JP2008180479A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of adjusting the dividing state of a refrigerant flow to heat exchange tubes. <P>SOLUTION: A refrigerant inlet header portion 1 and an intermediate header portion 2 are disposed at a front side of an upper header tank 31, and similarly, a refrigerant outlet header portion 3 and an intermediate header portion 4 are disposed at its rear side. The refrigerant inlet header portion 1 and the refrigerant outlet header portion 3 are positioned at the same side. Front and rear two heat exchange tube arrays 10, 11 are disposed between both of the upper and lower header tanks 31. The total heat exchange tubes 33 communicated with the intermediate header portion 2 of the upper header tank 31 in the rear-side heat exchange tube array 10 constitute a first heat exchange tube group 12 for allowing the refrigerant to flow from top down, and the total heat exchange tubes 33 communicated with the refrigerant outlet header portion 3 constitute a second heat exchange tube group 13 for allowing the refrigerant to flow from bottom up. A length of the refrigerant outlet header portion 3 is longer than a length of the intermediate header portion 4 of the rear-side header portion array 6. Cross-sectional areas of flow channels of the heat exchange tubes 33 are equal to each other, and the number of heat exchange tubes 33 of the second heat exchange tube group 13 is more than the number of heat exchange tubes 33 of the first heat exchange tube group 12. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

The present invention relates to a heat exchanger, and more particularly to a heat exchanger suitably used for an evaporator of a supercritical refrigeration cycle in which a supercritical refrigerant such as CO ₂ (carbon dioxide) is used.

  In this specification and claims, the term “supercritical refrigeration cycle” means a refrigeration cycle in which the refrigerant is in a supercritical state exceeding the critical pressure on the high pressure side, and “supercritical refrigerant” It shall mean a refrigerant used in a supercritical refrigeration cycle. Further, in this specification and claims, the upper, lower, left, and right sides of FIGS. 1 and 2 are referred to as the upper and lower sides and the left and right sides, respectively, and the downstream side of the air flowing in the ventilation gap between adjacent heat exchange tubes (in FIG. The direction indicated by arrow X) is the front, and the opposite side is the rear.

  For example, as a heat exchanger used in an evaporator of a supercritical refrigeration cycle used as a car air conditioner, the present applicant has previously made a pair of header tanks extending in the left-right direction and spaced apart in the vertical direction, A plurality of heat exchange pipes arranged in parallel between both header tanks and whose upper and lower ends are respectively connected to both header tanks, and a refrigerant inlet and a refrigerant outlet are formed in the upper header tank, The upper header tank is provided with two header part rows formed of two header parts arranged in the left-right direction at intervals in the front-rear direction, and one header part of the front header part row serves as a refrigerant inlet header part. In addition, the refrigerant inlet header portion leads to the refrigerant inlet, and one header portion on the same side as the refrigerant inlet header portion in the rear header portion row is a refrigerant outlet header portion. The refrigerant outlet communicates with the refrigerant outlet header part, the other header part of both header part rows of the upper header tank serves as an intermediate header part, and the inside of both intermediate header parts communicate with each other, so that the front and rear of the lower header tank On both sides, one intermediate header part is provided so as to straddle the two header parts of the front and rear header part rows of the upper header tank, and consists of a plurality of heat exchange tubes arranged in the left-right direction between the upper and lower header tanks. And two rows of heat exchange pipes are provided side by side in the front-rear direction, and both ends of the heat exchange pipe are connected to the upper and lower header tanks so as to communicate with the header part, and the refrigerant inlet header part is connected to the front side heat exchange pipe line. And a first heat exchange tube group consisting of a plurality of heat exchange tubes through which the refrigerant flows from top to bottom, and a plurality of heat exchange tubes which communicate with the intermediate header portion of the front header section row and through which the refrigerant flows from bottom to top Second heat exchange tube A first heat exchange tube group consisting of a plurality of heat exchange tubes that communicate with the intermediate header portion of the rear header portion row and from which the refrigerant flows from top to bottom, and a refrigerant outlet header. And a second heat exchange tube group comprising a plurality of heat exchange tubes through which the refrigerant flows from the bottom to the top, and the refrigerant flowing from the refrigerant inlet passes through all the heat exchange tubes and the header portion. A heat exchanger has been proposed which flows out from the refrigerant outlet and has the same total cross-sectional area of all the heat exchange tubes constituting each heat exchange tube group (see Patent Document 1).

  Generally, in an evaporator of a car air conditioner, the temperature of the blown air that has passed through the ventilation gap between adjacent heat exchange pipes is improved for the purpose of improving the comfort of the interior of a vehicle equipped with the car air conditioner. Although it is desirable to make it uniform in each part, for that purpose, it is necessary to adjust the refrigerant distribution state to each heat exchange pipe according to the wind velocity distribution of the air flowing through the ventilation gap between adjacent heat exchange pipes. .

However, as a result of intensive studies by the inventors, in the case of the heat exchanger described in Patent Document 1, the second heat exchange tube group of each heat exchange tube row, particularly the second outlet leading to the refrigerant outlet header portion of the rear heat exchange row. The pressure loss when the refrigerant flows through the heat exchange pipe of the heat exchange pipe group is considerably larger than the pressure loss when the refrigerant flows through the heat exchange pipe of the first heat exchange pipe group. As a result, the second heat exchange pipe group The amount of refrigerant flowing through the heat exchange tubes of the first heat exchange tube group is smaller than the amount of refrigerant flowing through the heat exchange tubes of the first heat exchange tube group. Therefore, the refrigerant distribution state to the heat exchange tubes of the first heat exchange tube group and the second heat exchange tube group of each heat exchange tube row is adjusted, and the inside of all heat exchange tubes of each heat exchange tube row is adjusted. There is a risk that it will be difficult to make the amount of flowing refrigerant uniform.
JP-A-2005-300135

  An object of the present invention is to provide a heat exchanger that solves the above-described problems and can adjust the refrigerant distribution state to the heat exchange tubes of each heat exchange tube row.

  In order to achieve the above object, the present invention comprises the following aspects.

1) A pair of header tanks extending in the left-right direction spaced apart in the vertical direction, and a plurality of heat exchanges arranged in parallel between both header tanks, with both upper and lower ends connected to both header tanks. A header portion row comprising a plurality of header portions arranged in the left-right direction in either one of the upper and lower header tanks, and having a refrigerant inlet and a refrigerant outlet. Are provided in a plurality of rows at intervals in the front-rear direction, and header portions constituting each header portion row of the first header tank at a position corresponding to each header portion row of the first header tank in the other second header tank A plurality of header portions that are one less than the number of the header portions are provided so as to straddle two adjacent header portions of each header portion row of the first header tank, and a plurality of header portions arranged in the left-right direction between the upper and lower header tanks. heat The same number of heat exchange tube rows as the header portion row of the first header tank are arranged in the front-rear direction, and both ends of the heat exchange tube are connected to the upper and lower header tanks so as to communicate with the header portion. In each heat exchange tube row, a first heat exchange tube group consisting of a plurality of heat exchange tubes where the refrigerant flows from top to bottom, and a second heat exchange tube group consisting of a plurality of heat exchange tubes where the refrigerant flows from bottom to top In the heat exchanger in which the refrigerant flowing in from the refrigerant inlet passes through all the heat exchange pipes and the header part and flows out from the refrigerant outlet,
The first heat exchange in which the total flow cross-sectional area of all the heat exchange tubes constituting the last second heat exchange tube group located closest to the refrigerant outlet side is adjacent to at least one of the left and right sides of the second heat exchange tube group A heat exchanger that is larger than the total flow passage cross-sectional area of all the heat exchange tubes constituting the tube group.

  2) The total flow cross-sectional area of all the heat exchange tubes constituting the last second heat exchange tube group constitutes the first heat exchange tube group adjacent to at least one of the left and right sides of the second heat exchange tube group. The heat exchanger according to 1) above, which is 1.1 to 1.7 times larger than the total flow passage cross-sectional area of the total heat exchange pipe.

  3) The cross-sectional area of each heat exchange pipe is equal, and the number of heat exchange pipes constituting the last second heat exchange pipe group is adjacent to at least one of the left and right sides of the second heat exchange pipe group The heat exchanger according to 1) or 2), wherein the number of heat exchange tubes constituting the first heat exchange tube group is larger.

  4) The number of heat exchange tubes constituting the last second heat exchange tube group and the number of heat exchange tubes constituting the first heat exchange tube group adjacent to at least one of the left and right sides of the second heat exchange tube group The first heat exchange tube group in which the flow path cross-sectional area of each heat exchange tube constituting the last second heat exchange tube group is adjacent to at least one of the left and right sides of the second heat exchange tube group The heat exchanger as described in 1) or 2) above, which is larger than the flow path cross-sectional area of each heat exchange pipe constituting the heat exchanger tube.

  5) The upper header tank serves as the first header tank and the lower header tank serves as the second header tank. The upper header tank is provided with two header sections each having two header sections, and one of the front header sections. The header portion is a refrigerant inlet header portion, the refrigerant inlet is connected to the refrigerant inlet header portion, and one header portion on the same side as the refrigerant inlet header portion in the rear header portion row is the refrigerant outlet header portion. In addition, the refrigerant outlet is connected to the refrigerant outlet header part, the other header part of both header part rows of the upper header tank is an intermediate header part, and the inside of both intermediate header parts is mutually communicated, so that the lower header tank One intermediate header portion is provided on each of the front and rear sides so as to straddle the two header portions of the front and rear header portion rows of the upper header tank. The total heat exchange pipe leading to the header portion constitutes the last second heat exchange pipe group, and the length of the refrigerant outlet header portion is longer than the length of the intermediate header portion of the rear header portion row. The above-mentioned 1) or 2), in which the cross-sectional areas of the pipes are equal and the number of heat exchange pipes leading to the refrigerant outlet header part is greater than the number of heat exchange pipes leading to the intermediate header part of the rear header part row The described heat exchanger.

  6) The length of the intermediate header portion of the front header portion row of the upper header tank is longer than the length of the refrigerant inlet header portion, and the cross-sectional area of each heat exchange pipe is equal, and the front header portion of the upper header tank The total heat exchange pipes that lead to the middle header section of the row constitute the second heat exchange pipe group, and the number of heat exchange pipes that lead to the middle header section of the front header section row of the upper header tank is the heat that leads to the refrigerant inlet header section. The heat exchanger as described in 5) above, which is larger than the number of exchange tubes.

  7) The lower header tank becomes the first header tank and the upper header tank becomes the second header tank, and the lower header tank is provided with two header portion rows each having two header portions, and one of the front header portion rows. The header portion is a refrigerant inlet header portion, the refrigerant inlet is connected to the refrigerant inlet header portion, and one header portion on the same side as the refrigerant inlet header portion in the rear header portion row is the refrigerant outlet header portion. In addition, the refrigerant outlet is connected to the refrigerant outlet header part, the other header part of both header part rows of the lower header tank is an intermediate header part, and the inside of both intermediate header parts is mutually communicated, and the upper header tank One intermediate header section is provided on both the front and rear sides so as to straddle the two header sections of the front and rear header section rows of the lower header tank. The total heat exchange pipe leading to the intermediate header section of the second section constitutes the last second heat exchange pipe group, and the length of the intermediate header section of the rear header section of the lower header tank is longer than the length of the refrigerant outlet header section. The heat exchange tubes connected to the intermediate header portion of the rear header portion row of the lower header tank are equal in number to the heat exchanger tubes connected to the refrigerant outlet header portion. The heat exchanger according to 1) or 2), wherein the heat exchanger is larger than the number.

  8) The length of the refrigerant inlet header section of the lower header tank is longer than the length of the intermediate header section of the front header section row, and the cross-sectional area of each heat exchange pipe is equal, and the refrigerant inlet of the lower header tank The total heat exchange pipes that lead to the header portion constitute the second heat exchange pipe group, and the number of heat exchange pipes that lead to the refrigerant inlet header part of the lower header tank is the number of heat exchange pipes that lead to the intermediate header part of the front header part row. The heat exchanger as described in 7) above, which is larger than the number.

  9) Each header tank is composed of a tank forming member and a pipe connecting plate that covers the surface of the tank forming member facing the heat exchange pipe, and the tank forming member extends in the length direction of the header tank and is heated. The above-described 1)-having a hollow portion opened on the surface facing the exchange tube side, and the header portion is formed by closing the opening facing the heat exchange tube side of the hollow portion with the tube connecting plate The heat exchanger according to any one of 8).

  10) The tank forming member is composed of a first plate and a second plate interposed between the first plate and the pipe connecting plate, and the hollow portion of the header portion straddles the first plate and the second plate. The heat exchanger according to 9) above, wherein is formed.

  11) An outward bulging portion extending in the length direction of the first plate is formed in the first plate of the tank forming member, and the internal space of the outward bulging portion forms a part of the hollow portion of the header portion. The heat exchanger as described in 10) above.

  12) A supercritical refrigeration cycle equipped with a compressor, gas cooler, evaporator, decompressor, and intermediate heat exchanger that exchanges heat between the refrigerant coming out of the gas cooler and the refrigerant coming out of the evaporator, and using a supercritical refrigerant. A supercritical refrigeration cycle comprising the heat exchanger according to any one of 1) to 11) above.

  According to the heat exchanger of 1) above, the total flow cross-sectional area of all the heat exchange tubes constituting the last second heat exchange tube group located closest to the refrigerant outlet side is at least that of the second heat exchange tube group. When the refrigerant flows through the heat exchange pipe of the second heat exchange pipe group, the total flow passage area of the total heat exchange pipe constituting the first heat exchange pipe group adjacent to either the left or right side is larger. And the pressure loss when the refrigerant flows through the heat exchange pipe of the first heat exchange pipe group adjacent to the pressure loss of the first heat exchange pipe group are made uniform, and as a result, the amount of refrigerant flowing through the heat exchange pipes of both the second heat exchange pipe groups And the amount of refrigerant flowing through the heat exchange tubes of the first heat exchange tube group are made uniform. Therefore, the refrigerant distribution state to the heat exchange pipe of the first heat exchange pipe group and the heat exchange pipe of the second heat exchange pipe group of each heat exchange pipe row is adjusted to a suitable one for improving the heat exchange performance, It is possible to achieve a uniform flow state of the refrigerant to each heat exchange tube.

  According to the heat exchanger of 2), the effect of 1) is further improved.

  According to the heat exchangers of 3) and 4) above, the total flow cross-sectional area of all the heat exchange tubes constituting the last second heat exchange tube group located closest to the refrigerant outlet side is calculated as the second heat exchange tube. It can be relatively easily made larger than the total flow path cross-sectional area of all the heat exchange tubes constituting the first heat exchange tube group adjacent to at least one of the left and right sides of the group.

  According to the heat exchanger of 5) above, the total flow cross-sectional area of all the heat exchange tubes constituting the second heat exchange tube group of the rear heat exchange tube row leading to the refrigerant outlet header portion of the upper header tank is Since it is larger than the total flow path cross-sectional area of all the heat exchange tubes constituting the first heat exchange tube group of the rear heat exchange tube row that leads to the intermediate header portion of the side header portion row, the rear heat exchange tube row The pressure loss when the refrigerant flows through the heat exchange pipe of the second heat exchange pipe group and the pressure loss when the refrigerant flows through the heat exchange pipe of the first heat exchange pipe group adjacent to the second heat exchange pipe group, As a result, the amount of refrigerant flowing through the heat exchange tubes of the second heat exchange tube group and the amount of refrigerant flowing through the heat exchange tubes of the first heat exchange tube group are made uniform. Therefore, the refrigerant distribution state to the heat exchange pipe of the first heat exchange pipe group and the heat exchange pipe of the second heat exchange pipe group in the rear heat exchange pipe row is adjusted to be suitable for improving the heat exchange performance. In addition, it is possible to make the flow distribution state of the refrigerant to each heat exchange pipe uniform.

  According to the heat exchanger of 6) above, in the heat exchanger of 5), all the heat exchanger tube rows constituting the second heat exchange tube group of the front heat exchange tube row leading to the intermediate header portion of the front header portion row of the upper header tank Since the total flow path cross-sectional area of the heat exchange pipe is larger than the total flow path cross-sectional area of all the heat exchange pipes constituting the first heat exchange pipe group of the front heat exchange pipe row leading to the refrigerant inlet header portion, Also in the front heat exchange tube row, the pressure loss when the refrigerant flows through the heat exchange tubes of the second heat exchange tube group, and the pressure when the refrigerant flows through the heat exchange tubes of the first heat exchange tube group adjacent thereto. Loss is made uniform, and as a result, the amount of refrigerant flowing through the heat exchange tubes of the second heat exchange tube group and the amount of refrigerant flowing through the heat exchange tubes of the first heat exchange tube group are made uniform. Therefore, the refrigerant diversion state to the heat exchange pipe of the first heat exchange pipe group and the heat exchange pipe of the second heat exchange pipe group in the front heat exchange pipe row is adjusted to a suitable one for improving the heat exchange performance, It is possible to achieve a uniform flow state of the refrigerant to each heat exchange tube.

  According to the heat exchanger of the above 7), the total flow path of all the heat exchange tubes constituting the second heat exchange tube group of the rear heat exchange tube row communicating with the intermediate header portion of the rear header portion row of the lower header tank Since the cross-sectional area is larger than the total flow cross-sectional area of all the heat exchange tubes constituting the first heat exchange tube group of the rear heat exchange tube row leading to the refrigerant outlet header portion, the rear heat exchange tube row The pressure loss when the refrigerant flows through the heat exchange pipe of the second heat exchange pipe group and the pressure loss when the refrigerant flows through the heat exchange pipe of the first heat exchange pipe group adjacent thereto are equalized. As a result, the amount of refrigerant flowing through the heat exchange tubes of the second heat exchange tube group and the amount of refrigerant flowing through the heat exchange tubes of the first heat exchange tube group are made uniform. Therefore, the refrigerant distribution state to the heat exchange pipe of the first heat exchange pipe group and the heat exchange pipe of the second heat exchange pipe group in the rear heat exchange pipe row is adjusted to be suitable for improving the heat exchange performance. In addition, it is possible to make the flow distribution state of the refrigerant to each heat exchange pipe uniform.

  According to the heat exchanger of the above 8), in the heat exchanger of the above 7), the total heat exchange tubes constituting the second heat exchange tube group of the front heat exchange tube row leading to the refrigerant inlet header portion of the lower header tank Since the total flow path cross-sectional area is larger than the total flow path cross-sectional area of the total heat exchange pipe constituting the first heat exchange pipe group of the front heat exchange pipe row leading to the intermediate header portion of the front header section row, Also in the front heat exchange tube row, the pressure loss when the refrigerant flows through the heat exchange tubes of the second heat exchange tube group, and the pressure when the refrigerant flows through the heat exchange tubes of the first heat exchange tube group adjacent thereto. Loss is made uniform, and as a result, the amount of refrigerant flowing through the heat exchange tubes of the second heat exchange tube group and the amount of refrigerant flowing through the heat exchange tubes of the first heat exchange tube group are made uniform. Therefore, the refrigerant diversion state to the heat exchange pipe of the first heat exchange pipe group and the heat exchange pipe of the second heat exchange pipe group in the front heat exchange pipe row is adjusted to a suitable one for improving the heat exchange performance, It is possible to achieve a uniform flow state of the refrigerant to each heat exchange tube.

  Embodiments of the present invention will be described below with reference to the drawings. In this embodiment, the heat exchanger according to the present invention is applied to an evaporator of a supercritical refrigeration cycle.

  In the following description, the term “aluminum” includes aluminum alloys in addition to pure aluminum. Moreover, the same code | symbol is attached | subjected to the same part and the same thing through all drawings, and the overlapping description is abbreviate | omitted.

Embodiment 1
This embodiment is shown in FIGS.

  1 to 3 show the overall configuration of an evaporator to which the present invention is applied, FIGS. 4 to 10 show the configuration of the main part of the evaporator, and FIG. 11 shows the flow of refrigerant in the evaporator of FIG.

1 to 3, an evaporator (30) of a supercritical refrigeration cycle using a supercritical refrigerant, for example, CO ₂ , is provided with two header tanks (31) (31) ( 32) and a plurality of flat heat exchange tubes (33) extending in the vertical direction and arranged in parallel with a space in the left-right direction between both header tanks (31) (32), and adjacent heat exchange tubes (33) The ventilation gap between the corrugated fins (34) disposed outside the heat exchange pipes (33) on both the left and right ends and brazed to the heat exchange pipes (33), and the corrugated fins on the left and right ends ( And an aluminum bear side plate (35) brazed to the corrugated fin (34). In this embodiment, the upper header tank (31) is referred to as a first header tank, and the lower header tank (32) is referred to as a second header tank.

  As shown in FIGS. 2 to 8, the first header tank (31) is formed of an aluminum tank forming member (36) and a brazing sheet having a brazing filler metal layer on both sides, here an aluminum brazing sheet, and the tank. A pipe connecting plate (37) brazed to the tank forming member (36) so as to cover the lower surface of the forming member (36). The tank forming member (36) is formed of a brazing sheet having a brazing filler metal layer on both sides, here an aluminum brazing sheet, and disposed on the upper side (outside), and a metal bear material, here A second plate (36B) made of aluminum bare material and interposed between the first plate (36A) and the pipe connection plate (37) and brazed to both plates (36A) (37). It is configured. In the first header tank (31), a header section row (5) composed of two header sections (1), (2), (3) and (4) formed so as to be arranged at intervals in the left-right direction. (6) is provided in two rows at intervals in the front-rear direction (see FIG. 1).

  Two outwardly bulging portions (39A) (39B) (39C) extending in the left-right direction on the front side portion and the rear side portion of the first plate (36A) of the tank forming member (36) of the first header tank (31), respectively. ) (39D) are formed at intervals in the left-right direction. Hereinafter, in this embodiment, the outer bulging portion (39A) of the front right portion is the first outer bulging portion, the outer bulging portion (39B) of the front left portion is the second outer bulging portion, and the rear The outward bulging portion (39C) in the right side portion is referred to as a third outward bulging portion, and the outward bulging portion (39D) in the rear left portion is referred to as a fourth outward bulging portion. The length in the left-right direction of the second outer bulge portion (39B) is longer than the length in the left-right direction of the first outer bulge portion (39A), and the length in the left-right direction of the third outer bulge portion (39C). The length is longer than the length in the left-right direction of the fourth outward bulging portion (39D). Further, the bulge height and width of each of the outward bulge portions (39A) to (39D) are equal. The opening of the first plate (36A) facing the lower side of the internal space (39a) (39b) (39c) (39d) of the first to fourth outward bulges (39A) to (39D) is the second plate. It is blocked by (36B). The first plate (36A) is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides.

  A plurality of through-tube insertion holes (41) that are long in the front-rear direction are formed in the front-rear side portions of the pipe connection plate (37), with a space in the left-right direction. The plurality of tube insertion holes (41) on the right side of the front row are formed in the left-right direction range of the first outer bulge portion (39A) of the first plate (36A), and the plurality of tube insertion holes on the left side of the front row (41) is formed within the range in the left-right direction of the second outer bulge portion (39B), and the plurality of tube insertion holes (41) on the right side of the rear row are formed on the third outer bulge portion (39C). The plurality of tube insertion holes (41) on the left side of the rear row are formed in the left-right range, and are formed in the left-right range of the fourth outward bulge portion (39D). In addition, the length of each tube insertion hole (41) is slightly longer than the width in the front-rear direction of each outward bulge portion (39A) to (39D), and both front and rear end portions of the tube insertion hole (41) are It protrudes outward from the front and rear side edges of the side bulges (39A) to (39D) (see FIG. 3). Also, the pipe connecting plate (37) protrudes upward and downward on both side edges, and the tip reaches the outer surface of the first plate (36A), and the first plate (36A) and the second plate (36B) A covering wall (42) covering the entire boundary is formed integrally, and is brazed to both the front and rear side surfaces of the first plate (36A) and the second plate (36B). A plurality of engaging portions (43) that engage with the outer surface of the first plate (36A) are integrally formed at the protruding end of each covering wall (42) at intervals in the left-right direction. ) Is brazed. The pipe connecting plate (37) is formed by pressing an aluminum brazing sheet having a brazing filler metal layer on both sides.

  The pipe insertion hole (41) of the pipe connection plate (37) is formed on the second plate (36B) of the tank forming member (36) of the first header tank (31), and the outward bulge portion of the first plate (36A). The same number of penetrating communication holes (44) that communicate with the internal spaces (39a) to (39d) of (39A) to (39D) are formed as many as the tube insertion holes (41). The communication hole (44) is slightly larger than the tube insertion hole (41). The plurality of tube insertion holes (41) on the right side of the front row of the pipe connection plate (37) are connected to the first outward expansion via the plurality of communication holes (44) on the right side of the front row of the second plate (36B). The plurality of tube insertion holes (41) on the left side of the front row are connected to the inner space (39a) of the outlet (39A), and the plurality of communication holes (44) on the right side of the front row of the second plate (36B) Through the inner space (39b) of the second outer bulge portion (39B), and the plurality of tube insertion holes (41) on the right side of the rear row are also provided on the right side of the rear row of the second plate (36B). The plurality of tube insertion holes (41) on the left side of the rear row are connected to the second plate (36B) through the communication hole (44) of the third outer bulge portion (39C). ) Through the inner space (39d) of the fourth outwardly bulging portion (39D) through a plurality of communication holes (44) in the left half of the rear side.

  All the communication holes (44) leading to the internal space (39a) of the first outer bulging portion (39A) of the first plate (36A) in the second plate (36B) of the tank forming member (36), the second outer All the communication holes (44) leading to the internal space (39b) of the side bulge portion (39B) and all the communication holes (44) leading to the internal space (39c) of the third outer bulge portion (39C) are Each of the second plates (36B) is communicated by a communicating portion (46) formed by cutting a central portion in the front-rear direction between communicating holes (44) adjacent in the left-right direction. And the communicating part which makes all the communicating holes (44) connected to the internal space (39a)-(39c) of the 1st-3rd outward bulging part (39A)-(39C) of a 1st plate (36A) communicate. (46) and the center part in the front-rear direction of the communication hole (44) (the part corresponding to the communication part (46) in the communication hole (44)), the second plate (36B) and the first plate (36A) Refrigerant circulation portions (40A), (40B), and (40C) that are connected to the inner spaces (39a) to (39c) of the first to third outer bulge portions (39A) to (39C) and in which the refrigerant flows in the left-right direction are formed. ing.

  Each communication hole (44) communicating with the internal space (39d) of the fourth outward bulge portion (39D) of the first plate (36A) in the second plate (36B), and the communication hole (44) in the left-right direction, Each communication hole (44) that is in a corresponding position and communicates with the internal space (39b) of the second outward bulge portion (39B) is a communication hole (44) adjacent in the front-rear direction in the second plate (36B). It is made to communicate by the refrigerant | coolant turn communication part (45) formed by cutting off the part between these, Thereby, the 2nd and 4th outward bulge part (39B) (39D) of a 1st plate (36A) The internal spaces (39b) and (39d) communicate with each other. The second plate (36B) is formed by pressing an aluminum bare material.

  Two right protrusions (36a) (36b) (37a) are formed at the right ends of the three plates (36A), (36B), and (37) at intervals in the front-rear direction. The second plate (36B) is formed with a notch (47) that leads from the front end of the two front and rear outward projections (36b) to the communication hole (44) at the right end, so that the first header tank ( 31) on the right end of the second plate (36B) on the right end of the second plate (36B) and the refrigerant communicating with the internal space (39a) of the first outwardly bulging portion (39A) of the first plate (36A) Refrigerant outlet communicating with the inlet (48) and the internal space (39c) of the third outer bulge part (39C) of the first plate (36A) and the refrigerant circulation part (40B) on the right side of the rear row of the second plate (36B) (49) is formed. The refrigerant inflow passage (52) and the refrigerant outlet (52) leading to the refrigerant inlet (48) span the two right protrusions (36a) (36b) (37a) of the three plates (36A) (36B) (37). 49) A refrigerant inlet / outlet member (51) having a refrigerant outlet passage (53) leading to 49) is brazed to the first header tank (31) by a brazing sheet having a brazing material layer on both sides, here an aluminum brazing sheet (57). ing. The refrigerant inlet / outlet member (51) is made of a metal bare material, here an aluminum bear material.

  The two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the first header tank (31) correspond to the first outward bulging portion (39A). The refrigerant inlet header portion (1) is formed by the portion, and the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the first header tank (31) are also formed. 2 The front intermediate header portion (2) is formed by the portion corresponding to the outward bulge portion (39B), and the front header row (5) is formed by the inlet header portion (1) and the front intermediate header portion (2). Is configured. In addition, the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the first header tank (31) and the third outward bulging portion (portion corresponding to 39C) As a result, the outlet header portion (2) is formed, and the fourth outside of the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the first header tank (31). A rear intermediate header portion (4) is formed by a portion corresponding to the side bulge portion (39D), and a rear header portion row (6) is formed by the outlet header portion (3) and the rear intermediate header portion (4). The length of the intermediate header portion (2) of the front header portion row (5) of the first header tank (31) is longer than the length of the inlet header portion (1), and the first header tank The length of the outlet header portion (3) of (31) is longer than the length of the intermediate header portion (4) of the rear header portion row (6).

  As shown in FIGS. 1 to 3 and 8, the second header tank (32) has substantially the same configuration as the first header tank (31), and the same components and the same parts are denoted by the same reference numerals. Both header tanks (31) and (32) are arranged so that the pipe connecting plates (37) face each other. The difference between the second header tank (32) and the first header tank (31) is as described below.

Two outward bulges (54A) (54B) extending in the left-right direction are formed in the first plate (36A) of the second header tank (32) at intervals in the front-rear direction. Both the outward bulge portions (54A) and (54B) are respectively the first outward bulge portion (39A) and the second outward bulge portion (39B) of the first plate (36A) of the first header tank (31). ), And the third outward bulge portion (39C) and the fourth outward bulge portion (39D), respectively, from the right end portion to the left end portion of the first plate (36A). The bulging height and width of the front and rear outer bulges (54A) (54B) are the same as those of the outer bulges (39A) to (39D) of the first plate (36A) of the first header tank (31). It is equal to the bulge height and width. The internal space of the front and rear outward bulging portion (54A) (54B) (54a ) (54b) is adapted to flow the CO ₂ in the lateral direction, respectively, CO ₂ is the front outward bulging portion (54A ) Flows from right to left, and flows from left to right in the inner space (54b) of the rear outward bulge portion (54B). Note that the both outwardly bulged portions (54A) and (54B) are not communicated with each other.

  A plurality of through-tube insertion holes (41) that are long in the front-rear direction are formed in the front-rear side portions of the pipe connection plate (37), with a space in the left-right direction. All the tube insertion holes (41) on the front side are formed within the lateral direction of the front outward bulge portion (54A) of the first plate (36A), and all the tube insertion holes (41) on the rear side are The rear outer bulge portion (54B) is formed within the range in the left-right direction.

  The tank forming member (36) is formed at a position corresponding to the pipe insertion hole (41) of the pipe connection plate (37) in the second plate (36B), and the pipe insertion hole (41) is formed in each outwardly bulging portion. All of the communication holes (44) communicating with the internal spaces (54a) and (54b) of (54A) and (54B) cut out portions between the communication holes (44) adjacent in the left-right direction in the second plate (36B). The communication part (46) formed by this is connected. And a communicating portion (46) for communicating all the communicating holes (44) leading to the internal spaces (54a) (54b) of the front and rear outwardly bulging portions (54A) (54B) of the first plate (36A), and The front and rear center of the communication hole (44) (the part corresponding to the communication part (46) in the communication hole (44)) causes the second plate (36B) to bulge both the front and rear sides of the first plate (36A). Refrigerant circulation portions (55A) and (55B) are formed which communicate with the internal spaces (54a) and (54b) of the portions (54A) and (54B) and through which the refrigerant flows in the left-right direction.

  The second header tank (32) is not formed with the refrigerant inlet (48) and the refrigerant outlet (49).

  The front and rear outward bulges (54A) (54B) of the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the second header tank (32) The two intermediate header portions (7) and (8) are formed by the corresponding portions.

  The heat exchange pipe (33) is made of a bare metal material, here an aluminum extruded shape, and has a flat shape that is wide in the front-rear direction, and a plurality of refrigerant passages (33a) that extend in the length direction are arranged in parallel in the heat exchange pipe (33). The cross-sectional areas of the heat exchange tubes are equal. Both ends of the heat exchange pipe (33) are inserted into the pipe insertion holes (41) of the header tanks (31) and (32), respectively, using the brazing material layer of the pipe connection plate (37). It is brazed to the pipe connection plate (37). Both ends of the heat exchange pipe (33) enter the communication hole (44) up to the middle part in the thickness direction of the second plate (36B).

  The total heat exchange pipe (33) is composed of a plurality of heat exchange pipes (33) arranged in parallel at intervals in the left-right direction, and the header section row (5) (6) of the first header tank (31). Are divided into the same number, that is, two heat exchange tube rows (10) and (11). The upper and lower ends of the plurality of heat exchange pipes (33) located on the right side of the front heat exchange pipe row (10) are in the inlet header part (1) of the first header tank (31) (the first outward bulge). The inner space (39a) of the section (39A), the right side refrigerant circulation section (40A)), and the inside of the front intermediate header section (7) of the second header tank (32) (inside the front outer bulging section (54A)) Connected to both header tanks (31) and (32) so as to communicate with the right side of the space (54a) and the refrigerant circulation section (55A) in the front row, and above and below the plurality of heat exchange tubes (33) which are also located on the left side Both ends are located in the front intermediate header portion (2) of the front header portion row (5) of the first header tank (31) (the internal space (39b) of the second outer bulge portion (39B) and the refrigerant on the left side of the front row) Distribution section (40B)) and in the front intermediate header section (7) of the second header tank (32) (the inner space (54a) of the front outer bulge section (54A) and the refrigerant distribution section (55A) in the front row). Connect to both header tanks (31) and (32) so as to communicate with the left side It is. In addition, the upper and lower ends of the plurality of heat exchange tubes (33) located in the right part of the rear heat exchange tube row (11) are located in the outlet header portion (3) of the first header tank (31) (the third outer portion). The internal space (39c) of the side bulge portion (39C) and the right side rear refrigerant circulation portion (40C)) and the rear intermediate header portion (8) of the second header tank (32) (rear side outward bulge portion) A plurality of heat exchange tubes that are connected to both header tanks (31) and (32) so as to communicate with the right side portion of the internal space (54b) of the rear row (54B) and the refrigerant circulation portion (55B) of the rear row, and are also located on the left side portion The upper and lower ends of (33) are arranged in the left intermediate header part (4) of the rear header part row (6) of the first header tank (31) (the inner space (39d ) And a communication hole (44) communicating with the inner space (39d) and the inner space (54b of the rear outer bulge portion (54B) in the rear intermediate header portion (8) of the second header tank (32). ) And the left side of the refrigerant distribution section (55B) in the rear row) Connected to the link (31) (32).

  The heat exchange pipe (33) leading to the inlet header portion (1) of the first header tank (31) and the front intermediate header portion (7) of the second header tank (32), and the first header tank (31) The refrigerant flows from top to bottom by the heat exchange pipe (33) that leads to the intermediate header section (4) of the rear header section row (6) and the rear intermediate header section (8) of the second header tank (32). A first heat exchange tube group (12) is formed. Also, a heat exchange pipe (33) leading to the outlet header section (3) of the first header tank (31) and the rear intermediate header section (8) of the second header tank (32), and the first header tank (31) The refrigerant flows from the bottom to the top by the heat exchange pipe (33) leading to the intermediate header section (2) of the front header section row (5) and the front intermediate header section (7) of the second header tank (32). Two heat exchange tube groups (13) are formed. Accordingly, the first heat exchange tube group (12) and the second heat exchange tube group (13) are provided in each heat exchange tube row (10) (11) side by side in the left-right direction, and the first header tank The length of the intermediate header part (2) of the front header part row (5) of (31) is longer than the length of the inlet header part (1), and the outlet header part (3) of the first header tank (31) Is longer than the length of the intermediate header part (4) of the rear header part row (6), the number of heat exchange pipes (33) constituting the second heat exchange pipe group (13) is It is larger than the number of heat exchange tubes (33) constituting one heat exchange tube group (12). As a result, since the cross-sectional area of each heat exchange pipe (33) is equal, the total cross-sectional area of the total heat exchange pipe (33) constituting each second heat exchange pipe group (13) is It is larger than the total flow passage cross-sectional area of the total heat exchange pipe (33) constituting the first heat exchange pipe group (12) adjacent thereto, for example, 1.1 to 1.7 times larger. It is preferable.

  The heat exchange pipe (33) was formed by rolling an aluminum brazing sheet having a brazing filler metal layer on both sides, instead of one made of an aluminum extruded profile, and continued through a connecting portion. Two flat wall forming portions, a side wall forming portion integrally formed in a raised shape from the side edge on the opposite side of the connecting portion in each flat wall forming portion, and a predetermined interval in the width direction of the flat wall forming portion. A plate having a plurality of partition wall forming portions integrally formed in a protruding shape from the flat wall forming portion is bent into a hairpin shape at the connecting portion, and the side wall forming portions are butted against each other to form a partition wall. You may use what formed the partition wall by the part.

  The corrugated fin (34) is formed in a wave shape using an aluminum brazing sheet having a brazing filler metal layer on both sides, and a plurality of the corrugated fins (34) are connected in parallel in the front-rear direction to the connecting portion connecting the wave head and the wave bottom. A louver is formed. The corrugated fin (34) is shared by both the front and rear heat exchange tube rows (10) and (11), and the width in the front and rear direction is the front edge and the rear edge of the heat exchange tube (33) of the front heat exchange tube row (10). The distance between the side heat exchange tube row (11) and the rear edge of the heat exchange tube (33) is substantially equal. In addition, instead of sharing one corrugated fin (34) with both the front and rear heat exchange tube rows (10) and (11), the adjacent heat exchange tubes (33) between the heat exchange tube rows (10) and (11) are connected to each other. Corrugated fins may be arranged between the two.

  Both header tanks (31) and (32) are manufactured as shown in FIGS.

  First, an aluminum brazing sheet having a brazing filler metal layer on both sides is pressed to form a first plate (36A) having outward bulges (39A) (39B) (39C) (39D) (54A) (54B). ). Further, by pressing the aluminum bear material, the second hole having the communication hole (44), the communication part (45) (46), and the refrigerant circulation part (40A) (40B) (40C) (55A) (55B) is provided. A plate (36B) is formed. Furthermore, by pressing the aluminum brazing sheet having the brazing filler metal layer on both sides, the engaging portion forming protrusion piece straightly connected to the tube insertion hole (41), the covering wall (42) and the covering wall (42). A pipe connecting plate (37) having (43A) is formed. The first plate (36A), the second plate (36B) and the pipe connection plate (37) of the first header tank (31) are respectively formed with right protrusions (36a) (36b) (37a), Further, a notch (47) is formed in the second plate (36B).

  Next, after the three plates (36A), (36B), and (37) are combined in a laminated form, the protruding piece (43A) is bent to form the engaging portion (43), and the engaging portion (43) is the first plate. Engage with (36A) to make a temporary fix. Thereafter, the three plates (36A) (36B) (37) are brazed to each other using the brazing material layer of the first plate (36A) and the brazing material layer of the pipe connecting plate (37), and the covering wall (42) is brazed to the front and rear side surfaces of the second plate (36B) and the first plate (36A), and the engaging portion (43) is brazed to the first plate (36A). Thus, both header tanks (31) and (32) are manufactured.

  The evaporator (30) is prepared by preparing the above-mentioned two temporary fixing bodies when manufacturing the header tanks (31) and (32), a plurality of heat exchange pipes (33) and corrugated fins (34), Temporary fixing bodies are arranged at intervals so that the pipe connection plates (37) face each other, multiple heat exchange pipes (33) and corrugated fins (34) are arranged alternately, heat exchange Insert both ends of the pipe (33) into the pipe insertion holes (41) of the pipe connection plates (37) of both temporary fixing bodies, and attach the side plates (35) to the outside of the corrugated fins (34) at both ends. Arranging the refrigerant inlet / outlet member (51) through the brazing sheet (57) so as to straddle the three plates (36A) (36B) (37), and the three plates (36A ) (36B) (37) are brazed together to form the header tank (31) (32), and at the same time, the heat exchange pipe (33) is attached to the header tank (31) (32). The fins (34) heat exchange tubes (33) and the side plate (35) in the fins (34) are prepared by respectively brazed to and out member (51) the first header tank (31).

  The evaporator (30) constitutes a supercritical refrigeration cycle together with an intermediate heat exchanger for exchanging heat between the refrigerant coming out of the compressor, the gas cooler, the decompressor and the gas cooler and the refrigerant coming out of the evaporator. For example, it is installed in a car.

In the above-described evaporator (30), as shown in FIG. 11, the liquid-phase CO ₂ decompressed through the expansion valve as the decompressor passes through the refrigerant inflow passage (52) of the inlet / outlet member (51). The refrigerant enters the inlet header portion (1) of the first header tank (31) from the refrigerant inlet (48), and flows into the left side of the first header tank (31). It flows into the refrigerant passage (33a) of the heat exchange pipe (33) of the group (12).

The CO ₂ flowing into the refrigerant passage (33a) of the heat exchange pipe (33) of the first heat exchange pipe group (12) of the front heat exchange pipe row (10) flows downward in the refrigerant passage (33a). The right part in the front intermediate header portion (7) of the second header tank (32) flows in, flows to the left in the inside, and divides the second heat exchange pipe group (13 in the front heat exchange pipe row (10)). ) Into the refrigerant passage (33a) of the heat exchange pipe (33).

The CO ₂ flowing into the refrigerant passage (33a) of the heat exchange pipe (33) of the second heat exchange pipe group (13) of the front heat exchange pipe row (10) changes its flow direction and enters the refrigerant passage (33a). And flows into the middle header part (2) of the front header part row (5) of the first header tank (31), flows to the left inside the first header tank (31), and for the refrigerant turn of the second plate (36B) It passes through the communication part (45) and enters the intermediate header part (4) of the rear header part row (6). The CO ₂ flowing into the intermediate header part (4) of the rear header part row (6) is transferred to the heat exchange pipe (33) of the first heat exchange pipe group (12) of the rear heat exchange pipe row (11). Flows into the refrigerant passage (33a), changes the flow direction, flows downward in the refrigerant passage (33a), flows into the left side portion of the rear intermediate header portion (8) of the second header tank (32), The inside flows to the right, divides, and flows into the refrigerant passage (33a) of the heat exchange pipe (33) of the second heat exchange pipe group (13) of the rear heat exchange pipe row (11).

The CO _{2 that} has flowed into the refrigerant passage (33a) of the heat exchange pipe (33) of the second heat exchange pipe group (13) of the rear heat exchange pipe row (11) changes the flow direction and changes to the refrigerant passage (33a). The refrigerant flows out upward, enters the outlet header portion (3) of the first header tank (31), flows to the right inside thereof, and flows out of the refrigerant outlet (49) and the refrigerant outlet passage (53) of the inlet / outlet member (51). Spill through. While CO ₂ flows in the refrigerant passage (33a) of the heat exchange pipe (33), heat exchange is performed between the air flowing in the direction indicated by the arrow X in FIGS. 1 and 11 to form a gas phase. Leaked.

  At this time, the total flow cross-sectional area of the total heat exchange pipe (33) constituting the second heat exchange pipe group (13) of the rear heat exchange pipe row (11) is equal to that of the rear heat exchange pipe row (11). Since the total cross-sectional area of the total heat exchange pipe (33) constituting the first heat exchange pipe group (12) is larger, the second heat exchange pipe group in the rear heat exchange pipe row (11) There is a pressure loss when the refrigerant flows through the heat exchange pipe (33) of (13) and a pressure loss when the refrigerant flows through the heat exchange pipe (33) of the first heat exchange pipe group (12) adjacent to the heat exchange pipe (33). As a result, the amount of refrigerant flowing through the heat exchange tube (33) of the second heat exchange tube group (13) and the amount of refrigerant flowing through the heat exchange tube (33) of the first heat exchange tube group (12) are It is made uniform. Therefore, the refrigerant distribution state to the heat exchange pipe (33) of the first heat exchange pipe group (12) and the heat exchange pipe (33) of the second heat exchange pipe group (13) of the rear heat exchange pipe row (11) Can be adjusted to be suitable for improving the heat exchanging performance, and the flow of refrigerant can be made uniform to each heat exchanging pipe (33). The total flow cross-sectional area of the total heat exchange tubes (33) constituting the second heat exchange tube group (13) of the front heat exchange tube row (10) is the first heat of the front heat exchange tube row (10). Since the total cross-sectional area of the total heat exchange pipe (33) constituting the exchange pipe group (12) is larger, the second heat exchange pipe group (13 The pressure loss when the refrigerant flows through the heat exchange pipe (33) of the first heat exchange pipe and the pressure loss when the refrigerant flows through the heat exchange pipe (33) of the first heat exchange pipe group (12) adjacent thereto are made uniform. As a result, the refrigerant quantity flowing through the heat exchange pipe (33) of the second heat exchange pipe group (13) and the refrigerant quantity flowing through the heat exchange pipe (33) of the first heat exchange pipe group (12) are made uniform. Is done. Therefore, the refrigerant distribution state to the heat exchange pipe (33) of the first heat exchange pipe group (12) and the heat exchange pipe (33) of the second heat exchange pipe group (13) of the front heat exchange pipe row (10) is changed. It can be adjusted to be suitable for improving the heat exchanging performance, and the distribution state of the refrigerant to each heat exchanging pipe (33) can be made uniform.

Embodiment 2
This embodiment is shown in FIGS.

  FIG. 12 shows the overall configuration of an evaporator to which the present invention is applied, FIGS. 13 to 15 show the configuration of the main part of the evaporator, and FIG. 16 shows the flow of refrigerant in the evaporator of FIG.

In FIG. 12, an evaporator (60) of a supercritical refrigeration cycle using a supercritical refrigerant, for example, CO ₂ , has two header tanks (61) (62) arranged in the vertical direction and extending in the horizontal direction. Between the header tanks (61) (62), a plurality of flat heat exchange pipes (33) arranged in parallel with a space in the left-right direction, and between adjacent heat exchange pipes (33) Corrugated fins (34) placed outside the heat exchange pipes (33) at the left and right ends and brazed to the heat exchange pipes (33), and outside the corrugated fins (34) at the left and right ends, respectively. And an aluminum bear side plate (35) brazed to the corrugated fin (34). In this embodiment, the upper header tank (61) is referred to as a second header tank, and the lower header tank (62) is referred to as a first header tank.

  As shown in FIG. 13, the second header tank (61) is the same as the second header tank (32) of the evaporator (30) of Embodiment 1 and is arranged upside down.

  The first header tank (62) has a configuration similar to that of the first header tank (31) of the evaporator (30) according to the first embodiment, which is disposed upside down.

The difference of the evaporator (30) of the first embodiment in the first header tank (62) from the first header tank (31) is as follows. That is, as shown in FIGS. 12, 14 and 15, the length of the first outward bulge portion (63A) formed in the front right portion of the first plate (36A) of the tank forming member (36) is The length of the second outward bulge portion (63B) formed in the front left portion is longer than the length in the left-right direction and the fourth outward bulge portion (63D) formed in the rear left portion. The length in the left-right direction is longer than the length in the left-right direction of the third outward bulge portion (63C) formed in the rear right portion. All the communication holes (44) leading to the internal space (63a) of the first outer bulging portion (63A) of the first plate (36A) in the second plate (36B) of the tank forming member (36), the third outer All the communication holes (44) leading to the internal space (63c) of the side bulge part (63C) and all the communication holes (44) leading to the internal space (63d) of the fourth outward bulge part (63D) are Each of the second plates (36B) is communicated by a communicating portion (46) formed by cutting a central portion in the front-rear direction between communicating holes (44) adjacent in the left-right direction. Then, the internal space (63a) (63b) of the first outer bulging portion (63A), the third outer bulging portion (63C) and the fourth outer bulging portion (63D) of the first plate (36A). By the communication part (46) communicating all the communication holes (44) leading to (63c) and the center part in the front-rear direction of the communication hole (44) (the part corresponding to the communication part (46) in the communication hole (44)) The second plate (36B) has an inner portion of the first outer bulging portion (63A), the third outer bulging portion (63C) and the fourth outer bulging portion (63D) of the first plate (36A). Refrigerant circulation portions (64A), (64B) and (64C) are formed which communicate with the spaces (63a), (63b) and (63c) and in which the refrigerant flows in the left-right direction. Each communication hole (44) communicating with the internal space (63b) of the second outward bulge portion (63B) of the first plate (36A) in the second plate (36B), and the communication hole (44) in the left-right direction, Each communication hole (44) in the corresponding position and communicating with the internal space (63d) of the fourth outward bulge portion (63D) is a communication hole (44) adjacent in the front-rear direction in the second plate (36B). The refrigerant turn communication portion (45) formed by cutting out the portion between the two is connected to the second plate of the first plate (36A).
The internal spaces (63b) and (63d) of the fourth outer bulges (63B) and (63D) communicate with each other.

  The two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the first header tank (62) correspond to the first outward bulging portion (63A). The refrigerant inlet header portion (65) is formed by the portion, and the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the first header tank (62) are also formed. 2 The front intermediate header portion (66) is formed by the portion corresponding to the outward bulge portion (63B), and the front header portion row (67) is formed by the inlet header portion (65) and the front intermediate header portion (66). Is configured. Moreover, it respond | corresponds with the 3rd outward bulge part (63C) in two plates (36A) (36B) and the pipe connection plate (37) which comprise the tank formation member (36) of a 1st header tank (62). An outlet header portion (68) is formed by the portion, and the fourth of the two plates (36A) (36B) and the pipe connection plate (37) constituting the tank forming member (36) of the first header tank (62). The rear intermediate header portion (69) is formed by the portion corresponding to the outward bulge portion (63D), and the rear header portion row (by the outlet header portion (68) and the rear intermediate header portion (69)) ( 71) is configured. The length of the inlet header portion (65) of the front header portion row (67) of the first header tank (62) is longer than the length of the intermediate header portion (66), and the rear header of the first header tank (62). The length of the intermediate header part (69) of the part sequence (71) is longer than the length of the outlet header part (68).

  The upper and lower ends of the plurality of heat exchange pipes (33) located on the right side of the front heat exchange pipe row (10) are in the front intermediate header part (7) of the second header tank (61) (front outward bulge). The right side portion of the internal space (54a) of the portion (54A) and the refrigerant circulation portion (55A) in the front row and the inside of the inlet header portion (65) (the internal space (63a) and the front row of the first outward bulging portion (63A)) The right and left ends of the plurality of heat exchange pipes (33), which are connected to both header tanks (61) and (62) so as to communicate with the right refrigerant circulation section (64A) In the front intermediate header portion (7) of (61) (the inner space (54a) of the front outward bulge portion (54A) and the refrigerant circulation portion (55A) of the front row) and the first header tank (62) Leads to the front intermediate header part (66) of the front header part row (67) (the internal space (63b) of the second outer bulge part (63B) and the communication hole (44) leading to the internal space (63b)). Connected to both header tanks (61) (62) . Also, the upper and lower ends of the plurality of heat exchange pipes (33) located in the right part of the rear heat exchange pipe row (11) are located in the rear intermediate header part (8) of the second header tank (61) (rear) The right side portion of the internal space (54b) of the side outward bulge portion (54B) and the refrigerant circulation portion (55B) in the rear row and the inside of the outlet header portion (3) of the first header tank (62) (third outward bulge) A plurality of heat exchange pipes that are connected to both header tanks (61) and (62) so as to communicate with the internal space (63c) of the outlet (63C) and the refrigerant circulation part (64B) on the right side of the rear row, and are also located on the left side The upper and lower ends of (33) are arranged in the rear intermediate header portion (8) of the second header tank (61) (the inner space (54b) of the rear outer bulge portion (54B) and the rear row refrigerant circulation portion ( 55B)) in the left side portion of the first header tank (62) and in the intermediate header portion (69) of the rear header portion row (71) (inner space (63d) and rear row of the fourth outward bulge portion (63D)) Both header tanks (61) and (62) lead to the refrigerant distribution section (64C) on the left side It is connected.

  And a heat exchange pipe (33) leading to the intermediate header section (66) of the front header section row (67) of the first header tank (62) and the front header section (7) of the second header tank (61), and The refrigerant flows from top to bottom by the heat exchange pipe (33) that leads to the rear intermediate header portion (8) of the second header tank (61) and the outlet header portion (68) of the first header tank (62). One heat exchange tube group (12) is formed. Further, the heat exchange pipe (33) leading to the front intermediate header (7) of the first header tank (62) and the inlet header (65) of the first header tank (62), and the second header tank (61) The refrigerant flows from the bottom to the top by the heat exchange pipe (33) leading to the middle header section (69) of the rear header section row (71) of the rear middle header section (8) and the first header tank (62). A second heat exchange tube group (13) is formed. Accordingly, the first heat exchange tube group (12) and the second heat exchange tube group (13) are provided in each heat exchange tube row (10) (11) side by side in the left-right direction, and the first header tank The length of the inlet header portion (65) of (62) is longer than the length of the intermediate header portion (66) of the front header portion row (67), and the rear header portion row of the first header tank (62) ( The length of the intermediate header portion (69) of 71) is longer than the length of the outlet header portion (68), so that the number of heat exchange tubes (33) constituting the second heat exchange tube group (13) is It is larger than the number of heat exchange tubes (33) constituting one heat exchange tube group (12). As a result, since the cross-sectional area of each heat exchange pipe (33) is equal, the total cross-sectional area of the total heat exchange pipe (33) constituting each second heat exchange pipe group (13) is It is larger than the total flow passage cross-sectional area of the total heat exchange pipe (33) constituting the first heat exchange pipe group (12) adjacent thereto, for example, 1.1 to 1.7 times larger. It is preferable.

  The other structure in the evaporator (60) of Embodiment 2 is the same as that of the evaporator (30) of Embodiment 1, and is manufactured by the same method as that of the evaporator (30) of Embodiment 1.

In the evaporator (60) described above, as shown in FIG. 16, the liquid-phase CO ₂ that has been decompressed through the expansion valve as the decompressor passes through the refrigerant inflow passage (52) of the inlet / outlet member (51). The refrigerant enters the inlet header portion (65) of the first header tank (62) from the refrigerant inlet (48), and flows into the left side of the inlet header portion (65) to be divided into the second heat exchange tubes of the front heat exchange tube row (10). It flows into the refrigerant passage (33a) of the heat exchange pipe (33) of the group (13).

The CO ₂ flowing into the refrigerant passage (33a) of the heat exchange pipe (33) of the second heat exchange pipe group (13) of the front heat exchange pipe row (10) flows upward in the refrigerant passage (33a). The right side portion of the second intermediate tank portion (7) of the second header tank (61) flows in, flows to the left in the inside, and is divided into first heat exchange tube groups (12) in the front heat exchange tube row (10). ) Into the refrigerant passage (33a) of the heat exchange pipe (33).

The CO ₂ flowing into the refrigerant passage (33a) of the heat exchange pipe (33) of the first heat exchange pipe group (12) of the front heat exchange pipe row (10) changes the flow direction and enters the refrigerant passage (33a). And flows into the intermediate header portion (66) of the front header portion row (67) of the first header tank (62), and passes through the refrigerant turn communication portion (45) of the second plate (36B). The intermediate header portion (69) of the side header portion row (71) is entered. The CO _{2 that} has flowed into the intermediate header portion (69) of the rear header portion row (71) is shunted while flowing through the inside, and the second heat exchange tube group (13) of the rear side heat exchange tube row (11). The refrigerant flows into the refrigerant passage (33a) of the heat exchange pipe (33), changes the flow direction, flows upward in the refrigerant passage (33a), and then reaches the rear intermediate header portion (8) of the second header tank (61). Flows into the left part of the inside, flows to the right inside, and divides the refrigerant passage (33a of the heat exchange pipe (33) of the first heat exchange pipe group (12) of the rear heat exchange pipe row (11). ) Flows in.

The CO ₂ flowing into the refrigerant passage (33a) of the heat exchange pipe (33) of the first heat exchange pipe group (12) of the rear heat exchange pipe row (11) changes the flow direction and changes to the refrigerant passage (33a). The refrigerant flows downward and enters the outlet header portion (68) of the first header tank (62), flows to the right inside thereof, and flows out of the refrigerant outlet (49) and the refrigerant outlet passage (53) of the inlet / outlet member (51). Spill through. While the CO ₂ flows in the refrigerant passage (33a) of the heat exchange pipe (33), heat exchange with the air flowing in the direction indicated by the arrow X in FIGS. Leaked.

  At this time, the total flow cross-sectional area of the total heat exchange pipe (33) constituting the second heat exchange pipe group (13) of the rear heat exchange pipe row (11) is equal to that of the rear heat exchange pipe row (11). Since the total cross-sectional area of the total heat exchange pipe (33) constituting the first heat exchange pipe group (12) is larger, the second heat exchange pipe group in the rear heat exchange pipe row (11) There is a pressure loss when the refrigerant flows through the heat exchange pipe (33) of (13) and a pressure loss when the refrigerant flows through the heat exchange pipe (33) of the first heat exchange pipe group (12) adjacent to the heat exchange pipe (33). As a result, the amount of refrigerant flowing through the heat exchange tube (33) of the second heat exchange tube group (13) and the amount of refrigerant flowing through the heat exchange tube (33) of the first heat exchange tube group (12) are It is made uniform. Therefore, the refrigerant distribution state to the heat exchange pipe (33) of the first heat exchange pipe group (12) and the heat exchange pipe (33) of the second heat exchange pipe group (13) of the rear heat exchange pipe row (11) Can be adjusted to be suitable for improving the heat exchanging performance, and the flow of refrigerant can be made uniform to each heat exchanging pipe (33). The total flow cross-sectional area of the total heat exchange tubes (33) constituting the second heat exchange tube group (13) of the front heat exchange tube row (10) is the first heat of the front heat exchange tube row (10). Since the total cross-sectional area of the total heat exchange pipe (33) constituting the exchange pipe group (12) is larger, the second heat exchange pipe group (13 The pressure loss when the refrigerant flows through the heat exchange pipe (33) of the first heat exchange pipe and the pressure loss when the refrigerant flows through the heat exchange pipe (33) of the first heat exchange pipe group (12) adjacent thereto are made uniform. As a result, the refrigerant quantity flowing through the heat exchange pipe (33) of the second heat exchange pipe group (13) and the refrigerant quantity flowing through the heat exchange pipe (33) of the first heat exchange pipe group (12) are made uniform. Is done. Therefore, the refrigerant distribution state to the heat exchange pipe (33) of the first heat exchange pipe group (12) and the heat exchange pipe (33) of the second heat exchange pipe group (13) of the front heat exchange pipe row (10) is changed. It can be adjusted to be suitable for improving the heat exchanging performance, and the distribution state of the refrigerant to each heat exchanging pipe (33) can be made uniform.

  In the above two embodiments, the cross-sectional areas of the heat exchange tubes (33) are equal, and the number of heat exchange tubes (33) constituting the second heat exchange tube group (13) is the first heat. Since the number of heat exchange pipes (33) constituting the exchange pipe group (12) is larger than the total number of heat exchange pipes (33) constituting the second heat exchange pipe group (13), The area is larger than the total flow cross-sectional area of the total heat exchange pipe (33) constituting the first heat exchange pipe group (12). Instead, the second heat exchange pipe group is constituted. The number of heat exchange tubes and the number of heat exchange tubes constituting the first heat exchange tube group are equal, and the cross-sectional area of each heat exchange tube constituting the second heat exchange tube group is the first heat. Since the flow passage cross-sectional area of each heat exchange pipe constituting the exchange pipe group is larger, the total flow cross-sectional area of all the heat exchange pipes constituting the second heat exchange pipe group is the first heat exchange pipe. Total flow cross section of all heat exchange tubes constituting the group It may be larger than.

  In the above two embodiments, the number of the second plates (36B) of the tank forming member (36) is 1, but the number is not limited to this, and the first plate (36A) and the pipe connection plate are not limited thereto. A plurality of second plates (36B) may be interposed between the two plates (37). In this case, a communication hole (44), a communication part (45) (46), etc. are formed in each 2nd plate (36B).

  In the above two embodiments, the heat exchanger according to the present invention is applied to an evaporator of a supercritical refrigeration cycle. However, the present invention is not limited to this, and the heat exchanger according to the present invention is used for other applications. Sometimes it is done.

Furthermore, in the above two embodiments, CO ₂ is used as the supercritical refrigerant in the supercritical refrigeration cycle, but is not limited to this, and ethylene, ethane, nitric oxide and the like are used.

It is a perspective view which shows the whole structure of Embodiment 1 of the evaporator to which the heat exchanger by this invention is applied. FIG. 2 is a partially omitted vertical sectional view of the front portion of the evaporator of FIG. It is an AA line expanded sectional view of FIG. FIG. 3 is an enlarged sectional view taken along line B-B in FIG. 2. FIG. 5 is an enlarged cross-sectional view taken along the line CC in FIG. 4. It is the DD sectional view taken on the line of FIG. It is a disassembled perspective view which shows the right end part of the 1st header tank in the evaporator of FIG. It is the EE sectional view taken on the line of FIG. It is a disassembled perspective view which shows the part of the 1st header tank of the evaporator of FIG. It is a disassembled perspective view which shows the part of the 2nd header tank of the evaporator of FIG. It is a figure which shows the flow of the refrigerant | coolant in the evaporator of FIG. It is a perspective view which shows the whole structure of Embodiment 2 of the evaporator to which the heat exchanger by this invention is applied. It is a disassembled perspective view which shows the part of the 1st header tank of the evaporator of FIG. It is a disassembled perspective view which shows the part of the 2nd header tank of the evaporator of FIG. It is a horizontal sectional view which shows the part of the 2nd header tank of the evaporator of FIG. It is a figure which shows the flow of the refrigerant | coolant in the evaporator of FIG.

Explanation of symbols

(1): Refrigerant inlet header
(2): Intermediate header
(3): Refrigerant outlet header
(4): Intermediate header
(5): Front header row
(6): Rear header column
(7) (8): Intermediate header
(10): Front heat exchange tube row
(11): Rear heat exchange tube row
(12): First heat exchange tube group
(13): Second heat exchange tube group
(30): Evaporator (heat exchanger)
(31) (32): Header tank
(33): Heat exchange pipe
(36): Tank forming member
(36A): 1st plate
(36B): Second plate
(37): Pipe connection plate
(39A) to (39D): outward bulge
(39a) to (39d): Internal space
(60): Evaporator
(61) (62): Header tank
(63A) to (63D): outward bulge
(65): Refrigerant inlet header
(66): Intermediate header
(67): Front header section
(68): Refrigerant outlet header
(69): Intermediate header
(71): Rear header column

Claims (12)

A pair of header tanks extending in the left-right direction spaced apart in the vertical direction, and a plurality of heat exchange tubes arranged in parallel between the header tanks and having upper and lower ends connected to the header tanks, respectively And a header portion row made up of a plurality of header portions arranged in the left-right direction on the first header tank of either one of the upper and lower header tanks. The number of header portions constituting each header portion row of the first header tank at a position corresponding to each header portion row of the first header tank in the other second header tank provided in a plurality of rows at intervals in the direction A plurality of header sections, which are provided so as to straddle two adjacent header sections in each header section row of the first header tank, and are arranged in a horizontal direction between the upper and lower header tanks. The heat exchange tube rows that are formed of tubes and have the same number as the header portion row of the first header tank are provided side by side in the front-rear direction. In each heat exchange tube row, a first heat exchange tube group consisting of a plurality of heat exchange tubes where the refrigerant flows from the top to the bottom, and a second heat exchange tube group consisting of a plurality of heat exchange tubes where the refrigerant flows from the bottom to the top, In the heat exchanger in which the refrigerant flowing in from the refrigerant inlet passes through all the heat exchange pipes and the header part and flows out from the refrigerant outlet,
The first heat exchange in which the total flow cross-sectional area of all the heat exchange tubes constituting the last second heat exchange tube group located closest to the refrigerant outlet side is adjacent to at least one of the left and right sides of the second heat exchange tube group A heat exchanger that is larger than the total flow passage cross-sectional area of all the heat exchange tubes constituting the tube group. The total flow cross-sectional area of the total heat exchange pipe constituting the last second heat exchange pipe group is the total heat constituting the first heat exchange pipe group adjacent to at least one of the left and right sides of the second heat exchange pipe group. The heat exchanger according to claim 1, wherein the heat exchanger is 1.1 to 1.7 times larger than a total flow passage cross-sectional area of the exchange pipe. The cross-sectional areas of the heat exchange tubes are equal, and the number of heat exchange tubes constituting the last second heat exchange tube group is the second adjacent to at least one of the left and right sides of the second heat exchange tube group. The heat exchanger according to claim 1 or 2, wherein the number is larger than the number of heat exchange tubes constituting one heat exchange tube group. The number of heat exchange tubes constituting the last second heat exchange tube group and the number of heat exchange tubes constituting the first heat exchange tube group adjacent to at least one of the left and right sides of the second heat exchange tube group are equal. And the flow passage cross-sectional area of each heat exchange pipe constituting the last second heat exchange pipe group constitutes the first heat exchange pipe group adjacent to at least one of the left and right sides of the second heat exchange pipe group. The heat exchanger according to claim 1 or 2, wherein the heat exchanger tube has a larger cross-sectional area than each other. The upper header tank becomes the first header tank and the lower header tank becomes the second header tank, and the upper header tank is provided with two header part rows each having two header parts, and one header of the front header part row. The refrigerant inlet header portion is connected to the refrigerant inlet header portion, and the one header portion on the same side as the refrigerant inlet header portion in the rear header portion row is the refrigerant outlet header portion and the refrigerant. The refrigerant outlet communicates with the outlet header section, the other header section of both header section rows of the upper header tank serves as an intermediate header section, and the interior of both middle header sections communicate with each other, and both the front and rear sides of the lower header tank In addition, one intermediate header portion is provided so as to straddle the two header portions of the front and rear header portion rows of the upper header tank, respectively, and the refrigerant outlet of the upper header tank The total heat exchange pipes leading to the header part constitute the last second heat exchange pipe group, and the length of the refrigerant outlet header part is longer than the length of the intermediate header part of the rear header part row. The flow path cross-sectional area of an exchange pipe is equal, and the number of the heat exchange pipes which lead to a refrigerant | coolant exit header part is larger than the number of the heat exchange pipes which lead to the intermediate header part of a rear side header part row | line | column. The described heat exchanger. The length of the intermediate header part of the front header part row of the upper header tank is longer than the length of the refrigerant inlet header part, the flow cross-sectional area of each heat exchange pipe is equal, and the length of the front header part row of the upper header tank The total heat exchange pipes that lead to the intermediate header part constitute the second heat exchange pipe group, and the number of heat exchange pipes that lead to the intermediate header part of the front header part row of the upper header tank leads to the refrigerant inlet header part The heat exchanger according to claim 5, wherein the heat exchanger is larger than the number of the heat exchangers. The lower header tank becomes the first header tank and the upper header tank becomes the second header tank, and the lower header tank is provided with two header portion rows each having two header portions, and one header of the front header portion row. The refrigerant inlet header portion is connected to the refrigerant inlet header portion, and the one header portion on the same side as the refrigerant inlet header portion in the rear header portion row is the refrigerant outlet header portion and the refrigerant. The refrigerant outlet communicates with the outlet header section, the other header section of both header section rows of the lower header tank serves as an intermediate header section, and the interior of both intermediate header sections communicate with each other. In addition, one intermediate header portion is provided so as to straddle the two header portions of the front and rear header portion rows of the lower header tank, and the rear header of the lower header tank is provided. The total heat exchange pipes that lead to the intermediate header part of the partial row constitute the last second heat exchange pipe group, and the length of the intermediate header part of the rear header part row of the lower header tank is longer than the length of the refrigerant outlet header part The number of heat exchange pipes connected to the refrigerant outlet header section is the same as the number of heat exchange pipes connected to the intermediate header section of the rear header section of the lower header tank. The heat exchanger according to claim 1 or 2, wherein the number of the heat exchangers is larger. The length of the refrigerant inlet header portion of the lower header tank is longer than the length of the intermediate header portion of the front header portion row, the flow passage cross-sectional areas of the respective heat exchange tubes are equal, and the refrigerant inlet header portion of the lower header tank The total heat exchange pipes that lead to the second heat exchange pipe group constitute the second heat exchange pipe group, and the number of heat exchange pipes that lead to the refrigerant inlet header part of the lower header tank is greater than the number of heat exchange pipes that lead to the intermediate header part of the front header part row The heat exchanger according to claim 7, which is also increased. Each header tank is composed of a tank forming member and a pipe connecting plate that covers a surface of the tank forming member facing the heat exchange pipe side, and the tank forming member extends in the length direction of the header tank and heat exchange pipe The header part is formed by having a hollow part opened in the surface which faced the side, and the opening which faced the heat exchange pipe side of the said hollow part is plugged up with the plate for pipe connection. A heat exchanger according to any of the above. The tank forming member includes a first plate and a second plate interposed between the first plate and the pipe connection plate, and a hollow portion of the header portion is formed across the first plate and the second plate. The heat exchanger according to claim 9. An outward bulge extending in the length direction of the first plate is formed in the first plate of the tank forming member, and the internal space of the outward bulge forms a part of the hollow portion of the header portion. The heat exchanger according to claim 10. A supercritical refrigeration cycle comprising a compressor, a gas cooler, an evaporator, a decompressor and an intermediate heat exchanger for exchanging heat between the refrigerant coming out of the gas cooler and the refrigerant coming out of the evaporator, and using a supercritical refrigerant A supercritical refrigeration cycle in which the evaporator comprises the heat exchanger according to any one of claims 1 to 11.

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