JP2014163639A - Lamination type heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a lamination type heat exchanger exhibiting high heat exchanging performance.SOLUTION: A lamination type heat exchanger 40 includes core parts 41 constituted by laminating core plates 41a, 41b. Offset type fins 41f are arranged in a plurality of refrigerant passages 41rf formed at the core parts 41. The offset type fins 41f promote flow of liquid component of refrigerant and contribute to improve a heat exchange efficiency. Outer edge cylindrical portions 41a2 of the core plates 41a are laminated in multi-layers at outer peripheral surfaces of the core parts 41. End portions of the core parts 41 are provided with end plates 41d. The end plates 41d are thicker than the core plates 41a, 41b. A connecting member 43 acting as an inlet for the refrigerant is connected at an additional connecting part 43b, to a main connecting part 43a around a through-pass passage 41ri for the refrigerant.

Description

  The invention disclosed herein relates to a stacked heat exchanger that exchanges heat between a refrigerant in a refrigeration cycle and a heat medium such as water.

  Patent Documents 1-6 disclose a stacked heat exchanger. In particular, Patent Document 1 discloses a water-cooled stacked heat exchanger that can be used as a condenser.

US Patent Application Publication No. 2012/0234523 JP 2005-147572 A JP 2010-216795 A JP-A-5-1890 JP-A-10-185462 JP 2009-36468 A

  In the stacked heat exchanger disclosed in Patent Document 1, a refrigerant passage is formed between the stacked plates, and unevenness is formed on the plates. However, such a shape cannot sufficiently exchange heat with the refrigerant. From such a viewpoint and other viewpoints, further improvements are required for the stacked heat exchanger.

  One of the objects of the invention is to provide a stacked heat exchanger that exhibits high heat exchange performance.

  Another object of the invention is to provide a stacked heat exchanger that can achieve high pressure resistance.

  Another object of the invention is to provide a stacked heat exchanger in which the internal flow path can be changed in various ways.

  Another object of the invention is to provide a highly miniaturized stacked heat exchanger for a refrigeration cycle.

  Another object of the present invention is to provide a laminated heat exchanger for a refrigeration cycle that can provide a water-cooled heat exchanger and a water-cooled evaporator and that has an internal heat exchange function.

  The present invention employs the following technical means to achieve the above object. It should be noted that the reference numerals in parentheses described in the claims and in this section indicate the correspondence with the specific means described in the embodiments described later as one aspect, and the technical scope of the present invention It is not limited.

  One of the disclosed inventions forms a flat refrigerant passage (41rf) for the refrigerant flowing through the refrigeration cycle and a flat heat medium passage (41wt) for the heat medium that exchanges heat with the refrigerant. In a stacked heat exchanger having a core portion (41, 61) including a plurality of stacked plates (41a, 41b, 641b, 41c, 241c, 741c, 41d, 41e, 61e), a refrigerant passage (41rf ) Connecting members (43, 543, 44, 344, 63, 64) for providing an inlet and an outlet for flowing the refrigerant to the heating medium, and a connection for providing an inlet and an outlet for flowing the heat medium to the heat medium passage (41 wt) The inlet and the outlet are set such that the heat medium flowing in the heat medium passage (41 wt) is opposed to the refrigerant flowing in the refrigerant passage (41rf). Connecting member (45, 46, 245, 246, 745, 746, 47, 48, 65, 66, 67, 68, 967, 968), and the core portion is an offset provided at least in the refrigerant passage (41rf) A mold fin (41f) is provided.

  According to this configuration, since the refrigerant and the heat medium flow in opposite directions, good heat exchange is realized. Furthermore, the offset fins provide excellent heat exchange performance for refrigerants that involve a phase change from gas to liquid or from liquid to gas. Therefore, a stacked heat exchanger that exhibits high heat exchange performance is provided.

1 is a block diagram of a thermal system according to a first embodiment of the invention. It is a front view of the lamination type heat exchanger of a 1st embodiment. It is a top view of the lamination type heat exchanger of a 1st embodiment. It is sectional drawing of the laminated heat exchanger of 1st Embodiment. It is a partial expanded sectional view of the lamination type heat exchanger of a 1st embodiment. It is a top view of the division plate of 1st Embodiment. It is a perspective view of the fin of a 1st embodiment. It is a front view which shows the flow path of the laminated heat exchanger of 1st Embodiment. It is a front view of the lamination type heat exchanger concerning a 2nd embodiment of the invention. It is a top view of the division plate of 2nd Embodiment. It is a front view of the laminated heat exchanger which concerns on 3rd Embodiment of invention. It is a front view of the laminated heat exchanger which concerns on 4th Embodiment of invention. It is a front view of the laminated heat exchanger which concerns on 5th Embodiment of invention. It is a partial expanded sectional view of the laminated heat exchanger which concerns on 6th Embodiment of invention. It is a block diagram of the thermal system which concerns on 7th Embodiment of invention. It is a front view which shows the flow path of the laminated heat exchanger of 7th Embodiment. It is a top view of the division plate of 7th Embodiment. It is a block diagram of the thermal system which concerns on 8th Embodiment of invention. It is a front view which shows the flow path of the laminated heat exchanger of 8th Embodiment. It is a block diagram of the thermal system which concerns on 9th Embodiment of invention. It is a front view which shows the flow path of the laminated heat exchanger of 9th Embodiment. It is a block diagram of the thermal system which concerns on 10th Embodiment of invention. It is a block diagram of the thermal system which concerns on 11th Embodiment of invention. It is a front view which shows the flow path of the laminated heat exchanger of 11th Embodiment. It is a block diagram of the thermal system which concerns on 12th Embodiment of invention. It is a block diagram of the thermal system which concerns on 13th Embodiment of invention. It is a block diagram of the thermal system which concerns on 14th Embodiment of invention. It is a block diagram of the thermal system which concerns on 15th Embodiment of invention. It is a block diagram of the thermal system which concerns on 16th Embodiment of invention.

  A plurality of modes for carrying out the invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Further, in the following embodiments, the correspondence corresponding to the matters corresponding to the matters described in the preceding embodiments is indicated by adding reference numerals that differ only by one hundred or more, and redundant description may be omitted. . Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not explicitly stated unless there is a problem with the combination. Is also possible.

(First embodiment)
As illustrated in FIG. 1, a first embodiment discloses a thermal system 10. The heat system 10 is mounted on a vehicle. The thermal system 10 provides an air conditioner for a vehicle or a temperature control device for equipment mounted on the vehicle. When utilized as an air conditioner, the thermal system 10 provides heating and / or cooling. When utilized as a temperature control device, the thermal system 10 provides a heat source for heating and / or a cold source for cooling. The thermal system 10 has a refrigeration cycle 20. The refrigeration cycle 20 is a vapor compression refrigeration cycle 20 that provides a low temperature and a high temperature by compressing the vapor of the refrigerant. The refrigerant is also called a first heat medium. Furthermore, the heat system 10 includes an auxiliary system 30 through which a heat medium that exchanges heat with the refrigerant of the refrigeration cycle 20 flows. The auxiliary system 30 circulates cooling water mainly composed of water as a heat medium. The cooling water is also called a second heat medium. The auxiliary system 30 can also be referred to as a high-temperature system that is thermally coupled to the radiator of the refrigeration cycle 20 or a first auxiliary system.

  The refrigeration cycle 20 includes a compressor 21, a heat exchanger 40, a decompressor 22, and a heat exchanger 23 arranged in a circulation type refrigerant path. The compressor 21 sucks in the refrigerant, compresses the sucked refrigerant, and discharges the compressed refrigerant.

  The heat exchanger 40 is a stacked heat exchanger for providing heat exchange between water and refrigerant. The heat exchanger 40 functions as a radiator. The heat exchanger 40 performs heat dissipation from the high-temperature and high-pressure refrigerant supplied from the compressor 21. The heat exchanger 40 exchanges heat with the water of the auxiliary system 30. The heat exchanger 40 can also be referred to as a stacked water-refrigerant heat exchanger for a refrigeration cycle. The heat exchanger 40 can also be referred to as a stacked water-refrigerant radiator. In the heating use or the heating use, the heat exchanger 40 provides a use side heat exchanger that heats a use side medium such as air for air conditioning.

  The decompressor 22 provides a low-temperature and low-pressure refrigerant by decompressing the high-pressure refrigerant that has radiated heat in the heat exchanger 40. The heat exchanger 23 exchanges heat between the low-temperature and low-pressure refrigerant supplied from the decompressor 22 and the heat source medium. The heat exchanger 23 functions as an evaporator. The heat exchanger 23 is also called a heat absorber. In the cooling use or the cooling use, the heat exchanger 23 provides a use side heat exchanger that cools a use side medium such as air-conditioning air.

  The auxiliary system 30 includes a pump 31 and a heat exchanger 32 arranged in a circulation type water path. The pump 31 circulates water in the auxiliary system 30. The heat exchanger 32 performs heat dissipation from the water flowing through the auxiliary system 30. The heat exchanger 32 exchanges heat with air, for example. A heat exchanger 40 is also arranged in the water path of the auxiliary system 30. The auxiliary system 30 supplies cooling water to the heat exchanger 40. Therefore, the auxiliary system 30 provides a heat carrying means provided on the high temperature side of the refrigeration cycle 20. The heat of the refrigeration cycle 20 is radiated to the cooling water via the heat exchanger 40 and further radiated from the heat exchanger 32. In the heating application, the air for air conditioning or the object is heated by the heat exchanger 32.

  In FIG. 2, the heat exchanger 40 includes a core portion 41 for heat exchange configured by stacking a plurality of metal plates, that is, plates. A refrigerant passage for the refrigerant and a water passage for water are defined between the adjacent plates. The core part 41 defines a plurality of passages therein. Each passage is a flat passage. The core part 41 has a plurality of refrigerant passages for the refrigerant and a plurality of water passages for the cooling water. In the core portion 41, the refrigerant passages and the water passages are alternately arranged in the stacking direction. The water passage is also referred to as a heat medium passage for the heat medium.

  The core part 41 is a substantially rectangular parallelepiped. The vertical direction in the figure corresponds to the stacking direction of the plates. This direction is called the stacking direction. The left-right direction in the drawing is orthogonal to the stacking direction of the core portions 41 and corresponds to the longitudinal direction of the passage formed in the core portion 41. This direction is called the lateral direction. The depth direction in the figure is orthogonal to the stacking direction of the core portions 41 and corresponds to the short direction of the passage formed in the core portion 41. This direction is called the width direction. As shown in the figure, the heat exchanger 40 can be mounted on a vehicle with the stacking direction positioned parallel to the direction of gravity. However, the heat exchanger 40 may be mounted on the vehicle with the stacking direction positioned parallel to the horizontal direction.

  The heat exchanger 40 includes a reinforcing plate 42 joined to the end portion of the core portion 41. The reinforcing plate 42 is obviously thicker than the other plates constituting the core portion 41. The reinforcing plate 42 is provided so as to cover a wide area in a planar shape at the end of the core portion 41. Further, the reinforcing plate 42 has a bent edge that is bent perpendicularly from its plane. The bent edge increases the rigidity of the reinforcing plate 42.

  The heat exchanger 40 includes a connection member 43 for inlet of the refrigerant. The heat exchanger 40 includes a connection member 44 for the outlet of the refrigerant. The connection members 43 and 44 are connectors called block joints. The connection members 43 and 44 have passage holes 43c and 44c for the refrigerant and bolt holes 43d and 44d for screwing the bolts. The heat exchanger 40 includes a connection member 45 for an inlet of cooling water. The heat exchanger 40 includes a connection member 46 for the outlet of the cooling water. The connection members 45 and 46 are tubular connectors for connecting hoses.

  As illustrated in FIG. 3, the core portion 41 has a quadrilateral end face. The core part 41 has a plurality of through passages 41ri, 41ro, 41wi, 41wo extending in the stacking direction. These through passages 41ri, 41ro, 41wi, 41wo are arranged at the corners of the core portion 41. The through passages 41 ri, 41 ro, 41 wi, 41 wo are distributed and arranged at the four corners of the core part 41. The through passages 41ri and 41ro for the refrigerant are arranged at two corners located diagonally of the core part 41. The through passages 41 wi and 41 wo for cooling water are arranged at two corners located on the diagonal of the core portion 41. The through passages 41ri and 41ro and the through passages 41wi and 41wo are arranged on different diagonal lines.

  The through passage 41ri in the drawing communicates with a corner portion at one end of the flat refrigerant passage and provides an inlet or an outlet. The through passage 41ro communicates with a diagonal corner at the other end of the flat refrigerant passage and provides an outlet or an inlet. The through passage 41wi communicates with a corner portion at one end of the flat water passage and provides an inlet or an outlet. The through passage 41wo communicates with the corner of the diagonal position at the other end of the flat water passage and provides an outlet or an inlet. Such an arrangement of the passages is effective for suppressing a dead flow area in a flat passage. This arrangement of the passage allows the coolant or water to flow through the entire flat passage.

  FIG. 4 illustrates a cross section taken along line IV-IV illustrated in FIG. In this figure, hatching is omitted for clarity. As illustrated, the core portion 41 is configured by stacking a plurality of plates 41a, 41b, 41c, 41d, and 41e. The core portion 41 includes core plates 41a, 41b, and 41c for forming a refrigerant passage and a water passage. The core part 41 includes end plates 41d and 41e arranged at both ends of the laminated body of the core plates 41a, 41b and 41c. The end plates 41d and 41e are clearly thicker and more rigid than the core plates 41a, 41b and 41c. According to this configuration, the pressure resistance of the core portion 41 is improved by the end plates 41d and 41e. An offset type fin 41f is disposed between the core plates 41a, 41b, and 41c. These plates 41a, 41b, 41c, 41d, 41e and fins 41f are made of an aluminum alloy. These plates 41a, 41b, 41c, 41d, 41e and the fins 41f are joined by brazing.

  FIG. 5 is a partially enlarged cross-sectional view in the vicinity of the connection member 43. The figure is hatched. A flat refrigerant passage 41rf or a flat water passage 41wt is formed between adjacent core plates 41a, 41b, 41c. The plurality of core plates 41a and 41b are alternately stacked to form a plurality of refrigerant passages 41rf and a plurality of water passages 41wt. The plurality of refrigerant passages 41rf and the plurality of water passages 41wt are alternately stacked. The refrigerant passage 41rf in the stacking direction is thinner than the water passage 41wt. The fins 41e are disposed in both the refrigerant passage 41rf and the water passage 41wt.

  The core plate 41a is also called a cooling plate. The core plate 41a has four passage cylindrical portions 41a1 for providing the through passages 41ri, 41ro, 41wi, 41wo. In the figure, a passage cylindrical portion 41a1 for providing the through passage 41ri is shown. The core plate 41a has an outer peripheral cylindrical portion 41a2 that extends and is exposed on the outer peripheral surface of the core portion 41. Further, the core plate 41a has a plate portion 41a3 extending between the cylindrical portions.

  The outer cylindrical portion 41a2 is slightly inclined outward so as to expand toward the opening end. Further, the outer edge cylindrical portion 41a2 extends high in the stacking direction. The outer cylindrical portion 41a2 extends higher than the height corresponding to the two-layer refrigerant passage 41rf or the two-layer water passage 41wt. In the illustrated example, the outer cylindrical portion 41a2 extends over a height corresponding to the two-layer refrigerant passage 41rf and the two-layer water passage 41wt. As a result, on the outer peripheral surface of the core portion 41, at least two outer edge cylindrical portions 41a2 are positioned so as to overlap each other. This configuration contributes to increasing the strength on the outer peripheral surface.

  The core plate 41b is also called an intermediate plate. The core plate 41b has four passage cylindrical portions 41b1 for providing the through passages 41ri, 41ro, 41wi, 41wo. In the drawing, a passage cylindrical portion 41b1 for providing the through passage 41ri is shown. The core plate 41b has an outer edge cylindrical portion 41b2 extending along the outer edge cylindrical portion 41a2 of the core plate 41a. Furthermore, the core plate 41b has a plate portion 41b3 extending between the cylindrical portions.

  The passage tubular portion 41a1 and the passage tubular portion 41b1 extend in opposite directions with respect to the stacking direction. The passage tubular portion 41a1 and the passage tubular portion 41b1 are arranged to be fitted inside and outside. The core plates 41a and 41b have four openings in the passage cylindrical portions 41a1 and 41b1 for providing the through passages 41ri, 41ro, 41wi, and 41wo.

  The core plate 41 b is not exposed on the outer peripheral surface of the core portion 41. The height of the outer cylindrical portion 41b2 corresponds to the thickness of the water passage 41wt. As a result, in the outer peripheral part of the core part 41, the outer edge cylindrical part 41b2 is laminated without entering between the two outer edge cylindrical parts 41a2.

  The core plates 41a and 41b have outer cylindrical portions 41a2 and 41b2 that are positioned on the outer periphery of the core portion 41 and overlap each other. The outer edge cylindrical portion 41a2 of the core plate 41a and the outer edge cylindrical portion 41b2 of the core plate 41b overlap, so that one core plate 41b and two core plates 41a are positioned outside the flat water passage 41wt. It is done. In other words, the triple core plates 41a and 41b are arranged outside the flat water passage 41wt. The outer cylindrical portions 41a2 and 41b2 are overlapped at least twice on the outer periphery of the core portion. The outer edge cylindrical portions 41 a 2 and 41 b 2 are partially overlapped on the outer periphery of the core portion 41 in a triple manner. According to this configuration, since the core plate is laminated on the outer periphery of the core portion, the outer periphery of the core portion is reinforced. This configuration contributes to realizing high strength outside the water passage 41 wt.

  As illustrated in FIG. 6, the core plate 41c has openings that provide the through passages 41ro and 41wo, but does not include openings that provide the through passages 41ri and 41wi, and closes their positions. The core plate 41c is also referred to as a partition plate 41c. The partition plate 41c divides the plurality of passages 41rf and 41wt in the heat exchanger 40 into a plurality of groups. The partition plate 41c provides a flow path that flows through these groups in series. The partition plate 41 c provides a partition plate for setting a flow path of the refrigerant and / or water in the core portion 41. Only one or several partition plates 41 c are provided in the core portion 41. In this embodiment, the partition plate 41c is provided by changing the shape of the core plate 41b. The core plate 41b has four passage cylindrical portions 41b1. The partition plate 41c also has four passage cylindrical portions 41b1. However, the partition plate 41c is closed without opening at least one of them.

  By forming at least one closed portion in the partition plate 41 c, a U-turn channel is formed in the core portion 41. The U-turn channel is positioned so as to lie down along the horizontal direction with respect to the stacking direction of the plates. According to this configuration, multistage flow paths are formed in the stacking direction. Further, the partition plate 41c makes it possible to set the positions of the connection members 43 and 44 on the core portion 41 and the positions of the connection members 45 and 46 to desirable positions.

  Returning to FIG. 4 and FIG. 5, the connection members 43 and 44 are metal block-like members. The connection members 43 and 44 are joined to the core portion 41 at the main first joint portions 43a and 44a around the through passage 41ri. The connection members 43 and 44 are mainly joined to the end plates 41d and 41e. The connection members 43 and 44 and the core part 41 are joined by brazing.

  Further, the connection members 43 and 44 have additional second joint portions 43b and 44b that are separated from the through passage 41ri and located closer to the center of the core portion 41 than the through passage 41ri. The second joint portions 43 b and 44 b are formed so as to protrude from the connection members 43 and 44 toward the core portion 41 in a foot shape. The distance between the outer edge of the core part 41 and the second joint parts 43b and 44b is larger than the distance between the outer edge of the core part 41 and the through passage 41ri.

  The second joint portions 43b and 44b suppress the deformation when the core portion 41 is expanded and / or contracted in the stacking direction. Further, the second joint portions 43b and 4b suppress the destruction of the first joint portions 43a and 44a when the above deformation occurs.

  As described above, the connection members 43 and 44 include the first joint portions 43 a and 44 a that are provided around the passage 41 ri for flowing the refrigerant or the heat medium and joined to the core portion 41. Furthermore, the connection members 43 and 44 include second joint portions 43b and 44b that are provided at positions closer to the center than the first joint portions 43a and 44a on the end surface in the stacking direction of the core portion 41 and are joined to the core portion 41. . According to this configuration, the connection members 43 and 44 are provided across the first joint portions 43a and 44a and the second joint portions 43b and 44b. The connection members 43 and 44 suppress the deformation of the core portion 41 between the first joint portions 43a and 44a and the second joint portions 43b and 44b. Therefore, the pressure resistance of the core part 41 is improved.

  As illustrated in FIG. 7, the fin 41 f is a so-called offset type fin. The fin 41f may also be called a divided fin. The fin 41f is made of an aluminum alloy. The fin 41fe is a corrugated plate. The fin 41f is in contact with the adjacent core plates 41a and 41b at the top thereof so that heat can be transferred. The fin 41f has a large number of slits communicating between both surfaces. The slit extends over the entire height direction of the fin 41f. The fins 41f are arranged so that the refrigerant RF flows in the direction of the arrow shown in the figure.

  The fin 41f can be viewed as an aggregate of a plurality of band-like portions 41g. One band-like portion 41g has a width WD along the flow direction. One band-like portion 41g is formed in a trapezoidal wave shape having a pitch PT in the direction orthogonal to the flow direction. Two band-like portions 41g adjacent in the flow direction are arranged so as to be shifted in a direction orthogonal to the flow direction by a quarter pitch (1 / 4PT).

  The fins 41f provide a number of tip portions in the refrigerant passage 41rf and the water passage 41wt. These tips improve heat exchange performance.

  The large number of large slits provided in the fin 41f promotes the flow of the refrigerant liquid component from the plate surface of the fin 41f. For this reason, the liquid component tends to spread throughout the refrigerant passage 41rf. As a result, the unevenness of the liquid refrigerant in the refrigerant passage 41rf is suppressed.

  Further, the flow of the refrigerant liquid component is promoted, so that the liquid film on the plate surface of the fin 41f is kept thin. As a result, the refrigerant phase change efficiently occurs on the plate surface of the fin 41f. In the process of condensing the refrigerant, the condensation of the refrigerant is promoted. On the other hand, in the process of evaporating the refrigerant, the evaporation of the liquid refrigerant is promoted.

  As shown in FIG. 8, the refrigerant RF flows in the heat exchanger 40 as indicated by solid arrows. In the heat exchanger 40, the water WT flows as indicated by the dashed arrows. The refrigerant and water flow as counterflows in the heat exchanger 40. Therefore, favorable heat exchange is realized between the refrigerant and water.

  The partition plate 41c divides a plurality of passages 41rf for the refrigerant in the heat exchanger 40 into two groups. The partition plate 41c has a closed portion that does not open in one of the through passages 41ri and 41ro. This blockage provides the division. Furthermore, the partition plate 41c arranges these two groups of passages 41rf in series between the refrigerant inlet and outlet, that is, between the connection members 43 and 44. The partition plate 41c has an opening in the other one of the through passages 41ri and 41ro. This opening provides the series arrangement. As a result, the two groups of passages 41rf provide serial flow paths.

  The partition plate 41c divides a plurality of passages 41wt for water in the heat exchanger 40 into two groups. The partition plate 41c has a closed portion that does not open in one of the through passages 41wi and 41wo. This blockage provides the division. Furthermore, the partition plate 41c arranges these two groups of passages 41wt in series between the water inlet and outlet, that is, between the connection members 45 and 46. The partition plate 41c has an opening in the other one of the through passages 41wi and 41wo. This opening provides the series arrangement. As a result, the two groups of passages 41 wt provide serial flow paths.

  In the illustrated example, the two groups are positioned at the top and bottom of the heat exchanger 40. The connection members 43 and 44 and the connection members 45 and 46 are used as an inlet and an outlet, respectively, so that the refrigerant and water are opposed to each other in the core portion 41. In other words, the connection members 43, 44, 45, and 46 are assigned inlets and outlets so that the heat medium flowing in the heat medium passage 41wt is opposed to the refrigerant flowing in the refrigerant passage 41rf. Is done. As a result, a counter flow is obtained in one group. Furthermore, a counter flow is also obtained in the other group. According to this configuration, the counter flow of the coolant and water is formed over a long distance.

  In this embodiment, the core plates 41a, 41b, and 41c include a partition plate 41c that divides the refrigerant passage 41rf and / or the heat medium passage 41wt in the core portion 41 into a plurality of groups and communicates these groups in series. . The partition plate 41c has a closing portion that closes the through passages 41ri, 41ro, 41wi, 41wo extending from the connection members 43, 44. The core plates 41a, 41b other than the partition plate 41c have openings that provide all of the through passages 41ri, 41ro, 41wi, 41wo extending from the connection members 43, 44.

  According to this embodiment, the connection members 43 and 44 and the connection members 45 and 46 can be dispersedly arranged on both end faces of the core portion 41. Further, the connecting members 43 and 44 and the connecting members 45 and 46 can be concentrated on one side of the core portion 41 in the lateral direction, that is, on the left side in the drawing. Such an arrangement of the inlet and outlet for the refrigerant and water makes it possible to arrange the refrigerant distribution connecting member and the water pipe in a straight line. Therefore, it contributes to the improvement of mountability of the core portion 41 in the vehicle. Moreover, the said arrangement contributes to the improvement of the connection work of piping.

  When the heat system 10 operates, the refrigeration cycle 20 supplies a high-temperature and high-pressure refrigerant to the heat exchanger 40. The auxiliary system 30 supplies water to the heat exchanger 40. The refrigerant and water exchange heat in the core portion 41. The refrigerant is cooled and condensed by water. Furthermore, the refrigerant is supercooled by water. Thereby, the efficiency of the refrigeration cycle 20 can be increased.

(Second Embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, the counter flow is formed in the entire core portion 41. Instead, in this embodiment, a counter flow is formed in a part of the core portion 41.

  As illustrated in FIG. 9, the heat exchanger 40 includes a pipe 245 that is an inlet of water and a connecting member 246 that is an outlet of water on one end face. The connecting member 245 and the connecting member 246 are disposed at diagonally positioned corners of the upper end surface in the drawing. These connecting members 245 and 246 extend in parallel. The connection members 43 and 44 are arranged in a distributed manner on both end surfaces of the core portion 41. The connection members 43 and 44 are concentrated on one side in the lateral direction. Furthermore, in this embodiment, a partition plate 241c is used.

  As illustrated in FIG. 10, the partition plate 241c has a blocking portion in the through passage 41ri. The partition plate 241c has openings in the through passages 41ro, 41wi, and 41wo. As a result, the partition plate 241c divides only the plurality of passages 41rf for the refrigerant into two groups. The partition plate 241c does not divide the plurality of passages 41rwt for water.

  In this embodiment, a U-turn flow path is formed in the core portion 41 along the lateral direction for the refrigerant. All of the plurality of passages 41 wt formed in the core portion 41 are connected in parallel between the connection members 245 and 246. Since the connecting members 245 and 246 are concentrated on one end face, a flow path for U-shaped water along the stacking direction is formed in the core portion 41. According to this structure, the length of the flow path for the refrigerant can be increased. Further, the refrigerant and water can be counterflowed in approximately half of the flow path for the refrigerant.

(Third embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, the partition plates 41c and 241c are used. In this embodiment, no compartment plate is used.

  As illustrated in FIG. 11, the heat exchanger 40 includes a connection member 43 and a connection member 46 on one end surface. Furthermore, the heat exchanger 40 has a connection member 245 and a connection member 344 as a refrigerant outlet on the other end face. In this embodiment, no compartment plate is used. For this reason, all of the plurality of passages 41rf formed in the core portion 41 are connected in parallel between the connection members 43 and 344. Since the connection members 43 and 344 are distributed on both surfaces, a flow path for the S-shaped refrigerant is formed in the core portion 41. All of the plurality of passages 41 wt formed in the core portion 41 are connected in parallel between the connection members 245 and 46. Since the connecting members 245 and 46 are distributed on both surfaces, a flow path for S-shaped water is formed in the core portion 41. Also in this embodiment, the counter flow is provided in the entire core portion 41.

(Fourth embodiment)
This embodiment is a modification based on the preceding embodiment. As illustrated in FIG. 12, the heat exchanger 40 has a connection member 43 on one end face. Furthermore, the heat exchanger 40 has connection members 245 and 246 and a connection member 344 on the other end surface. In this embodiment, no compartment plate is used. For this reason, all of the plurality of passages 41rf formed in the core portion 41 are connected in parallel between the connection members 43 and 344. Since the connection members 43 and 344 are distributed on both surfaces, a flow path for the S-shaped refrigerant is formed in the core portion 41. Also in this embodiment, the counter flow is provided in the entire core portion 41.

(Fifth embodiment)
This embodiment is a modification based on the preceding embodiment. As illustrated in FIG. 13, the heat exchanger 40 includes connection members 245 and 246 and a connection member 344 on one end surface. Furthermore, the heat exchanger 40 has a connection member 543 for the inlet of the refrigerant on the same end surface. In this embodiment, no compartment plate is used. For this reason, all of the plurality of passages 41rf formed in the core portion 41 are connected in parallel between the connection members 543 and 344. Since the connecting members 543 and 344 are concentrated on one end surface, a flow path for a U-shaped refrigerant along the stacking direction is formed in the core portion 41. Also in this embodiment, the counter flow is provided in the entire core portion 41.

(Sixth embodiment)
This embodiment is a modification based on the preceding embodiment. In the said embodiment, in the outer peripheral part of the core part 41, the core plates 41a and 41b were piled up in the position corresponding to a water path. In this embodiment, the core plates 41a and 41b are stacked three times at positions corresponding to the refrigerant passages.

  As shown in FIG. 14, the core plate 641b is bent so as to overlap the other core plate 41a outside the passage for the refrigerant. Thereby, the rigidity of the core part 41 in the outer side of a refrigerant path can be improved.

(Seventh embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, the heat exchanger 40 is cooled only by the auxiliary system 30. Instead, in this embodiment, the heat exchanger 740 cooled by the plurality of auxiliary systems 30 and 50 is employed.

  As illustrated in FIG. 15, the heat system 10 includes an auxiliary system 50 through which a heat medium that exchanges heat with the refrigerant of the refrigeration cycle 20 flows. The auxiliary system 50 circulates cooling water mainly composed of water as a heat medium. The cooling water is also called a third heat medium. The auxiliary system 50 can also be referred to as a low-temperature system thermally coupled to the evaporator of the refrigeration cycle 20 or a second auxiliary system.

  The refrigeration cycle 20 includes a heat exchanger 740. The heat exchanger 740 is a stacked heat exchanger for providing water-refrigerant heat exchange. The heat exchanger 740 functions as a heat radiator. The heat exchanger 740 includes multi-stage heat exchange units 40a and 40b that radiate the refrigerant in stages.

  The front stage 40a is disposed upstream of the rear stage 40b in the refrigerant flow. The front stage 40 a cools the high-temperature and high-pressure refrigerant supplied from the compressor 21. Water is supplied from the auxiliary system 30 to the front stage 40a. The front stage 40 a provides heat exchange between the refrigerant and the water of the auxiliary system 30.

  The rear stage 40b is disposed downstream of the front stage 40a in the refrigerant flow. The rear stage 40b further cools the refrigerant cooled in the front stage 40a. Water is supplied from the auxiliary system 50 to the rear stage 40b. The rear stage 40 b provides heat exchange between the refrigerant and the water of the auxiliary system 50.

  The refrigeration cycle 20 includes a heat exchanger 60. The heat exchanger 60 is a stacked heat exchanger for providing water-refrigerant heat exchange. The heat exchanger 60 functions as an evaporator. The heat exchanger 60 has the same structure as the heat exchanger 40 in the above-described embodiment. The stacked heat exchanger disclosed herein can be used as both a radiator and an evaporator. The heat exchanger 60 is configured by stacking a plurality of plates corresponding to the core plates 41a, 41b, and 41c. The heat exchanger 60 has a refrigerant passage corresponding to the refrigerant passage 41rf and a water passage corresponding to the water passage 41wt.

  The heat exchanger 60 performs heat absorption to the low-temperature and low-pressure refrigerant supplied from the decompressor 22. The heat exchanger 60 exchanges heat with the water of the auxiliary system 50. The heat exchanger 60 can also be referred to as a stacked water-refrigerant heat exchanger for a refrigeration cycle. The heat exchanger 60 can also be referred to as a stacked water-refrigerant evaporator. In the cooling application or the cooling application, the heat exchanger 60 provides a usage-side heat exchanger that cools a usage-side medium such as air-conditioning air.

  The auxiliary system 50 includes a pump 51 and a heat exchanger 52 arranged in a circulation type water path. The pump 51 circulates water in the auxiliary system 50. The heat exchanger 52 performs heat absorption to the water flowing through the auxiliary system 50. The heat exchanger 52 exchanges heat with air, for example. The auxiliary system 50 has a pipe configured to supply water to the rear stage 40b of the heat exchanger 740. A heat exchanger 60 is also disposed in the water path of the auxiliary system 50. The auxiliary system 50 supplies cooling water to the heat exchanger 60. Therefore, the auxiliary system 50 provides a heat carrying means provided on the low temperature side of the refrigeration cycle 20. The refrigeration cycle 20 absorbs heat from the cooling water via the heat exchanger 60. In the cooling application, the air for air conditioning or the object is cooled by the heat exchanger 52.

  In this configuration, the water of the auxiliary system 50 is cooled by the refrigeration cycle 20. As a result, the temperature of the water in the auxiliary system 50 is lower than the temperature of the water in the auxiliary system 30. Therefore, the relatively high temperature water WT (H) is supplied to the front stage 40a. Relatively low temperature water WT (C) is supplied to the rear stage 40b. The front stage 40a functions as a condenser that condenses the refrigerant. The latter stage 40b functions as a supercooler that further supercools the condensed refrigerant. Thereby, the heat exchanger 40 supplies the supercooled refrigerant to the decompressor 22.

  As shown in FIG. 16, the heat exchanger 740 includes connecting members 43 and 44 for the inlet and outlet of the refrigerant. Furthermore, the heat exchanger 740 includes connection members 745 and 746 for water inlets and outlets connected to the auxiliary system 30. The connection members 745 and 746 are disposed on one end surface of the core portion 41. The heat exchanger 740 includes connection members 47 and 48 for water inlets and outlets connected to the auxiliary system 50. The connection members 47 and 48 are disposed on the other end surface of the core portion 41.

  As illustrated in FIG. 17, the partition plate 741c has a blocking portion in the through passages 41ri, 41wi, 41wo. The partition plate 741c has an opening in the through passage 41ro. As a result, the partition plate 741c divides the plurality of passages 41rf for the refrigerant into two groups. Furthermore, the partition plate 741c arranges the two groups of passages 41rf in series. On the other hand, the partition plate 741c completely divides the plurality of passages 41wt for water into two groups and does not communicate these groups. As a result, the front stage 40a and the rear stage 40b are partitioned in the core portion 41 and formed separately.

  In this embodiment, a U-turn flow path is formed in the core portion 41 along the lateral direction for the refrigerant. The plurality of passages 41 wt belonging to one group are connected in parallel between the connection members 745 and 746. Since the connecting members 745 and 746 are concentrated on one end face, a flow path for the U-shaped water WT (H) along the stacking direction is formed in the core portion 41. The plurality of passages 41 wt belonging to the other group are connected in parallel between the connection members 47 and 48. Since the connecting members 47 and 48 are concentrated on one end surface, a flow path for the U-shaped water WT (C) along the stacking direction is formed in the core portion 41. According to this structure, the length of the flow path for the refrigerant can be increased. Further, the refrigerant and water can be counterflowed in the entire flow path for the refrigerant.

(Eighth embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, the water WT (C) of the second auxiliary system 50 is supplied to the rear stage 40b. Instead, in this embodiment, the heat exchanger 60 is also provided with a front stage 60a and a rear stage 60b. Furthermore, in this embodiment, the 3rd auxiliary | assistant system 70 which provides heat exchange between the back | latter stage 40b and the back | latter stage 60b is employ | adopted.

  As illustrated in FIG. 18, the heat system 10 includes a heat exchanger 740. Furthermore, the heat system 10 includes a heat exchanger 860. The heat exchanger 860 has the same structure as the heat exchanger 740. The heat exchanger 860 includes multi-stage heat exchange units 60a and 60b that cause the refrigerant to absorb heat step by step.

  The front stage 60a is disposed upstream of the rear stage 60b in the refrigerant flow. The front stage 60a heats the low-temperature and low-pressure refrigerant supplied from the decompressor 22 to absorb heat. Water is supplied from the auxiliary system 50 to the front stage 60a. The front stage 60 a provides heat exchange between the refrigerant and the water of the auxiliary system 50.

  The rear stage 60b is disposed downstream of the front stage 60a in the refrigerant flow. The rear stage 60b further absorbs heat by the refrigerant that has absorbed heat in the front stage 60a. Water is supplied from the auxiliary system 70 to the rear stage 60b. The rear stage 60 b provides heat exchange between the refrigerant and the water of the auxiliary system 70.

  The auxiliary system 70 thermally couples the rear stage 40b and the rear stage 60b. The auxiliary system 70 includes a bump 71 in a path through which water circulates. In the auxiliary system 70, a rear stage 40b and a rear stage 60b are arranged. Therefore, the auxiliary system 70 allows water to circulate between the rear stage 40b and the rear stage 60b.

  As illustrated in FIG. 19, the heat exchanger 860 includes the same components as the heat exchanger 740. The heat exchanger 860 has a core portion 61. The core part 61 has the same structure as the core part 41 described above. The core portion 61 is partitioned into a front stage 60a and a rear stage 60b by a partition plate 61c. The partition plate 61c has the same shape as the partition plate 741c. The heat exchanger 860 includes connection members 63 and 64 for the refrigerant inlet and outlet. The heat exchanger 860 includes connection members 65 and 66 for water inlet and outlet connected to the auxiliary system 50. The connection members 65 and 66 are disposed on one end face of the core portion 61. The heat exchanger 860 includes connection members 67 and 68 for water inlets and outlets connected to the auxiliary system 70. The connection members 67 and 68 are disposed on the other end surface of the core portion 61.

  According to this embodiment, the water of the auxiliary system 70 is cooled by the low-temperature and low-pressure refrigerant in the rear stage 60b. The water of the auxiliary system 70 is supplied to the rear stage 40b. As a result, the water in the auxiliary system 70 cools the refrigerant on the high-pressure side of the refrigeration cycle 20. In the desired operating state, the refrigerant supplied to the decompressor 22 is supercooled. The water of the auxiliary system 70 is heated in the rear stage 40b. The water of the auxiliary system 70 is supplied to the rear stage 60b. As a result, the water in the auxiliary system 70 heats the refrigerant on the low pressure side of the refrigeration cycle 20. In a desirable operating state, the refrigerant sucked into the compressor 21 is overheated. Thus, internal heat exchange of the refrigeration cycle 20 is provided via the auxiliary system 70.

(Ninth embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, the internal heat exchange of the refrigeration cycle 20 is provided through the heat medium different from the water of the auxiliary system 70, that is, the refrigerant. Instead, in this embodiment, direct internal heat exchange is provided using the refrigerant of the refrigeration cycle 20.

  As illustrated in FIG. 20, the heat exchanger 960 includes a front stage 60a and a rear stage 960b. The rear stage 960b provides heat exchange between the low-temperature and low-pressure refrigerant that has passed through the front stage 60a and the high-temperature and high-pressure refrigerant RF (H) that has passed through the heat exchanger 40.

  As illustrated in FIG. 21, the heat exchanger 960 includes the same components as the heat exchanger 860. The heat exchanger 960 includes connection members 967 and 968 for the inlet and outlet of the high-temperature and high-pressure refrigerant RF (H). In this embodiment, the latter stage that provides internal heat exchange between the high-temperature high-pressure refrigerant RF (H) and the low-temperature low-pressure refrigerant RF (C) to a part of the heat exchanger 960 configured as a water-refrigerant heat exchanger. 960b can be provided.

(10th Embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, the internal heat exchanger is configured integrally with the heat exchanger 960. Instead, in this embodiment, an internal heat exchanger is integrally formed with the heat exchanger 1040.

  As illustrated in FIG. 22, the heat exchanger 1040 includes a front stage 40a and a rear stage 1040b. The rear stage 1040b provides heat exchange between the refrigerant that has passed through the front stage 40a and the refrigerant RF (C) that has passed through the heat exchanger 60. In this embodiment, a subsequent stage that provides internal heat exchange between the high-temperature high-pressure refrigerant RF (H) and the low-temperature low-pressure refrigerant RF (C) to a part of the heat exchanger 1040 configured as a water-refrigerant heat exchanger. 1040b can be provided.

  In the seventh embodiment to the tenth embodiment, the core portions 41 and 61 include the former stages 40a and 60a that provide heat exchange between the refrigerant and the first heat medium by using the heat medium as the first heat medium. Prepare. Furthermore, the core parts 41 and 61 are provided with back | latter stage 40b, 60b, 960b, and 1040b which provide the heat exchange between the refrigerant | coolant heat-exchanged in the front | former stage 40a, and the 2nd heat medium which has a temperature different from a 1st heat medium. . This provides a two-stage heat exchange.

  When the refrigerant supplied to the front stage and the rear stage is a refrigerant on the high-pressure side of the refrigeration cycle 20, the second heat medium can be a heat medium WT (C) heat-exchanged with the refrigerant on the low-pressure side of the refrigeration cycle 20. . When the refrigerant supplied to the front stage and the rear stage is the low-pressure side refrigerant of the refrigeration cycle 20, the second heat medium can be the heat medium WT (H) heat-exchanged with the high-pressure side refrigerant of the refrigeration cycle 20. . When the refrigerant supplied to the front stage and the rear stage is the low-pressure side refrigerant of the refrigeration cycle 20, the second heat medium can be the high-pressure side refrigerant RF (H) of the refrigeration cycle. When the refrigerant supplied to the front stage and the rear stage is a refrigerant on the high pressure side of the refrigeration cycle 20, the second heat medium can be the refrigerant RF (C) on the low pressure side of the refrigeration cycle.

(Eleventh embodiment)
This embodiment is a modification based on the preceding embodiment. In the said embodiment, the heat exchanger 40 and the heat exchanger 60 were arrange | positioned as a separate component in the position away from each other. Instead, in this embodiment, the core portion of the heat exchanger 80 provided as a single component includes a high-pressure side heat exchange portion 1140 to which a high-pressure side refrigerant of the refrigeration cycle 20 is supplied, and a refrigeration cycle. 20 low-pressure side heat exchange portion 1160 to which the low-pressure side refrigerant is supplied.

  As illustrated in FIG. 23, the refrigeration cycle 20 includes a composite heat exchanger 80 including a heat exchange portion 1140 and a heat exchange portion 1160. The heat exchanger 80 is a stacked heat exchanger. A heat exchange portion 1140 is provided by a half of the heat exchanger 80. A heat exchange portion 1160 is provided by the remaining half of the heat exchanger 80. Between the heat exchange part 1140 and the heat exchange part 1160, it is divided through the boundary plate which comprises a laminated heat exchanger. This boundary plate provides a heat transfer portion that provides internal heat exchange between the high and low pressure sides of the refrigeration cycle 20.

  As shown in FIG. 24, the heat exchanger 80 is formed by directly joining a stacked heat exchanger that provides the heat exchange portion 1140 and a stacked heat exchanger that provides the heat exchange portion 1160. Is formed. An end plate 41e disposed at the end of the heat exchange portion 1140 and an end plate 61e disposed at the end of the heat exchange portion 1160 are disposed back to back and brazed. End plates 41e, 61e provide the boundary plates. As a result, direct heat conduction between the heat exchange portion 1140 and the heat exchange portion 1160 is possible. This heat conduction provides internal heat exchange.

(Twelfth embodiment)
This embodiment is a modification based on the preceding embodiment. In this embodiment, the refrigeration cycle 20 illustrated in FIG. 25 is employed. The refrigeration cycle 20 employs a stacked heat exchanger that is a water-refrigerant heat exchanger for only the low pressure side heat exchanger, that is, the heat exchanger 60. The refrigeration cycle 20 includes an air-cooled heat exchanger 24. The heat exchanger 24 functions as a radiator. Thus, a water-refrigerant heat exchanger may be adopted only for the low-pressure side heat exchanger.

(13th Embodiment)
This embodiment is a modification based on the preceding embodiment. In this embodiment, the refrigeration cycle 20 illustrated in FIG. 26 is employed. The refrigeration cycle 20 is a reversible refrigeration cycle. The refrigeration cycle 20 includes a switching valve 25 that switches a refrigerant circulation direction. Therefore, the refrigeration cycle 20 can selectively execute a cooling operation for cooling and a heating operation (heat pump operation) for heating.

  When the high-temperature and high-pressure refrigerant compressed by the compressor 21 is supplied to the heat exchanger 24, the heat exchanger 60 functions as an evaporator. On the other hand, when the high-temperature and high-pressure refrigerant compressed by the compressor 21 is supplied to the heat exchanger 60, the heat exchanger 60 functions as a radiator.

  In this configuration, the high-pressure side refrigerant of the refrigeration cycle 20 and the low-pressure side refrigerant of the refrigeration cycle 20 are selectively supplied to the refrigerant passage. Therefore, the heat exchanger 60 can be selectively functioned as a radiator or an evaporator. As a result, the water of the auxiliary system 50 can be cooled or heated by the refrigeration cycle 20.

(14th Embodiment)
This embodiment is a modification based on the preceding embodiment. In this embodiment, the refrigeration cycle 20 illustrated in FIG. 27 is employed. The refrigeration cycle 20 is a bypass refrigeration cycle in which the heat exchanger 60 is selectively positioned on the high pressure side or the low pressure side of the refrigeration cycle 20. The refrigeration cycle 20 can selectively execute a cooling operation for cooling and a heating operation for heating (heat pump operation).

  The refrigeration cycle 20 includes an on-off valve 26 that can bypass the pressure reducer 22. When the on-off valve 26 is opened, the decompressor 22 cannot perform the decompression function. As a result, the high-temperature and high-pressure refrigerant is supplied to the heat exchanger 60. Between the heat exchanger 60 and the compressor 21, a bypass passage including the switching valve 27, the decompressor 28, and the heat exchanger 29 is provided. When the on-off valve 26 is opened, the switching valve 27 is switched so that the refrigerant flows through the bypass passage. As a result, the heat exchanger 29 functions as an evaporator.

  Even in this configuration, the high-pressure side refrigerant of the refrigeration cycle 20 and the low-pressure side refrigerant of the refrigeration cycle 20 are selectively supplied to the refrigerant passage. Therefore, the heat exchanger 60 can be selectively functioned as a radiator or an evaporator. As a result, the water of the auxiliary system 50 can be cooled or heated by the refrigeration cycle 20. In this configuration, the refrigerant flow direction and the water flow direction in the heat exchanger 60 do not change. For this reason, even if the function of the heat exchanger 60 exists in any of a radiator and an evaporator, a counterflow can be obtained.

(Fifteenth embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, only the heat exchanger 40 is disposed in the high pressure portion of the refrigeration cycle 20. In addition to this, another heat exchanger may be additionally provided in the high-pressure portion. FIG. 28 illustrates additional heat exchangers 24a, 24b, 24c. At least one of these can be employed. The heat exchanger 24a is arranged in parallel with the heat exchanger 40 in the refrigerant flow. The heat exchanger 24b is arranged in series upstream of the heat exchanger 40 in the refrigerant flow. The heat exchanger 24c is arranged in series downstream of the heat exchanger 40 in the refrigerant flow.

(Sixteenth embodiment)
This embodiment is a modification based on the preceding embodiment. In the above embodiment, only the heat exchanger 60 is disposed in the low pressure portion of the refrigeration cycle 20. In addition to this, another heat exchanger may be additionally provided in the cold pressure portion. FIG. 29 illustrates additional heat exchangers 23a, 23b, 23c. At least one of these can be employed. The heat exchanger 23a is arranged in parallel with the heat exchanger 60 in the refrigerant flow. The heat exchanger 23b is arranged in series upstream of the heat exchanger 60 in the refrigerant flow. The heat exchanger 23c is arranged in series downstream of the heat exchanger 60 in the refrigerant flow.

(Other embodiments)
The preferred embodiments of the invention have been described above, but the invention is not limited to the above-described embodiments, and various modifications can be made. The structure of the said embodiment is an illustration to the last, Comprising: The technical scope of invention is not limited to the range of these description. The invention is not limited to the combinations shown in the embodiments, and can be implemented independently. Some technical scope of the invention is indicated by the description of the scope of claims, and further includes all modifications within the meaning and scope equivalent to the description of the scope of claims.

  For example, the auxiliary systems 30, 50, and 70 may circulate a heat medium such as oil instead of the cooling water mainly composed of water.

  Further, the fin 41f may be provided only in the passage 41rf for the refrigerant. In this case, no fins may be provided in the passage 41wt for water, or fins having no slits may be provided.

  Moreover, in the said embodiment, some connection members were provided by the tubular connector. Alternatively, all connecting members may be provided by block joints.

10 heat system, 20 refrigeration cycle, 30, 50, 70 auxiliary system,
40, 740, 60, 860, 960, 1040, 80 stacked heat exchanger,
40a, 60a first stage, 40b, 60b, 960b, 1040b latter stage,
41, 61 core, 41rf refrigerant passage, 41 wt water passage,
41a, 41b, 641b core plate,
41c, 241c, 741c partition plate,
41a1, 41b1 passage cylindrical part, 41a2, 41b2 outer edge cylindrical part,
41a3, 41b3 plate part,
41d, 41e, 61e end plate, 41f fin,
41ri, 41ro, 41wi, 41wo through passage,
42 reinforcing plate, 43, 543, 44, 344, 63, 64 connecting member,
43a, 44a first joint, 43b, 44b second joint,
45, 46, 245, 246, 745, 746, 47, 48 connecting member,
65, 66, 67, 68, 967, 968 Connection member.

Claims (18)

A plurality of layers arranged so as to form a flat refrigerant passage (41rf) for the refrigerant flowing in the refrigeration cycle and a flat heat medium passage (41wt) for the heat medium exchanging heat with the refrigerant. In a stacked heat exchanger having a core part (41, 61) including plates (41a, 41b, 641b, 41c, 241c, 741c, 41d, 41e, 61e),
Connecting members (43, 543, 44, 344, 63, 64) for providing an inlet and an outlet for flowing the refrigerant through the refrigerant passage (41rf);
A connection member that provides an inlet and an outlet for allowing a heat medium to flow through the heat medium passage (41 wt), the heat flowing through the heat medium passage (41 wt) with respect to the refrigerant flowing through the refrigerant passage (41rf) Connecting members (45, 46, 245, 246, 745, 746, 47, 48, 65, 66, 67, 68, 967, 968) in which the inlet and the outlet are set so that the medium is in a counterflow Prepared,
The core part is
A laminated heat exchanger comprising at least an offset type fin (41f) provided in the refrigerant passage (41rf). The core part is
A plurality of core plates (41a, 41b, 641b, 41c, 241c, 741c) forming the refrigerant passage and the heat medium passage;
The laminated heat exchanger according to claim 1, further comprising end plates (41d, 41e, 61e) provided at both ends of the laminated body of the core plates and thicker than the core plate. The core plate is
2. The refrigerant passage and / or the heat medium passage in the core portion is divided into a plurality of groups, and partition plates (41c, 241c, 741c) that communicate these groups in series are included. Or the laminated heat exchanger of Claim 2.   4. The stacked heat exchanger according to claim 3, wherein the partition plate has a closing portion that closes a through passage (41ri, 41ro, 41wi, 41wo) extending from the connection member.   5. The laminate according to claim 4, wherein the core plates (41 a, 41 b) other than the partition plates have openings that provide through passages (41 ri, 41 ro, 41 wi, 41 wo) extending from the connection member. Mold heat exchanger.   6. The stacked heat exchanger according to claim 3, wherein the core portion forms a U-turn-shaped flow path along a horizontal direction with respect to a stacking direction of the plates. .   The laminated heat exchange according to any one of claims 1 to 6, wherein the core plate has outer cylindrical portions (41a2, 41b2) that are positioned on an outer periphery of the core portion and overlap each other. vessel.   The stacked heat exchanger according to claim 7, wherein the outer peripheral tubular portions (41a2, 41b2) are overlapped at least twice on the outer periphery of the core portion.   The stacked heat exchanger according to claim 8, wherein the outer peripheral tubular portions (41a2, 41b2) are partially overlapped on the outer periphery of the core portion. The core section provides a heat exchange between the refrigerant and the first heat medium by using the heat medium as a first heat medium (40a, 60a),
The post-stage (40b, 60b) for providing heat exchange between the refrigerant heat-exchanged in the front stage and a second heat medium having a temperature different from that of the first heat medium. The laminated heat exchanger according to claim 9. The refrigerant supplied to the front stage and the rear stage is a high-pressure side refrigerant of the refrigeration cycle,
11. The stacked heat exchanger according to claim 10, wherein the second heat medium is a heat medium (WT (C)) heat-exchanged with a refrigerant on a low-pressure side of the refrigeration cycle. The refrigerant supplied to the front stage and the rear stage is a low-pressure side refrigerant of the refrigeration cycle,
11. The stacked heat exchanger according to claim 10, wherein the second heat medium is a heat medium (WT (H)) heat-exchanged with a refrigerant on a high-pressure side of the refrigeration cycle. The refrigerant supplied to the front stage and the rear stage is a low-pressure side refrigerant of the refrigeration cycle,
The stacked heat exchanger according to claim 10, wherein the second heat medium is a refrigerant (RF (H)) on a high pressure side of the refrigeration cycle. The refrigerant supplied to the front stage and the rear stage is a high-pressure side refrigerant of the refrigeration cycle,
The stacked heat exchanger according to claim 10, wherein the second heat medium is a refrigerant (RF (C)) on a low pressure side of the refrigeration cycle. The connecting member is
A first joint (43a, 44a) provided around the passage (41ri) for flowing the refrigerant or the heat medium and joined to the core;
2. A second joint portion (43 b, 44 b) provided at a position closer to the center than the first joint portion on the end face in the stacking direction of the core portion and joined to the core portion. The stacked heat exchanger according to claim 14.   The lamination according to any one of claims 1 to 15, wherein a refrigerant on a high-pressure side of the refrigeration cycle and a refrigerant on a low-pressure side of the refrigeration cycle are selectively supplied to the refrigerant passage. Mold heat exchanger. The core part is
A high pressure side heat exchange portion (1140) to which a refrigerant on the high pressure side of the refrigeration cycle is supplied;
The laminated heat exchanger according to any one of claims 1 to 16, further comprising a low-pressure side heat exchange portion (1160) to which a refrigerant on a low-pressure side of the refrigeration cycle is supplied. A plate (41e) disposed at an end of the high-pressure side heat exchange portion (1140);
The stacked heat exchanger according to claim 17, wherein a plate (61e) arranged at an end of the low-pressure side heat exchange part (1160) is arranged back to back and joined.

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