outlet header 6 side. ing. Moreover, the 1st flat tube 1 is provided with the inflow part 1a, the heat exchange part 1c, the outflow part 1d, and the bending part 1b. The inflow portion 1a is connected to the first inlet header 3, and the flow path is substantially horizontal. The outflow portion 1d is connected to the first outlet header 4, and the flow path is substantially horizontal. The heat exchanging portion 1c and the heat exchanging portion 2c of the second flat tube 2 are laminated so that their flat surfaces are in contact with each other. The bent portion 1b connects between the inflow portion 1a and the heat exchange portion 1c and between the heat exchange portion 1c and the outflow portion 1d. The bending direction of the end portion on the first inlet header 3 side of the first flat tube 1 is the same as the bending direction of the end portion on the second outlet header 6 side of the second flat tube 2. The bending direction of the end portion on the first outlet header 4 side of the first flat tube 1 is the same as the bending direction of the end portion on the second inlet header 5 side of the second flat tube 2.

In the heat exchanger 10 configured as described above, in addition to the effect of the first embodiment, when a plurality of heat exchangers 10 are installed, the installation space in the height direction can be made compact. That is, in order to increase the heat exchange capability, when installing a plurality of heat exchangers 10 stacked in the stacking direction of the

flat tubes

1 and 2, while preventing interference between the

headers

3, 4, 5 and 6, The clearance in the height direction of the heat exchanger 10 can be reduced.

In addition, the heat exchanger 10 shown in FIG. 6C is provided with a second flat tube below the first flat tube 1 in addition to the first flat tube 1. The 2nd flat tube 2A arrange | positioned above the 1st flat tube 1 is equipped with inflow part 2Aa, heat exchange part 2Ac, outflow part 2Ad, and bending part 2Ab. The inflow portion 2Aa is connected to the second inlet header 5A, and the flow path is substantially horizontal. The outflow portion 2Ad is connected to the second outlet header 6A, and the flow path is substantially horizontal. Heat exchange part 2Ac and 1st flat tube 1 are laminated so that a mutually flat surface may contact. The bent portion 2Ab connects between the inflow portion 2Aa and the heat exchange portion 2Ac and between the heat exchange portion 2Ac and the outflow portion 2Ad. The end of the second flat tube 2A is bent so as to ride over the first inlet header 3 and the first outlet header 4.

The second flat tube 2B disposed below the first flat tube 1 includes an inflow portion 2Ba, a heat exchange portion 2Bc, an outflow portion 2Bd, and a bent portion 2Bb. The inflow portion 2Ba is connected to the second inlet header 5B, and the flow path is substantially horizontal. The outflow portion 2Bd is connected to the second outlet header 6B, and the flow path is substantially horizontal. Heat exchange part 2Bc and 1st flat tube 1 are laminated so that a mutual flat surface may contact. The bent portion 2Bb connects between the inflow portion 2Ba and the heat exchange portion 2Bc and between the heat exchange portion 2Bc and the outflow portion 2Bd. The end of the second flat tube 2B is bent so as to go below the first inlet header 3 and the first outlet header 4.

Two second

flat tubes

2A and 2B are arranged with respect to one first flat tube 1, such as when heat exchange capacity is increased or heat transfer / flow characteristics of the second flat tube 2 are optimized. There is a case. In the heat exchanger 10 configured as described above, the outflow direction when the low-temperature fluid in the gas-liquid two-phase state flows out into the through hole 21 of the second flat tube 2A is substantially horizontal. Moreover, in the heat exchanger 10 comprised in this way, the outflow direction when the low-temperature fluid of a gas-liquid two-phase state flows out into the through-hole 21 of the 2nd flat tube 2B is substantially horizontal. For this reason, similarly to Embodiment 1, the gas-liquid ratio of the low-temperature fluid distributed to each through hole 21 can be made equal, and the compact and high-performance heat exchanger 10 can be obtained.

Embodiment 3 FIG.
The heat exchanger 10 of Embodiment 1 or Embodiment 2 is mounted on a refrigerating and air-conditioning apparatus such as an air conditioner, a hot water storage apparatus, and a refrigerator. Below, an example of the refrigerating air-conditioner which mounts the heat exchanger 10 of Embodiment 1 or Embodiment 2 is demonstrated.

FIG. 7 is a refrigerant circuit diagram illustrating an example of a refrigerating and air-conditioning apparatus according to Embodiment 3 of the present invention.
The refrigerating and air-conditioning apparatus shown in FIG. 7 has a first refrigerant circuit in which a first compressor 30, a first radiator 31, a first decompressor 32, and a first cooler 33 are sequentially connected by piping. The first refrigerant circuit is configured so that the first refrigerant, which is a high-temperature fluid, circulates and operates in a vapor compression refrigeration cycle. Further, the heat exchanger 10 is disposed between the first radiator 31 of the first refrigerant circuit and the first pressure reducing device 32, and the first inlet header 3 of the heat exchanger 10 is connected to the first radiator 31. The first outlet header 4 is connected to the first pressure reducing device 32.

In addition, this refrigeration air conditioner has a second refrigerant circuit in which the heat exchanger 10, the second compressor 40, the second radiator 41, and the second decompression device 42 are connected in order by piping. The second outlet header 6 of the heat exchanger 10 is connected to the second compressor 40, and the second inlet header 5 is connected to the second decompression device 42. The second refrigerant circuit is configured so that the second refrigerant, which is a low-temperature fluid, circulates and operates in a vapor compression refrigeration cycle. As the first refrigerant and the second refrigerant, refrigerants such as carbon dioxide, HFC refrigerant, HC refrigerant, HFO refrigerant, and ammonia are used. In the third embodiment, carbon dioxide is used as the first refrigerant.

The first refrigerant is compressed by the first compressor 30 and discharged as a high-temperature and high-pressure supercritical fluid. The 1st refrigerant | coolant used as the high temperature / high pressure supercritical fluid is sent to the 1st heat radiator 31, heat exchanges with air etc. in the 1st heat radiator 31, temperature falls, and it becomes a high pressure supercritical fluid. The first refrigerant, which has become a high-pressure supercritical fluid, is cooled by the heat exchanger 10 and the temperature is lowered. Then, the first refrigerant flows into the first decompression device 32 and is decompressed to change into a low-temperature and low-pressure gas-liquid two-phase flow state. Then, it is sent to the first cooler 33. The first refrigerant in a low-temperature and low-pressure gas-liquid two-phase flow state is evaporated by exchanging heat with air or the like in the first cooler 33 and returns to the first compressor 30.

On the other hand, the second refrigerant is compressed by the second compressor 40 and discharged as high-temperature and high-pressure steam. The second refrigerant that has become high-temperature and high-pressure vapor is sent to the second radiator 41, and heat exchange with the air or the like is performed by the second radiator 41 to lower the temperature, and become a high-pressure liquid. The second refrigerant that has become a high-pressure liquid is decompressed by the second decompression device 42, changes to a low-temperature gas-liquid two-phase flow state, and is sent to the heat exchanger 10. The second refrigerant in the low-temperature gas-liquid two-phase flow state is heated by the heat exchanger 10 to become steam and returns to the second compressor 40.

In the refrigeration air conditioner configured as described above, it is possible to ensure a large degree of supercooling of the refrigerant that has flowed out of the first radiator 31, and to greatly improve the efficiency of the refrigeration air conditioner.
Even when an HFC refrigerant, HC refrigerant, HFO refrigerant, or ammonia is used as the first refrigerant flowing through the first refrigerant circuit, a large degree of supercooling of the refrigerant that has flowed out of the first radiator 31 is ensured. This improves the efficiency of the refrigeration air conditioner. When the first refrigerant in the first refrigerant circuit is carbon dioxide and radiates heat at a critical point or higher, the efficiency of the refrigeration air conditioner is particularly improved.
In the third embodiment, the second refrigerant circuit is a vapor compression refrigeration cycle. However, the second refrigerant is brine (antifreeze) such as water or ethylene glycol aqueous solution, and the second compressor 40 is pumped. You may comprise.

FIG. 8 is a refrigerant circuit diagram illustrating another example of the refrigerating and air-conditioning apparatus according to Embodiment 3 of the present invention.
The refrigeration air conditioner shown in FIG. 8 omits the first radiator 31 from the configuration of the refrigeration air conditioner shown in FIG. 7, and exchanges all heat of the first refrigerant that is high-temperature and high-pressure steam discharged from the first compressor 30. It is cooled by the vessel 10. That is, the refrigeration air conditioner shown in FIG. 8 is a so-called secondary loop type refrigeration air conditioner. In this case, the heat exchanger 10 is used as the first radiator 31. In the refrigeration air conditioner shown in FIG. 8, the necessary heat exchange amount is increased in the heat exchanger 10, and the volume ratio in the entire refrigeration air conditioner is larger than that in the case where the first radiator 31 is provided. By making the heat exchanger 10 compact, the effect of making the entire refrigeration air conditioner compact is further enhanced.

FIG. 9 is a refrigerant circuit diagram illustrating still another example of the refrigerating and air-conditioning apparatus according to Embodiment 3 of the present invention.
The refrigeration air conditioner shown in FIG. 9 includes a refrigerant circuit in which a first compressor 30, a first radiator 31, a first decompressor 32, and a first cooler 33 are connected in order. Further, the refrigeration air conditioner shown in FIG. 9 includes a bypass pipe 52. One end of the bypass pipe 52 is connected between the first radiator 31 and the first pressure reducing device 32, and the other end is an injection port 53 provided in the middle of the refrigerant compression process in the first compressor 30, or here Then, although not shown, it is connected between the compressor 30 and the first cooler 33. The heat exchanger 10 is disposed between the first heat radiator 31 and the first pressure reducing device 32 in the refrigerant circuit and at a position in the middle of the bypass pipe 52. In the heat exchanger 10, the first inlet header 3 and the first radiator 31 are connected, and the first outlet header 4 and the first pressure reducing device 32 are connected. Further, the heat exchanger 10 is connected to the second inlet header 5 and the bypass pressure reducing device 51, and is connected to the second outlet header 6 and the injection port 53, or although not shown here, the compressor 30 and the first cooler 33. Are connected.

The refrigerant (low-temperature fluid) decompressed by the bypass decompression device 51 changes to a low-temperature gas-liquid two-phase flow state, and exchanges heat with the refrigerant (high-temperature fluid) flowing out from the first radiator 31 by the heat exchanger 10. It is sent to the injection port 53 of the first compressor 30. In the refrigerating and air-conditioning apparatus shown in FIG. 9, refrigerants such as HFC refrigerant, HC refrigerant, HFO refrigerant, ammonia, and carbon dioxide are used.

Also in the refrigeration air conditioner configured as described above, it is possible to ensure a large degree of supercooling of the refrigerant that has flowed out of the first radiator 31, and to greatly improve the efficiency of the refrigeration air conditioner.

In the refrigeration air conditioner shown in FIG. 9, the higher the saturation temperature (vapor-liquid equilibrium temperature) of the low-temperature fluid flowing from the heat exchanger 10 into the injection port 53, the higher the efficiency of the first compressor 30 and the required Power can be reduced. As shown in FIG. 9, when the outlet of the first radiator 31 is cooled, particularly when the outside air temperature is high and the temperature of the high-temperature fluid at the outlet of the first radiator 31 is relatively high, The temperature difference can be sufficiently large. For this reason, the temperature of the low-temperature fluid flowing into the injection port 53 can be maintained high, and the high efficiency of the first compressor 30 can be ensured.

In addition, when the other end of the bypass pipe 52 is connected between the first compressor 30 and the first cooler 33, the first effect is achieved without reducing the refrigeration effect as compared with the case where the heat exchanger 10 is not used. The flow rate of the refrigerant flowing through the cooler 33 can be reduced. In particular, when the piping length between the first compressor 30 and the first cooler 33 is long, it is possible to suppress a decrease in performance due to an increase in pressure loss, which is useful.

As described above, by mounting the compact and high-performance heat exchanger 10, it is possible to obtain a compact refrigeration air conditioner while having the above-described effects.

Embodiment 4 FIG.
In the first embodiment and the second embodiment, the first flat tube 1 through which the high-temperature fluid flows and the second flat tube 2 through which the low-temperature fluid flows are configured separately, and the first flat tube 1 and the second flat tube 2 are formed separately. The heat exchanger 10 in which the flat surfaces of the tube 2 are joined together by brazing or the like and laminated together has been described. That is, in the first embodiment and the second embodiment, the heat exchanger 10 is described in which the refrigerant flow path through which the high-temperature fluid flows and the refrigerant flow path through which the low-temperature fluid flows are formed as separate parts. However, the heat exchanger 10 may be configured by forming the refrigerant flow path through which the high-temperature fluid flows and the refrigerant flow path through which the low-temperature fluid flows in the same component (that is, the first flow path according to the present invention). Part and the second flow path part may be integrally formed). And you may mount the heat exchanger 10 comprised in this way in the refrigerating air conditioner as shown in Embodiment 3. FIG. In the fourth embodiment, items that are not particularly described are the same as those in the first to third embodiments.

FIG. 10 is a structural diagram of a heat exchanger according to Embodiment 4 of the present invention. Among these, Fig.10 (a) is a perspective view of the heat exchanger 10, and FIG.10 (b) is A arrow view of Fig.10 (a).
As shown in FIG. 10, in the main body 110 of the heat exchanger 10 according to the fourth embodiment, a plurality of first refrigerant flow paths 101 a through which a first refrigerant (for example, high-temperature fluid) flows are, for example, in the longitudinal direction ( It is formed penetrating in the vertical direction of FIG. And these 1st refrigerant | coolant flow paths 101a are arrange | positioned in parallel, and the 1st refrigerant | coolant path | pass 101 is comprised. The main body 110 is formed with a plurality of second refrigerant flow paths 102a through which a second refrigerant (for example, low-temperature fluid) flows, for example, penetrating in the longitudinal direction (vertical direction in FIG. 10). These second refrigerant flow paths 102 a are arranged in parallel to constitute the second refrigerant path 102. The first refrigerant path 101 and the second refrigerant 102 are arranged such that the juxtaposed direction of the first refrigerant channel 101a and the juxtaposed direction of the second refrigerant channel 102a are aligned. In the heat exchanger 10 shown in FIG. 10, the first refrigerant path 101 (that is, the first refrigerant flow path 101a) and the second refrigerant path 102 (that is, the second refrigerant flow path 102a) are arranged vertically. .
Here, “aligning” does not mean that the juxtaposed direction of the first refrigerant flow path 101a and the juxtaposed direction of the second refrigerant flow path 102a are strictly parallel. It shows that the direction is substantially aligned. For this reason, even if the juxtaposed direction of the first refrigerant channel 101a and the juxtaposed direction of the second refrigerant channel 102a are slightly inclined, in the fourth embodiment, the juxtaposed direction of both is “aligned”. Express.

That is, in the fourth embodiment, the first refrigerant path 101 and the second refrigerant path 102 are integrally formed. The main body 110 in which the first refrigerant path 101 and the second refrigerant path 102 are formed is formed of, for example, aluminum or aluminum alloy, copper or copper alloy, steel, or stainless alloy, and is manufactured by extrusion or pultrusion molding or the like. Is done.

In addition, a second inlet communication hole 105a that communicates with all the second refrigerant flow paths 102a is formed along one of the two ends of the main body 110 in the refrigerant flow direction along the direction in which the second refrigerant flow paths 102a are juxtaposed. Has been. On the other side, second outlet communication holes 106a communicating with all the second refrigerant flow paths 102a are formed along the parallel direction of the second refrigerant flow paths 102a. That is, in the heat exchanger 10 shown in FIG. 10, the second inlet communication hole 105a and the second outlet communication hole 106a are horizontally arranged.

Similarly, all the first refrigerant flow paths 101a are arranged along the direction in which the first refrigerant flow paths 101a are arranged on both sides of the main body 110 in the refrigerant flow direction on the side where the second outlet communication holes 106a are formed. A first inlet communication hole 103a communicating with the first inlet hole 103a is formed. Further, on both sides of the main body 110 in the refrigerant flow direction on the side where the second inlet communication holes 105a are formed, all the first refrigerant flow paths 101a are arranged along the parallel arrangement direction of the first refrigerant flow paths 101a. A first outlet communication hole 104a that communicates is formed. That is, in the heat exchanger 10 shown in FIG. 10, the first inlet communication hole 103a and the first outlet communication hole 104a are horizontally arranged.

Furthermore, the first inlet communication hole 103a and the second outlet communication hole 106a are formed slightly shifted in the refrigerant flow direction of the first refrigerant channel 101a (in other words, the second refrigerant channel 102a). Further, the first outlet communication hole 104a and the second inlet communication hole 105a are formed with a slight shift in the refrigerant flow direction of the first refrigerant flow path 101a (in other words, the second refrigerant flow path 102a).

In addition, the penetration direction of the first inlet communication hole 103a and the first outlet communication hole 104a is not necessarily perpendicular to the direction of each first refrigerant flow path 101a. Further, the penetrating direction of the second inlet communication hole 105a and the second outlet communication hole 106a is not necessarily perpendicular to the direction of the second refrigerant channel 102a.

In addition, one end of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a is opened, and the first inlet connection so as to communicate with the outside respectively. The pipe 103, the first outlet connecting pipe 104, the second inlet connecting pipe 105, and the second outlet connecting pipe 106 are connected. The other ends of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are closed by a sealing member or the like.
In FIG. 10, the opening (or closing) side end portions of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are all on the same side. Yes. However, the opening (or closing) side end portions of the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second outlet communication hole 106a are limited to the positions shown in FIG. Instead, each communication hole need not be on the same side as long as one end is opened and the other end is closed.

In addition, both ends of the plurality of first refrigerant channels 101a and second refrigerant channels 102a formed so as to penetrate in the longitudinal direction of the main body 110 are sealed by pinching or the like or sealed by a sealing member (Not shown).

Here, the heat exchanger 10 according to the fourth embodiment is assumed to be used in a posture in which a low-temperature fluid and a high-temperature fluid flow in the vertical direction as shown in FIG. Further, in the heat exchanger 10 according to the fourth embodiment, the low-temperature fluid in the gas-liquid two-phase state flows through each second refrigerant flow in the second refrigerant path via the second inlet connection pipe 105 and the second inlet communication hole 105a. This is assumed to flow into the path 102a. For this reason, the heat exchanger 10 according to the fourth embodiment is based on the knowledge obtained by the experiments shown in FIGS. 3 to 5 of the first embodiment, that is, the above-described attitude angles α, β excellent in heat transfer characteristics. , Γ, the second inlet communication hole 105a is arranged at the following position.

That is, when the second inlet communication hole 105a is observed in the central axis direction of the second inlet communication hole 105a, the central axis of the second inlet communication hole 105a is the second inlet communication hole 105a and the second refrigerant path 102 (that is, , A position that coincides with a connection portion with each second refrigerant flow path 102a), or a position that is farther from the first refrigerant path 101 (that is, each first refrigerant flow path 101a) than the connection portion.
As a result, in the heat exchanger 10 according to the fourth embodiment, the second flow path portion 102 and the second inlet header 5 are set to a posture angle α of 0 ° ≦ α <110 ° (in the same direction as FIG. 3). When positive, the connection is made at −110 ° <α ≦ 0).

The first refrigerant path 101, the second refrigerant path 102, the first inlet communication hole 103a, the first outlet communication hole 104a, the second inlet communication hole 105a, and the second inlet communication hole 106a are the “first flow” of the present invention. It corresponds to a “channel portion”, “second flow path portion”, “first inlet header”, “first outlet header”, “second inlet header”, and “second outlet header”.

Next, the heat exchange operation between the high-temperature fluid and the low-temperature fluid in the heat exchanger 10 according to Embodiment 4 will be described with reference to FIG.

The high-temperature fluid flows into the first inlet communication hole 103a through the first inlet connection pipe 103, flows in the order of the first refrigerant path 101, and the first outlet communication hole 104a, and then passes through the first outlet connection pipe 104. leak. On the other hand, the low-temperature fluid flows into the second inlet communication hole 105a through the second inlet connection pipe 105 in a gas-liquid two-phase state, and flows in the order of the second refrigerant path 102 and the second outlet communication hole 106a. And flows out from the second outlet connecting pipe 106. At this time, heat exchange is performed between the high-temperature fluid flowing through the first refrigerant path 101 and the low-temperature fluid flowing through the second refrigerant path 102 in a counterflow through a partition between the refrigerant paths.

As described above, in the heat exchanger 10 configured as in Embodiment 4, when the second inlet communication hole 105a is observed in the central axis direction of the second inlet communication hole 105a, the second inlet communication hole 105a The central axis corresponds to a connection portion between the second inlet communication hole 105a and the second refrigerant path 102 (that is, each second refrigerant flow path 102a), or the first refrigerant path 101 (that is, the connection portion). The first refrigerant flow path 101a) is away from each other. Accordingly, the posture angle α when the low-temperature refrigerant in the gas-liquid two-phase state flows into the second refrigerant path 102 from the second inlet communication hole 105a is 0 ° ≦ α <110 °. For this reason, the low-temperature refrigerant in the gas-liquid two-phase state is easily distributed to each second refrigerant flow path 102a of the second refrigerant path 102 at a substantially equal gas-liquid ratio, and the heat exchanger 10 with stable performance is obtained.

As can be seen from the first embodiment, when the arrow direction in FIG. 10B is a positive direction, when 80 ° <α <100 °, the distribution characteristics of the gas phase component and the liquid phase component of the low-temperature fluid Is most preferred. Then, the distance between the adjacent first refrigerant path 101 and the second refrigerant path 102 can be reduced. For this reason, when the direction of the arrow in FIG. 10B is a positive direction, the second inlet communication hole 105a is formed so as to satisfy 80 ° <α <100 °. And the performance of the heat exchanger 10 can be further improved.

Moreover, the following various effects can also be acquired by comprising the 1st refrigerant path 101 and the 2nd refrigerant path 102 as integral in the main body 110. FIG.

First, when the flow path through which the high-temperature fluid circulates and the flow path through which the low-temperature refrigerant circulate are formed as separate parts, the heat resistance generated at the joint surfaces of these parts is suppressed, and the heat exchange performance of the heat exchanger 10 is reduced. Can be improved.

In addition, since the first inlet communication hole 103a and the first outlet communication hole 104a are provided inside the main body 110 of the heat exchanger 10, it is not necessary to provide a separate header pipe for connecting to the first refrigerant path 101. The heat exchanger 10 can be made compact and the manufacturing process can be simplified. The same applies to the second inlet communication hole 105a and the second outlet communication hole 106a for the second refrigerant path 102.

Furthermore, since the first inlet communication hole 103a and the second outlet communication hole 106a, and the first outlet communication hole 104a and the second inlet communication hole 105a are formed slightly shifted in the flow direction of each fluid, Compared with the case where it does not shift, the distance between the adjacent first refrigerant path 101 and the second refrigerant path 102 can be reduced, and the heat exchanger 10 can be made compact.

In the heat exchanger 10 according to the fourth embodiment, as shown in FIG. 10, the first refrigerant flow path 101a and the second refrigerant flow path 102a have rectangular cross-sectional shapes. The shape of the cross section is not limited to a rectangle. The cross sections of the first refrigerant flow path 101a and the second refrigerant flow path 102a may be formed in a polygonal shape, for example, or may be circular in order to improve pressure resistance. Of course, the cross sections of the first refrigerant flow path 101a and the second refrigerant flow path 102a may be long holes or ellipses. In this case, it goes without saying that the flow path cross section of the first refrigerant flow path 101a and the flow path cross section of the second refrigerant flow path 102a need not have the same shape. Furthermore, in order to improve the heat transfer performance, a groove may be provided on the inner surface of the first refrigerant channel 101a or the second refrigerant channel 102a to increase the heat transfer area. In this case, if this groove is processed at the same time as extrusion molding or pultrusion molding of the main body 10, the manufacturing operation can be simplified.

Further, in the heat exchanger 10 according to the fourth embodiment, the number of the first refrigerant flow paths 101a of the first refrigerant path 101 and the second refrigerant flow paths 102a of the second refrigerant path 102 is set as shown in FIG. Although the number is the same, it is not limited to this. That is, different numbers are used so that the heat exchanger 10 has a high heat transfer performance, a low pressure loss, and a suitable heat exchanger 10 according to the operating conditions or flow property values of the high temperature fluid and the low temperature fluid in the heat exchanger 10. It is good.

In addition, the high-temperature fluid flowing through the first refrigerant path 101 and the low-temperature fluid flowing through the second refrigerant path 102 are assumed to perform heat exchange in a counterflow, but are not limited thereto. It is good also as what implements heat exchange as a parallel flow. For example, if the high temperature fluid flows in from the first inlet connecting pipe 103 and the low temperature fluid flows in from the second outlet connecting pipe 106, the high temperature fluid and the low temperature fluid become parallel flows.

In addition, in FIG. 10, the heat exchanger 10 used in a posture in which the low-temperature fluid and the high-temperature fluid flow in the vertical direction has been described, but in the fourth embodiment in which the first refrigerant path 101 and the second refrigerant path 102 are integrally formed. The installation posture of the heat exchanger 10 is not limited to the posture shown in FIG.

FIG. 11 is a structural diagram showing another example of a heat exchanger according to Embodiment 4 of the present invention. Among these, Fig.11 (a) is a perspective view of the heat exchanger 10, and FIG.11 (b) is A arrow view of Fig.11 (a).
The heat exchanger 10 shown in FIG. 11 is assumed to be used in a posture in which a low-temperature fluid and a high-temperature fluid flow in the left-right direction (substantially horizontal direction). That is, in the heat exchanger 10 shown in FIG. 11, the first refrigerant path 101 (that is, the first refrigerant flow path 101a) and the second refrigerant path 102 (that is, the second refrigerant flow path 102a) are arranged horizontally. It is. The other configuration is the same as that of the heat exchanger 10 shown in FIG. 10, and has the same effect. 10 and FIG. 11 have the same function and operation, and thus description of the function and operation is omitted.

Also in the heat exchanger 10 configured as shown in FIG. 11, when the second inlet communication hole 105a is observed in the central axis direction of the second inlet communication hole 105a, the central axis of the second inlet communication hole 105a is The position corresponding to the connection portion between the two inlet communication holes 105a and the second refrigerant path 102 (that is, each second refrigerant flow path 102a), or the first refrigerant path 101 (that is, each first refrigerant than the connection portion). What is necessary is just to set it as the position away from the flow path 101a). Thereby, the attitude angle α when the low-temperature refrigerant in the gas-liquid two-phase state flows into the second refrigerant path 102 from the second inlet communication hole 105a can be set to 0 <α ≦ 90 °. For this reason, the low-temperature refrigerant in the gas-liquid two-phase state is easily distributed to each second refrigerant flow path 102a of the second refrigerant path 102 at a substantially equal gas-liquid ratio, and the heat exchanger 10 with stable performance is obtained. However, 80 ° <α <100 ° is most suitable as the distribution characteristic. However, in the case of the fourth embodiment, as α approaches 90 ° from 0 ° (that is, the central axis of the second inlet communication hole 105a). The distance between the first refrigerant path 101 and the second refrigerant path 102 that are adjacent to each other can be reduced as the distance between the first refrigerant path 101 and the second refrigerant path 102 increases. For this reason, it is sufficient that the posture angle α that can suppress the thermal resistance due to heat conduction and improve the performance is at least between 0 <α <90 °.

As shown in FIGS. 10 and 11, in the heat exchanger 10 according to the fourth embodiment, a low-temperature fluid in a gas-liquid two-phase state is caused to flow from the second outlet connection pipe 106 and the second inlet connection pipe. A usage pattern in which a low-temperature fluid flows out from 105 is also assumed. For this reason, when the second outlet communication hole 106a is observed in the central axis direction of the second outlet communication hole 106a, the central axis of the second outlet communication hole 106a is connected to the second outlet communication hole 106a and the second refrigerant path 102 ( That is, it is set to a position that coincides with a connection portion with each second refrigerant flow path 102a) or a position farther from the first refrigerant path 101 (that is, each first refrigerant flow path 101a) than the connection portion.

DESCRIPTION OF SYMBOLS 1 1st flat tube, 1a inflow part, 1b bending part, 1c heat exchange part, 1d outflow part, 2nd flat tube, 2a inflow part, 2b bending part, 2c heat exchange part, 2d outflow part, 2A 2nd flat Pipe, 2Aa inflow part, 2Ab bent part, 2Ac heat exchange part, 2Ad outflow part, 2B second flat tube, 2Ba inflow part, 2Bb bent part, 2Bc heat exchange part, 2Bd outflow part, 3 first inlet header, 4th 1 outlet header, 5 second inlet header, 5A second inlet header, 5B second inlet header, 6 second outlet header, 6A second outlet header, 6B second outlet header, 10 heat exchanger, 21 through hole, 30 1st compressor, 31 1st radiator, 32 1st decompression device, 33 1st cooler, 40 2nd compressor, 41 2nd radiator, 42 2nd decompression device, 52 bypass piping, 53 injection port, 101 First 1 refrigerant path, 101a first refrigerant flow path, 102 second refrigerant path, 102a second refrigerant flow path, 103 first inlet connection pipe, 103a first inlet communication hole, 104 first outlet connection pipe, 104a first outlet communication Hole, 105 second inlet connecting pipe, 105a second inlet connecting hole, 106 second outlet connecting pipe, 106a second outlet connecting hole, 110 main body.

Claims

A first flow path portion having a plurality of through holes through which a high-temperature fluid flows;
A second flow path portion having a plurality of through holes through which a low-temperature fluid flows;
A tubular first inlet header connected to one end of the first flow path portion;
A tubular first outlet header connected to the other end of the first flow path portion;
A tubular second inlet header connected to one end of the second flow path portion;
A tubular second outlet header connected to the other end of the second flow path portion;
With
The first flow path part and the second flow path part are arranged so as to be able to exchange heat via a partition wall provided between them.
At least one of the high temperature fluid flowing from the first inlet header into the through hole of the first flow path portion and the low temperature fluid flowing from the second inlet header to the through hole of the second flow path portion is gas-liquid. A two-phase fluid,
The inflow direction of the fluid in the gas-liquid two-phase state from the inlet header to the flow path section is −110 ° <attitude angle α <110 °, where the angle α from the vertical direction to the downward direction is positive. Heat exchanger.
Assuming that the inflow direction of the fluid in the gas-liquid two-phase state from the inlet header to the flow path is positive when the angle α from the vertical direction to the downward direction is positive, −80 ° <attitude angle α <−100 ° or 80 ° <attitude The heat exchanger according to claim 1, wherein the angle α <100 °.
2. The heat exchanger according to claim 1, wherein an inflow direction of the fluid in the gas-liquid two-phase state from the inlet header to the flow path is substantially horizontal or upward from the substantially horizontal. .
2. The heat according to claim 1, wherein the inflow direction of the fluid in the gas-liquid two-phase state from the inlet header to the flow path is in a positive range when the angle from the horizontal to the upward direction is positive. Exchanger.
The inflow direction from the inlet header to the flow path portion of the gas-liquid two-phase fluid is substantially horizontal when the angle from the horizontal to the upward direction is positive. Heat exchanger.
The end of the flow path connected to the inlet header through which the gas-liquid two-phase fluid flows is bent inside the inlet header through which the gas-liquid two-phase fluid flows. The heat exchanger according to any one of claims 1 to 5.
The end portion of the flow path connected to the inlet header through which the gas-liquid two-phase fluid flows is bent outside the inlet header through which the gas-liquid two-phase fluid flows. The heat exchanger according to any one of claims 1 to 5.
A plurality of through-holes through which a high-temperature fluid flows are arranged in parallel and arranged vertically or horizontally;
A plurality of through-holes through which a low-temperature fluid flows are arranged side by side and arranged vertically or horizontally; and
A tubular first inlet header connected to one end of the first flow path portion and disposed horizontally;
A tubular first outlet header connected to the other end of the first flow path portion and disposed horizontally;
A tubular second inlet header connected to one end of the second flow path portion and disposed horizontally;
A tubular second outlet header connected to the other end of the second flow path portion and disposed horizontally;
The first flow path part, the second flow path part, the first inlet header, the first outlet header, the second inlet header and the second outlet header are integrally formed,
The first flow path part and the second flow path part are arranged with the through-holes arranged in parallel so that heat exchange is possible via a partition wall provided between them.
At least one of the high temperature fluid flowing from the first inlet header into the through hole of the first flow path portion and the low temperature fluid flowing from the second inlet header to the through hole of the second flow path portion is gas-liquid. A two-phase fluid,
In the state where the inlet header through which the gas-liquid two-phase fluid flows is observed in the central axis direction of the inlet header,
The central axis of the inlet header through which the fluid in the gas-liquid two-phase state flows coincides with the connection portion between the inlet header and the flow path portion connected to the inlet header, or the inlet header rather than the connection portion. A heat exchanger characterized in that the heat exchanger is located away from a flow path portion not connected to the heat exchanger.
A refrigerating and air-conditioning apparatus comprising the heat exchanger according to any one of claims 1 to 8.