Patent Grant
10962307
This application is a U.S. National Phase Application under 35 U.S.C. 371 of International Application No. PCT/JP2014/000901 filed on Feb. 21, 2014 and published in Japanese as WO 2014/132602 A1 on Sep. 4, 2014. This application is based on and claims the benefit of priority from Japanese Patent Application No. 2013-37466 filed on Feb. 27, 2013 and Japanese Patent Application No. 2013-191695 filed on Sep. 17, 2013 The entire disclosures of all of the above applications are incorporated herein by reference.
The present disclosure is related to a stacked heat exchanger in which heat is exchanged between refrigerant of a refrigerating cycle and heat medium.
PTL 1 to PTL 6 disclose stacked heat exchangers. In particular, PTL 1 discloses a water cooled stacked heat exchanger that can be used as a condenser.
In the stacked heat exchanger disclosed in PTL 1, a passage of refrigerant is defined between stacked plates, and irregularities are formed on the plates. However, such a shape makes it impossible to sufficiently perform heat exchange with the refrigerant. From that viewpoint and other viewpoints, a further improvement in the stacked heat exchanger has been demanded.
PTL 7 discloses a stacked heat exchanger that performs a heat exchange between a high temperature fluid and a low temperature fluid. In the stacked heat exchanger, multiple substantially tabular heat transfer plates are stacked on each other at intervals whereby high temperature fluid flow paths and low temperature fluid flow paths are alternately defined between the heat transfer plates.
In PTL 7, irregular shapes are provided on the heat transfer plates, and the respective irregularities of the adjacent heat transfer plates are brazed together. As a result, a heat transfer area is increased by an irregularly shaped portion, and a heat exchange between the high temperature fluid and the low temperature fluid can be promoted.
However, in the stacked heat exchanger disclosed in PTL 7, because the flow path shapes of the high temperature fluid flow paths and the low temperature fluid flow paths are defined by the irregularly shaped portion, the high temperature fluid flow paths and the low temperature fluid flow paths are identical in the flow path shape with each other. This makes it difficult to arbitrarily set the heat transfer area and a flow channel cross-sectional area according to the physical properties of a high temperature fluid and a low temperature fluid, and optimize the heat transfer characteristic and the pressure loss characteristic.
PTL 1: US 2012/0234523 A1
PTL 2: JP 2005-147572 A
PTL 3: JP 2010-216795 A
PTL 4: JP H05-1890 A
PTL 5: JP H10-185462 A
PTL 6: JP 2009-36468 A
PTL 7: JP 5194011 B
One object of the present disclosure is to provide a stacked heat exchanger that exerts a high heat exchanging performance.
Another object of the present disclosure is to provide a stacked heat exchanger that can realize a high pressure resistance.
Still another object of the present disclosure is to provide a stacked heat exchanger that can variously change an internal flow path.
Yet another object of the present disclosure is to provide a stacked heat exchanger which is highly downsized for a refrigeration cycle.
A further object of the present disclosure is to provide a stacked heat exchanger for a refrigeration cycle, which can provide a water cooled heat exchanger and a water cooled evaporator and further has an internal heat exchange function.
According to an aspect of the present disclosure, a stacked heat exchanger includes a core portion having a plurality of plates stacked on each other to define a flat refrigerant passage for refrigerant which flows in a refrigeration cycle, and a flat heat medium passage for heat medium which performs a heat exchange with the refrigerant. The stacked heat exchanger further includes: a connection member that provides an inlet and an outlet for allowing the refrigerant to flow into the refrigerant passage; and a connection member that provides an inlet and an outlet for allowing the heat medium to flow into the heat medium passage, in which the inlet and the outlet are configured in a state where the heat medium flowing into the heat medium passage flows in an opposite direction to that of the refrigerant flowing in the refrigerant passage. The core portion includes an offset fin disposed in at least the refrigerant passage.
According to the above configuration, since the refrigerant and the heat medium flow as counter flows, an excellent heat exchange is realized. Further, the offset fin provides an excellent heat exchanging performance to the refrigerant associated with a phase change from gas to liquid or from liquid to gas. Hence, the stacked heat exchanger exerting the high heat exchanging performance is provided.
According to an aspect of the present disclosure, a stacked heat exchanger includes a heat exchanging unit that performs a heat exchange between a refrigerant of a refrigeration cycle and a heat medium. The heat exchanging unit is formed by stacking a plurality of plate members on each other, and joining the plate members to each other. A plurality of refrigerant flow channels in which the refrigerant flows, and a plurality of heat medium flow channels in which the heat medium flows are defined between the respective plate members. The plurality of refrigerant flow channels and the plurality of heat medium flow channels are arranged side by side in a stacking direction of the plurality of plate members. An inner fin that joins the adjacent plate members to each other, and facilitates a heat exchange between the refrigerant and the heat medium is disposed in each of the plurality of refrigerant flow channels and the plurality of heat medium flow channels. The inner fin disposed in the refrigerant flow channel is a refrigerant side offset fin in which a large number of cut-and-raised parts which are partially cut and raised are formed in a flowing direction of the refrigerant, and the respective cut-and-raised parts adjacent to each other in the flowing direction of the refrigerant offset each other. The inner fin disposed in the heat medium flow channel is a heat medium side offset fin in which a large number of cut-and-raised parts which are partially cut and raised are formed in a flowing direction of the heat medium, and the respective cut-and-raised parts adjacent to each other in the flowing direction of the heat medium offset each other. A refrigerant flow path height which is a length of the refrigerant flow channel in a stacking direction of the plate members is equal to a refrigerant side fin height Frh which is a length of the refrigerant side offset fin in the stacking direction of the plate members. A heat medium flow path height which is a length of the heat medium flow channel in a stacking direction of the plate members is equal to a heat medium side fin height Fwh which is a length of the heat medium side offset fin in the stacking direction of the plate members. The refrigerant side fin height Frw and the heat medium side fin height Fwh are configured to satisfy a relationship of 0.14<Frh/(Frh+Fwh)<0.49.
According to the above configuration, the refrigerant side fin height Frw and the heat medium side fin height Fwh are set to satisfy a relationship of 0.14<Frh/(Frh+Fwh)<0.49 with the results that the heat transfer performance between the refrigerant and the heat medium can be improved while the pressure losses of the refrigerant and the heat medium are reduced. For that reason, the heat exchanging performance can be improved.
According to an aspect of the present disclosure, a stacked heat exchanger includes a heat exchanging unit that performs a heat exchange between a refrigerant of a refrigeration cycle and a heat medium. The heat exchanging unit is formed by stacking a plurality of plate members on each other, and joining the plate members to each other. A plurality of refrigerant flow channels in which the refrigerant flows, and a plurality of heat medium flow channels in which the heat medium flows are defined between the respective plate members. The plurality of refrigerant flow channels and the plurality of heat medium flow channels are arranged side by side in a stacking direction of the plurality of plate members. An inner fin that joins the adjacent plate members to each other, and facilitates a heat exchange between the refrigerant and the heat medium is disposed in each of the plurality of refrigerant flow channels and the plurality of heat medium flow channels. The inner fin disposed in the refrigerant flow channel is a refrigerant side offset fin in which a large number of cut-and-raised parts which are partially cut and raised are formed in a flowing direction of the refrigerant, and the respective cut-and-raised parts adjacent to each other in the flowing direction of the refrigerant offset each other. The inner fin disposed in the heat medium flow channel is a heat medium side offset fin in which a large number of cut-and-raised parts which are partially cut and raised are formed in a flowing direction of the heat medium, and the respective cut-and-raised parts adjacent to each other in the flowing direction of the heat medium offset each other. The heat exchanging unit is disposed in a state where the stacking direction of the plate members intersects with a gravity direction, and the heat exchanging unit has a U-turn portion that U-turns the flow of the refrigerant circulating in the refrigerant flow channel.
According to the above configuration, with the provision of the U-turn portion that U-turns a flow of refrigerant flowing in the refrigerant flow channel in the heat exchanging unit, after the refrigerant diffused once in the refrigerant flow channel before being U-turned is congregated, the refrigerant can be further diffused in the refrigerant flow channel after being U-turned. Further, with the placement of the heat exchanging unit having a stacking direction intersecting with a gravity direction, the liquid-phase refrigerant can be separated by the gas-liquid density difference. With the above configuration, the heat transfer performance can be improved by ensuring the flow channel area (effective heat transfer surface) of the refrigerant flow channel in which the gas-phase refrigerant flows. For that reason, the heat exchanging performance can be improved.
Embodiments of the present disclosure will be described hereafter referring to drawings. In the embodiments, a part that corresponds to a matter described in a preceding embodiment may be assigned with the same reference numeral, and redundant explanation for the part may be omitted. When only a part of a configuration is described in an embodiment, another preceding embodiment may be applied to the other parts of the configuration. The parts may be combined even if it is not explicitly described that the parts can be combined. The embodiments may be partially combined even if it is not explicitly described that the embodiments can be combined, provided there is no harm in the combination.
As illustrated in
The refrigeration cycle 20 includes a compressor 21, a heat exchanger 40, a decompressor 22, and a heat exchanger 23, which are arranged in a circulation refrigerant route. The compressor 21 takes in the refrigerant, compresses the taken refrigerant, and discharges the compressed refrigerant.
The heat exchanger 40 is a stacked heat exchanger for providing a heat exchange between water and the refrigerant. The heat exchanger 40 functions as a radiator. The heat exchanger 40 executes the heat radiation from the refrigerant of high temperature and high pressure, which is supplied from the compressor 21. The heat exchanger 40 performs a heat exchange with water of the auxiliary system 30. The heat exchanger 40 can be also called “stacked water-refrigerant heat exchanger for refrigeration cycle”. The heat exchanger 40 can be also called “stacked water-refrigerant radiator”. In heater applications or heating applications, the heat exchanger 40 provides a user side heat exchanger for heating a user side medium such as conditioning air.
The decompressor 22 decompresses a high pressure refrigerant thermally radiated in the heat exchanger 40 to provide a refrigerant of low temperature and low pressure. The heat exchanger 23 performs a heat exchange between the refrigerant of low temperature and low pressure which is supplied from the decompressor 22 and a heat source medium. The heat exchanger 23 functions as an evaporator. The heat exchanger 23 is also called “heat absorber”. In cooler applications and cooling applications, the heat exchanger 23 provides the user side heat exchanger for cooling the user side medium such as conditioning air.
The auxiliary system 30 includes a pump 31 and a heat exchanger 32, which are disposed in a circulation water pathway. The pump 31 circulates water in the auxiliary system 30. The heat exchanger 32 executes heat radiation from water flowing in the auxiliary system 30. The heat exchanger 32 performs the heat exchange with air. The heat exchanger 40 is also disposed in the water pathway of the auxiliary system 30. The auxiliary system 30 supplies a coolant to the heat exchanger 40. Hence, the auxiliary system 30 provides heat transporting means disposed at a high temperature side of the refrigeration cycle 20. The heat of the refrigeration cycle 20 is radiated to the coolant through the heat exchanger 40, and further radiated from the heat exchanger 32. In the heating applications, the conditioning air or an object is heated by the heat exchanger 32.
Referring to
The core portion 41 is substantially cuboid. A vertical direction in the figure corresponds to the stacking direction of the plates. The direction is called “stacking direction”. A horizontal direction in the figure is orthogonal to the stacking direction of the core portion 41 and corresponds to a longitudinal direction of the passages defined in the core portion 41. The direction is called “transverse direction”. A depth direction in the figure corresponds to a lateral direction of the passages orthogonal to the stacking direction of the core portion 41 and defined in the core portion 41. The direction is called “widthwise direction”. The heat exchanger 40 can be mounted in the vehicle in a state where the stacking direction is positioned in parallel to the gravity direction as shown in the figure. The heat exchanger 40 may be mounted in the vehicle in a state where the stacking direction is positioned in parallel to the horizontal direction.
The heat exchanger 40 includes a reinforcement plate 42 joined to an end of the core portion 41. The reinforcement plate 42 is apparently thicker than other plates configuring the core portion 41. The reinforcement plate 42 is disposed to cover an area extensively spread in a planar shape on an end of the core portion 41. Further, the reinforcement plate 42 has a folded edge bent perpendicularly from a plane thereof. The folded edge enhances the rigidity of the reinforcement plate 42.
The heat exchanger 40 includes a connection member 43 for an inlet of the refrigerant. The heat exchanger 40 includes a connection member 44 for an 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, 44c for the refrigerant, and bolt holes 43d, 44d into which bolts are screwed, respectively. The heat exchanger 40 includes a connection member 45 for an inlet of the coolant. The heat exchanger 40 includes a connection member 46 for an outlet of the coolant. The connection members 45 and 46 are tubular connectors for connection to hoses. The connection members 43 and 44 are refrigerant connection members, and correspond to a first connection member. The connection members 45 and 46 are heat medium connection members, and correspond to a second connection member.
As illustrated in
The through passage 41ri in the figure communicates with the corner on one end of the flat refrigerant passages, and provides an inlet or an outlet. The through passage 41ro communicates with the corner of a diagonal position on the other end of the flat refrigerant passages, and provides an inlet or an outlet. The through passage 41wi communicates with the corner on one end of the flat water passages, and provides an inlet or an outlet. The through passage 41wo communicates with the corner of a diagonal position on the other end of the flat water passages, and provides an inlet or an outlet. The arrangement of those passages is effective for suppressing a death basin in the flat passage. The arrangement of those passages makes it possible to allow the refrigerant or water to flow into the overall flat passages.
The core plates 41a are also called “cooling plates”. Each of the core plates 41a has four passage cylindrical portions 41a1 for providing the through passages 41ri, 41ro, 41wi, and 41wo. In the figure, the passage cylindrical portion 41a1 for providing the through passage 41ri is illustrated. Each of the core plates 41a has an outer cylindrical portion 41a2 extended and exposed out of an outer peripheral surface of the core portion 41. Further, each of the core plates 41a has a plate portion 41a3 spread between those cylindrical portions.
The outer cylindrical portion 41a2 is inclined slightly outward so as to spread toward an opening end. The outer cylindrical portion 41a2 extends highly in the stacking direction. The outer cylindrical portion 41a2 extends to be higher than a height corresponding to two refrigerant passages 41rf or two water passages 41wt. In an example shown in the figure, the outer cylindrical portion 41a2 extends with a height corresponding to the two refrigerant passages 41rf and the two water passages 41wt. As a result, at least the two outer cylindrical portions 41a2 are located to overlap with each other on the outer peripheral surface of the core portion 41. That configuration contributes to an increase in the strength of the outer peripheral surface.
The core plates 41b are also called “intermediate plates”. Each of the core plates 41b has four passage cylindrical portions 41b1 for providing the through passages 41ri, 41ro, 41wi, and 41wo. In the figure, the passage cylindrical portion 41b1 for providing the through passage 41ri is illustrated. Each of the core plates 41b has an outer cylindrical portion 41b2 extended along the outer cylindrical portion 41a2 of each core plate 41a. Further, the core plate 41b has a plate portions 41b3 spread between those cylindrical portions.
The passage cylindrical portions 41a1 and the passage cylindrical portions 41b1 extend in opposite directions to each other along the stacking direction. The passage cylindrical portions 41a1 and the passage cylindrical portions 41b1 are disposed to be fitted to each other inside and outside. The core plates 41a and 41b have four openings for providing the through passages 41ri, 41ro, 41wi, and 41wo in the passage cylindrical portions 41a1 and 41b1, respectively.
Each of the core plates 41b is not exposed to the outer peripheral surface of the core portion 41. A height of the outer cylindrical portions 41b2 corresponds to a thickness of the water passages 41wt. As a result, in the outer peripheral portion of the core portion 41, the outer cylindrical portions 41b2 are stacked without being inserted between the two outer cylindrical portions 41a2.
The core plates 41a and 41b have the outer cylindrical portions 41a2 and 41b2 positioned on an outer periphery of the core portion 41 and stacked on each other, respectively. The outer cylindrical portions 41a2 of the core plates 41a overlap with the outer cylindrical portions 41b2 of the core plates 41b with the results that one core plate 41b and two core plates 41a are located outside of the flat water passage 41wt. In other words, the triple core plates 41a and 41b are arranged outside of each flat water passage 41wt. The outer cylindrical portions 41a2 and 41b2 are at least doubly stacked on each other in the outer periphery of the core portion. The outer cylindrical portions 41a2 and 41b2 are partially triply stacked on each other in the outer periphery of the core portion 41. According to the above configuration, since the core plates are stacked on each other in the outer periphery of the core portion, the outer periphery of the core portion is reinforced. That configuration contributes to a realization of the high strength outside of the water passages 41wt.
As illustrated in
The core plate 41c is also called “partition plate 41c”. The partition plate 41c divides the multiple passages 41rf and 41wt in the heat exchanger 40 into multiple groups. The partition plate 41c provides a flow path flowing in those groups in series. The partition plate 41c provides a partition plate for setting a flow route of the refrigerant and/or water within the core portion 41. Only one or several partition plates 41c are provided in the core portion 41. In this embodiment, the partition plate 41c is provided by changing a shape of the core plate 41b. The core plate 41b has the four passage cylindrical portions 41b1. The partition plate 41c also has the four passage cylindrical portions 41b1. However, the partition plate 41c closes at least one of those passage cylindrical portions without opening.
With the formation of at least one closing portion in the partition plate 41c, a U-turn shaped flow path is defined in the core portion 41. The U-turn shaped flow path is a flow path extending along a horizontal direction orthogonal to the stacking direction of the plates, and positioned so that the U-shape is toppled over sideways. In other words, the core portion 41 defines the U-shaped flow path that extends toward one way in the horizontal direction orthogonal to the stacking direction of the core plates, thereafter extends in the stacking direction of the core plates, and then extends toward the other way in the horizontal direction orthogonal to the stacking direction of the core plates. With the above configuration, multistage flow paths are defined in the stacking direction. The provision of 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 on the core portion 41 to desired positions.
Returning to
Further, the connection members 43 and 44 have additional second joints 43b and 44b which are separated from the through passage 41ri, and located closer to a center of the core portion 41 than the through passage 41ri. The second joints 43b and 44b are formed to project toward the core portion 41 from the connection members 43 and 44 in a leg shape. A distance between an outer edge of the core portion 41 and the second joints 43b, 44b is larger than a distance between an outer edge of the core portion 41 and the through passage 41ri.
When the core portion 41 is deformed to expand and/or contract in the stacking direction, the second joints 43b and 44b suppress such deformations. When the core portion 41 is deformed, the second joints 43b and 44b suppress destruction in the first joints 43a and 44a, respectively.
As described above, the connection members 43 and 44 include the first joints 43a and 44a disposed around the passage 41ri for allowing the refrigerant or the heat medium to flow therein, and joined to the core portion 41, respectively. Further, the connection members 43 and 44 include the second joints 43b and 44b joined to the core portion 41 disposed at positions closer to the center than the first joints 43a and 44a on an end surface in the stacking direction of the core portion 41, respectively. According to the above configuration, the connection members 43 and 44 are disposed across the first joints 43a and 44a, and the second joints 43b and 44b, respectively. The connection members 43 and 44 suppress the deformation of the core portion 41 between the first joints 43a, 44a, and the second joints 43b, 44b, respectively. Hence, the pressure resistance of the core portion 41 is improved.
As illustrated in
The fin 41f can be regarded as an aggregation of multiple strip portions 41g. Each of the strip portions 41g has a width WD along a flowing direction. Each of the strip portions 41g is molded in a trapezoidal shape having pitches PT in a direction orthogonal to the flowing direction. Two of the strip portions 41g adjacent to each other in the flowing direction are displaced from each other in the direction orthogonal to the flowing direction by ¼ pitches (¼ PT).
The fin 41f provides a large number of tip portions in the refrigerant passages 41rf and the water passages 41wt. Those tip portions improve the heat exchanging performance.
The large number of large slits provided in the fin 41f facilitates flow down of a refrigerant liquid component from a plate surface of the fin 41f. For that reason, the liquid component is likely to spread over the overall refrigerant passages 41rf. As a result, the deviation of the liquid refrigerant in the refrigerant passages 41rf is suppressed.
With the facilitation of the flow down of the refrigerant liquid component, a thickness of a liquid film on the plate surface of the fin 41f is maintained thinly. This effectively causes a phase change in the refrigerant on the plate surface of the fin 41f. In a process of condensing the refrigerant, the condensation of the refrigerant is facilitated. On the other hand, in a process of evaporating the refrigerant, the evaporation of the liquid refrigerant is facilitated.
As illustrated in
The partition plate 41c divides the multiple passages 41rf for the refrigerant in the heat exchanger 40 into two groups. The partition plate 41c has a closing portion that is not opened in one of the through passages 41ri and 41ro. The above division is provided by the closing portion. Further, in the partition plate 41c, those two groups of refrigerant passages 41rf are arranged in series between an inlet and an outlet of the refrigerant, that is, between the connection members 43 and 44. The partition plate 41c has an opening in the other of the through passages 41ri and 41ro. The above series arrangement is provided by the opening. As a result, the two groups of refrigerant passages 41rf provide a series flow path.
The partition plate 41c divides the multiple passages 41wt for the water in the heat exchanger 40 into two groups. The partition plate 41c has a closing portion that is not opened in one of the through passages 41wi and 41wo. The above division is provided by the closing portion. Further, in the partition plate 41c, those two groups of passages 41wt are arranged in series between an inlet and an outlet of the water, that is, between the connection members 45 and 46. The partition plate 41c has an opening in the other of the through passages 41wi and 41wo. The above series arrangement is provided by the opening. As a result, the two groups of passages 41wt provide a series flow path.
In an example shown in the figure, two groups are positioned on an upper portion and a lower portion of the heat exchanger 40. The connection members 43, 44, and the connection members 45, 46 are used as inlets and outlets, respectively, so that the refrigerant and the water flow in the core portion 41 in opposite directions. In other words, the inlets and the outlets are allocated, and configured to the connection members 43, 44, 45, and 46 so that the heat medium flowing in the heat medium passages 41wt flows in the opposite direction to that of the refrigerant flowing in the refrigerant passages 41rf. As a result, the counter flows are obtained for one group. Further, the counter flows are obtained for the other group. According to the above configuration, the counter flows of the refrigerant and the water are produced over a long distance.
In this embodiment, the core plates 41a, 41b, and 41c include the partition plate 41c that divides the refrigerant passages 41rf and/or the heat medium passages 41wt in the core portion 41 into multiple groups, and communicates with those groups in series. The partition plate 41c has closing portions for closing the through passages 41ri, 41ro, 41wi, and 41wo extending from the connection members 43, 44, 45, and 46. The core plates 41a and 41b other than the partition plate 41c have openings for providing all of the through passages 41ri, 41ro, 41wi, and 41wo extending from the connection members 43, 44, 45, and 46, respectively.
According to this embodiment, the connection members 43, 44, and the connection members 45, 46 can be dispersively arranged on both end surfaces of the core portion 41. The connection members 43, 44, and the connection members 45, 46 can be concentrated on one side of the core portion 41 in the horizontal direction, that is, on a left side in the figure. The arrangement of the inlets and the outlets for the refrigerant and the water makes it possible to arrange a refrigerant piping and a water piping linearly. Hence, the arrangement contributes to an improvement in mountability of the core portion 41 in the vehicle. The above arrangement also contributes to an improvement in connection work of the piping.
When the thermal system 10 operates, the refrigeration cycle 20 supplies the refrigerant of the high temperature and high pressure to the heat exchanger 40. The auxiliary system 30 supplies water to the heat exchanger 40. The refrigerant and the water perform the heat exchange within the core portion 41. The refrigerant is cooled and condensed by the water. Further, the refrigerant is subcooled by the water. This makes it possible to enhance the efficiency of the refrigeration cycle 20.
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiment, the counter flows are produced in the overall core portion 41. Instead, in this embodiment, the counter flows are produced in a part of the core portion 41.
As illustrated in
As illustrated in
In this embodiment, a U-turn shaped flow path along a horizontal direction for refrigerant is defined in the core portion 41. All of the passages 41wt defined in the core portion 41 are connected in parallel to each other between the connection members 245 and 246. Since the connection members 245 and 246 are intensively arranged on one of the end surfaces, a U-shaped flow path for water along the stacking direction is defined in the core portion 41. According to the above configuration, a length of the flow path for the refrigerant can be lengthened. The refrigerant and the water can flow in the opposite directions in about half of the flow path for the refrigerant.
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, the partition plates 41c and 241c are used. In this embodiment, no partition plate is used.
As illustrated in
This embodiment is a modification with the preceding embodiment as a basic configuration. As illustrated in
This embodiment is a modification with the preceding embodiment as a basic configuration. As illustrated in
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, the core plates 41a and 41b are triply stacked on each other at a position corresponding to the water passage in the outer periphery of the core portion 41. In this embodiment, the core plates 41a and 41b are triply stacked on each other at a position corresponding to the refrigerant passage.
As illustrated in
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, the heat exchanger 40 is cooled by only the auxiliary system 30. Instead, in this embodiment, a heat exchanger 740 which is cooled by multiple auxiliary systems 30 and 50 is employed.
As illustrated in
The refrigeration cycle 20 has a heat exchanger 740. The heat exchanger 740 is a stacked heat exchanger for providing a heat exchange between water and the refrigerant. The heat exchanger 740 functions as a radiator. The heat exchanger 740 has heat exchanging units 40a and 40b of multiple stages which radiate heat from refrigerant in a stepwise fashion.
A previous stage 40a is disposed on an upstream side of a subsequent stage 40b in a refrigerant flow. The previous stage 40a cools the refrigerant of high temperature and high pressure, which is supplied from a compressor 21. Water is supplied to the previous stage 40a from the auxiliary system 30. The previous stage 40a provides a heat exchange between the refrigerant and water in the auxiliary system 30.
The subsequent stage 40b is disposed on a downstream side of the previous stage 40a in the refrigerant flow. The subsequent stage 40b further cools the refrigerant cooled in the previous stage 40a. Water is supplied to the subsequent stage 40b from the auxiliary system 50. The subsequent stage 40b provides a heat exchange between the refrigerant and water in the auxiliary system 50.
The refrigeration cycle 20 has a heat exchanger 60. The heat exchanger 60 is a stacked heat exchanger for providing a heat exchange between water and the refrigerant. The heat exchanger 60 functions as an evaporator. The heat exchanger 60 has the same structure as that of the heat exchanger 40 in the above embodiments. The stacked heat exchanger disclosed in the present specification can be used as not only a radiator but also an evaporator. The heat exchanger 60 is configured by stacking multiple plates corresponding to the core plates 41a, 41b, and 41c. The heat exchanger 60 has refrigerant passages corresponding to the refrigerant passages 41rf and water passages corresponding to the water passages 41wt.
The heat exchanger 60 executes a heat absorption on the refrigerant of low temperature and low pressure which is supplied from the decompressor 22. The heat exchanger 60 performs a heat exchange with water of the auxiliary system 50. The heat exchanger 60 can be also called “stacked water-refrigerant heat exchanger for refrigeration cycle”. The heat exchanger 60 can be also called “stacked water-refrigerant evaporator”. In cooler applications and cooling applications, the heat exchanger 60 provides the user side heat exchanger for cooling the user side medium such as conditioning air.
The auxiliary system 50 includes a pump 51 and a heat exchanger 52, which are disposed in a circulation water pathway. The pump 51 circulates water in the auxiliary system 50. The heat exchanger 52 executes heat absorption on water flowing in the auxiliary system 50. The heat exchanger 52 performs the heat exchange with air. The auxiliary system 50 has a piping configured to supply water to the subsequent stage 40b of the heat exchanger 740. The heat exchanger 60 is also disposed in the water pathway of the auxiliary system 50. The auxiliary system 50 supplies a coolant to the heat exchanger 60. Hence, the auxiliary system 50 provides heat transporting means disposed at a low temperature side of the refrigeration cycle 20. The refrigeration cycle 20 absorbs heat from the coolant through the heat exchanger 60. In the cooling applications, the conditioning air or an object is heated by the heat exchanger 52.
In the above configuration, the water in the auxiliary system 50 is cooled by the refrigeration cycle 20. As a result, a temperature of the water in the auxiliary system 50 is lower than a temperature of the water in the auxiliary system 30. Hence, a water WT (H) of a relatively high temperature is supplied to the previous stage 40a. A water WT (C) of a relatively low temperature is supplied to the subsequent stage 40b. The previous stage 40a functions as a condenser for condensing the refrigerant. The subsequent stage 40b functions as a subcooler for further subcooling the condensed refrigerant. As a result, the heat exchanger 40 supplies a subcooling refrigerant to the decompressor 22.
As illustrated in
As illustrated in
In this embodiment, a U-turn shaped flow path along a horizontal direction for refrigerant is defined in the core portion 41. The multiple passages 41wt belonging to one of the groups are connected in parallel to each other between the connection members 745 and 746. Since the connection members 745 and 746 are intensively arranged on one of the end surfaces, a U-shaped flow path for water WT(H) along the stacking direction is defined in the core portion 41. The multiple passages 41wt belonging to the other group are connected in parallel to each other between the connection members 47 and 48. Since the connection members 47 and 48 are intensively arranged on one of the end surfaces, a U-shaped flow path for water WT(C) along the stacking direction is defined in the core portion 41. According to the above configuration, a length of the flow path for the refrigerant can be lengthened. The refrigerant and the water can flow in the opposite directions in the overall flow path for the refrigerant.
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, the water WT(C) of the second auxiliary system 50 is supplied to the subsequent stage 40b. Instead, in this embodiment, a previous stage 60a and a subsequent stage 60b are also disposed in the heat exchanger 60. Further, in this embodiment, a third auxiliary system 70 that provides a heat exchange between the subsequent stage 40b and the subsequent stage 60b is employed.
As illustrated in
The previous stage 60a is disposed on an upstream side of the subsequent stage 60b in a refrigerant flow. The previous stage 60a heats the refrigerant of low temperature and low pressure, which is supplied from a decompressor 22, to thereby allow the refrigerant to absorb the heat. Water is supplied to the previous stage 60a from the auxiliary system 50. The previous stage 60a provides a heat exchange between the refrigerant and water in the auxiliary system 50.
The subsequent stage 60b is disposed on a downstream side of the previous stage 60a in the refrigerant flow. The subsequent stage 60b allows the refrigerant that has absorbed the heat in the previous stage 60a to further absorb heat. Water is supplied to the subsequent stage 60b from the auxiliary system 70. The subsequent stage 60b provides a heat exchange between the refrigerant and water in the auxiliary system 70.
The auxiliary system 70 thermally couples between the subsequent stage 40b and the subsequent stage 60b. The auxiliary system 70 includes a pump 71 in a route in which water circulates. The subsequent stage 40b and the subsequent stage 60b are arranged in the auxiliary system 70. Hence, the auxiliary system 70 allows the water to flow so as to circulate between the subsequent stage 40b and the subsequent stage 60b.
As illustrated in
According to this embodiment, the water in the auxiliary system 70 is cooled by the refrigerant of low temperature and low pressure in the subsequent stage 60b. The water in the auxiliary system 70 is supplied to the subsequent stage 40b. As a result, the water in the auxiliary system 70 cools the refrigerant on a high pressure side of the refrigeration cycle 20. In a desired operating state, the refrigerant to be supplied to the decompressor 22 is subcooled. The water in the auxiliary system 70 is heated in the subsequent stage 40b. The water in the auxiliary system 70 is supplied to the subsequent stage 60b. As a result, the water in the auxiliary system 70 heats the refrigerant on a low pressure side of the refrigeration cycle 20. In the desired operating state, the refrigerant drawn into the compressor 21 is superheated. As described above, an internal heat exchange of the refrigeration cycle 20 is provided through the auxiliary system 70.
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, the internal heat exchange of the refrigeration cycle 20 is provided through the water in the auxiliary system 70, that is, a heat medium different from the refrigerant. Instead, in this embodiment, a direct internal heat exchange is provided with the use of the refrigerant in the refrigeration cycle 20.
As illustrated in
As illustrated in
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, the internal heat exchanger is integrated with the heat exchanger 960. Instead, in this embodiment, an internal heat exchanger is integrated with a heat exchanger 1040.
As illustrated in
In the seventh embodiment to the tenth embodiment, core portions 41 and 61 include the previous stages 40a and 60a that provide the heat exchange between the refrigerant and the first heat medium with the use of the heat medium as the first heat medium, respectively. Further, the core portions 41 and 61 include subsequent stages 40b, 60b, 960b, and 1040b that provide the heat exchange between the refrigerant that has performed the heat exchange in the previous stage 40a and the second heat medium having a temperature different from that of the first heat medium. As a result, the heat exchange of two stages is provided.
When the refrigerant to be supplied to the previous stage and the subsequent stage is a refrigerant on a high pressure side of the refrigeration cycle 20, the second heat medium can be set as a heat medium WT(C) that has performed a heat exchange with the refrigerant on a low pressure side of the refrigeration cycle 20. When the refrigerant to be supplied to the previous stage and the subsequent stage is a refrigerant on a low pressure side of the refrigeration cycle 20, the second heat medium can be set as a heat medium WT(H) that has performed a heat exchange with the refrigerant on a high pressure side of the refrigeration cycle 20. When the refrigerant to be supplied to the previous stage and the subsequent stage is a refrigerant on a low pressure side of the refrigeration cycle 20, the second heat medium can be set as a refrigerant RF(H) on a high pressure side of the refrigeration cycle. When the refrigerant to be supplied to the previous stage and the subsequent stage is a refrigerant on a high pressure side of the refrigeration cycle 20, the second heat medium can be set as a refrigerant RF(C) on a low pressure side of the refrigeration cycle.
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, the heat exchanger 40 and the heat exchanger 60 are arranged at positions distant from each other as separate components. Instead, in this embodiment, a core portion of a heat exchanger 80 disposed as a single component includes a heat exchange portion 1140 on a high pressure side to which a refrigerant on the high pressure side of the refrigeration cycle 20 is supplied, and a heat exchange portion 1160 on a low pressure side to which a refrigerant on the low pressure side of the refrigeration cycle 20 is supplied.
As illustrated in
As illustrated in
This embodiment is a modification with the preceding embodiment as a basic configuration. In this embodiment, a refrigeration cycle 20 illustrated in
This embodiment is a modification with the preceding embodiment as a basic configuration. In this embodiment, a refrigeration cycle 20 illustrated in
When a high-temperature high-pressure refrigerant compressed by a compressor 21 is supplied to a heat exchanger 24, a heat exchanger 60 functions as an evaporator. On the other hand, when the high-temperature high-pressure refrigerant compressed by the compressor 21 is supplied to the heat exchanger 60, the heat exchanger 60 functions as a radiator.
In the above configuration, the refrigerant on a high pressure side of the refrigeration cycle 20 and the refrigerant on a low pressure side of the refrigeration cycle 20 are selectively supplied to the refrigerant passages. Hence, the heat exchanger 60 can selectively function as the radiator or the evaporator. As a result, water in an auxiliary system 50 can be cooled or heated by the refrigeration cycle 20.
This embodiment is a modification with the preceding embodiment as a basic configuration. In this embodiment, a refrigeration cycle 20 illustrated in
The refrigeration cycle 20 includes an opening-and-closing valve 26 that can bypass the decompressor 22. When the opening-and-closing valve 26 is opened, the decompressor 22 does not exert a decompression function. As a result, the refrigerant of high temperature and high pressure is supplied to the heat exchanger 60. A bypass passage having a switching valve 27, a decompressor 28, and a heat exchanger 29 is disposed between the heat exchanger 60 and a compressor 21. When the opening-and-closing valve 26 is opened, the switching valve 27 switches so that the refrigerant flows in the bypass passage. As a result, the heat exchanger 29 functions as an evaporator.
Similarly, in the above configuration, the refrigerant on a high pressure side of the refrigeration cycle 20 and the refrigerant on a low pressure side of the refrigeration cycle 20 are selectively supplied to the refrigerant passages. Hence, the heat exchanger 60 can selectively function as the radiator or the evaporator. As a result, water in an auxiliary system 50 can be cooled or heated by the refrigeration cycle 20. In the above configuration, a flowing direction of the refrigerant and a flowing direction of the water in the heat exchanger 60 do not change. For that reason, even if the heat exchanger 60 functions as any one of the radiator and the evaporator, the counter flow can be obtained.
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, only a heat exchanger 40 is disposed in a high pressure portion of a refrigeration cycle 20. In addition, another heat exchanger may be additionally provided in the high pressure portion.
This embodiment is a modification with the preceding embodiment as a basic configuration. In the above embodiments, only the heat exchanger 60 is disposed in the low pressure portion of the refrigeration cycle 20. In addition, another heat exchanger may be additionally provided in the low pressure portion.
A seventeenth embodiment will be described with reference to
The coolant can be, for example, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluidic, or antifreeze material. In this embodiment, the coolant is made of ethylene glycol-based antifreeze (LLC).
The heat exchanger 2010 is formed integrally by stacking a large number of plate members 2011 on each other, and joining the plate members 2011 to each other. In the following description, the stacking direction (vertical direction in an example of
The plate members 2011 are formed of a substantially rectangular slender plate member, and, for example, a two-sided clad material obtained by cladding a brazing material on both surfaces of an aluminum core is used as a specific material.
Protruding portions 2111 that protrude in a substantially plate stacking direction (in other words, a direction substantially orthogonal to the plate surfaces of the plate members 2011) are formed on respective outer peripheral edges of the substantially rectangular plate members 2011. The large number of plate members 2011 are joined to each other by brazing the respective protruding portions 2111 together in a state where the plate members 2011 are stacked on each other.
The large number of plate members 2011 is arranged in a state where protruding tips of the protruding portions 2111 face the same side (substantially downward in an example of
The large number of plate members 2011 forms a heat exchanging unit 2012, a refrigerant first tank space 2013, a refrigerant second tank space 2014, a coolant first tank space 2015, and a coolant second tank space 2016. The heat exchanging unit 2012 is configured by multiple refrigerant flow channels 2121 and multiple coolant flow channels 2122.
The multiple refrigerant flow channels 2121 and the multiple coolant flow channels 2122 are formed between the respective multiple plate members 2011. A longitudinal direction of the refrigerant flow channels 2121 and the coolant flow channels 2122 matches a longitudinal direction of the plate members 2011.
The refrigerant flow channels 2121 and the coolant flow channels 2122 are alternately stacked (in parallel) in the plate stacking direction one by one. The plate members 2011 function as partition walls for partitioning the refrigerant flow channels 2121 and the coolant flow channels 2122. A heat exchange between the refrigerant flowing in the refrigerant flow channels 2121 and the coolant flowing in the coolant flow channels 2122 is performed through the plate members 2011.
The refrigerant first tank space 2013 and the coolant first tank space 2015 are arranged on one side (left side in an example of
The refrigerant first tank space 2013 and the refrigerant second tank space 2014 distribute and collect the refrigerant with respect to the multiple refrigerant flow channels 2121. The coolant first tank space 2015 and the coolant second tank space 2016 distribute and collect the coolant with respect to the multiple coolant flow channels 2122.
The refrigerant first tank space 2013, the refrigerant second tank space 2014, the coolant first tank space 2015, and the coolant second tank space 2016 are configured by communication holes defined in four corners (four corners of right, left, up, and down in an example of
A first joint 2021 and a first coolant pipe 2022 are fitted to a first endmost plate member 2011A located on the plate stacking direction one end side of the multiple plate members 2011 configuring the heat exchanging unit 2012. The first joint 2021 is a member for joining a refrigerant piping, and forms a refrigerant inlet 2101 of the heat exchanger 2010. The first coolant pipe 2022 provides a coolant outlet 2102 of the heat exchanger 2010.
A second joint 2023 and a second coolant pipe 2024 are fitted to a second endmost plate member 2011B located on the plate stacking direction other end side of the multiple plate members 2011 configuring the heat exchanging unit 2012. The second joint 2023 is a member for joining a refrigerant piping, and forms a refrigerant outlet 2103 of the heat exchanger 2010. The second coolant pipe 2024 provides a coolant inlet 2104 of the heat exchanger 2010.
The refrigerant inlet 2101 and the refrigerant outlet 2103 communicate with the refrigerant first tank space 2013. The coolant outlet 2102 and the coolant inlet 2104 communicate with the coolant first tank space 2015.
As illustrated in
A center plate member 2011C is located substantially in the center of the multiple plate members 2011 configuring the heat exchanging unit 2012 in the plate stacking direction. The center plate member 2011C has a closing portion 2011g that closes the protruding portion 2011f configuring the refrigerant first tank space 2013. With the above configuration, the refrigerant first tank space 2013 is partitioned into two spaces in the plate stacking direction. The closing portion 2011g is formed integrally with the protruding portion 2011f, that is, the center plate member 2011C.
Therefore, as indicated by solid arrows in
Although not shown, likewise, in the center plate member 2011C, the protruding portion 2011f configuring the coolant first tank space 2015 is closed. With that configuration, the coolant first tank space 2015 is partitioned into two spaces in the plate stacking direction.
Therefore, as indicated by dashed arrows in
The heat exchanger 2010 is configured so that the flow of refrigerant and the flow of coolant are opposite to each other (counter flow).
An offset fin illustrated in
The offset fin is a plate-like member in which cut-and-raised parts 2030a that are partially cut and raised are formed. A large number of the cut-and-raised parts 2030a are formed in a direction F1 (longitudinal direction of the plate members 2011) which is in parallel to the flowing direction of refrigerant and coolant.
The cut-and-raised parts 2030a adjacent to each other in the direction F1 parallel to the flowing direction of the refrigerant and the coolant offset each other. In an example of
For example, a two-sided clad material obtained by cladding a brazing material on both surfaces of an aluminum core is used as a specific material of the offset fin. The offset fin is joined to both of the adjacent plate members 2011 by brazing.
Therefore, the offset fin configures an inner wall that joins the adjacent plate members 2011 together, and crosses the refrigerant flow channels 2121 and the coolant flow channels 2122 in the plate stacking direction. A length (hereinafter called “flow path height”) of the refrigerant flow channels 2121 and the coolant flow channels 2122 in the plate stacking direction is equal to a length of the offset fin disposed in the refrigerant flow channels 2121 and the coolant flow channels 2122 in the plate stacking direction.
There are two different types of offset fins disposed in the refrigerant flow channels 2121 and the coolant flow channels 2122. Hereinafter, the offset fin disposed in the refrigerant flow channels 2121 is referred to as “refrigerant side offset fin 2301”, and the offset fin disposed in the coolant flow channels 2122 is referred to as “coolant side offset fin 2302”.
A height of the refrigerant side offset fin 2301 in the plate stacking direction is referred to herein as the “fin height Frh of the refrigerant side offset fin 2301”. A height of the coolant side offset fin 2302 in the plate stacking direction is referred to herein as the “fin height Fwh of the coolant side offset fin 2302”.
In embodiments of the present disclosure, the height Frh of the refrigerant side offset fin 2301 is lower than the height Fwh of the coolant side offset fin 2302. For that reason, the flow path height of the refrigerant flow channels 2121 is lower than the flow path height of the coolant flow channels 2122.
The present inventors have studied a change in heat transfer performance and pressure loss when changing the height Frh of the refrigerant side offset fin 2301 relative to the fixed height Fwh of the coolant side offset fin 2302.
When one refrigerant side offset fin 2301 and one coolant side offset fin 2302 are provided as one set, the heat transfer performance, or the pressure loss of the refrigerant or the coolant, is related to a ratio (Frh/(Frh+Fwh)), as illustrated in
Referring to
As indicated by the solid line in
As represented by the one-dot chain line in
Therefore, the ratio of the fin height of the refrigerant side offset fin 2301 to a total fin height (Frh+Fwh) is set to be larger than 0.14 and smaller than 0.49. In other words, the ratio of the fin height of the refrigerant side offset fin 2301 to a total fin height (Frh+Fwh) is set to satisfy a relationship of 0.14<Frh/(Frh+Fwh)<0.49. As a result, the heat transfer performance between the refrigerant and the coolant can be improved with a reduction in the pressure loss of the refrigerant and the coolant.
As represented by the dashed line in
In this example, as illustrated in
Subsequently, the present inventors have studied a change in the pressure loss of the refrigerant in changing a shape of the refrigerant flow channels 2121.
As illustrated in
A relationship of the aspect ratio of the refrigerant flow channel 2121 or the coolant flow channel 2122 to the pressure loss when the segment length S of the refrigerant side offset fin 2301 is set to L/80 or smaller is illustrated in
Because the coolant is high in viscosity, the coolant is diffused in the coolant flow channels 2122 due to the viscosity of the coolant itself. For that reason, the pressure loss of the coolant in the coolant flow channels 2122 depends on the flow path length. Hence, as indicated by a dashed line in
On the other hand, since a gaseous refrigerant is low in the viscosity, the gaseous refrigerant is unlikely to diffuse into the refrigerant flow channels 2121, and the drift is likely to be generated. On the contrary, as indicated by a solid line in
Incidentally, in the refrigeration cycle, because a coefficient of performance (COP) of the cycle is deteriorated more as the pressure loss of the refrigerant is larger, it is desirable to reduce the pressure loss. As with the coolant flow channels 2122, in the refrigerant flow channels 2121, the pressure loss increases more as the flow path length is longer in a region where the aspect ratio of the refrigerant flow channels 2121 is equal to or larger than 1.3.
In practical use, it is desirable that the pressure loss of the refrigerant falls within 1.5 times of the minimum pressure loss. When the pressure loss of the refrigerant is 1.5 times of the minimum pressure loss, the COP is deteriorated by 5% of the maximum COP. As the aspect ratio of the refrigerant flow channels 2121 becomes larger, a body size of the heat exchanger 2010 is upsized more. Therefore, for the purpose of suppressing a reduction in the COP and downsizing the body size of the heat exchanger 2010, it is desirable that the aspect ratio of the refrigerant flow channels 2121 is set to be equal to or smaller than 4.
Incidentally, the heat exchanging unit 2012 according to this embodiment is disposed in a state where the plate stacking direction intersects with the gravity direction. Specifically, the heat exchanging unit 2012 is disposed in a state where a widthwise direction of the refrigerant flow channels 2121 becomes in parallel to the gravity direction.
In the heat exchanging unit 2012, the refrigerant performs a heat exchange with the coolant, to thereby be condensed and evaporated. When the refrigerant is condensed and evaporated, the heat transmitting rate is improved more as a liquid film of the heat transfer surface is thinner.
As illustrated by a dashed arrow in
In the heat exchanger 2010 according to a comparative example in which the flow of refrigerant circulating in the refrigerant flow channel 2121 is not U-turned, a liquid-phase refrigerant of a gas-liquid two phase refrigerant diffused into the refrigerant flow channel 2121 from the refrigerant inflow portion 2121a is attached to the refrigerant side offset fin 2301, and stays. Because a gas-phase refrigerant is likely to flow in a portion where the liquid-phase refrigerant does not stay, the drift is generated. Once the drift is generated, since an improvement is difficult, the drift is kept to be generated in all of the refrigerant flow channels 2121, and the heat transmitting rate is lowered.
On the contrary, in the heat exchanger 2010 according to this embodiment, in the refrigerant flow channels 2121 before being U-turned, the liquid-phase refrigerant is attached to the refrigerant side offset fin 2301, and stays. The liquid-phase refrigerant moves downward in the gravity direction due to a gas-liquid density difference, and is congregated in the refrigerant outlet portion 2121b. Then, in the refrigerant flow channels 2121 after being U-turned, the refrigerant of the gas-liquid two phase state is again diffused from the refrigerant inflow portion 2121a. As with the refrigerant flow channels 2121 before the U-turn, in the refrigerant flow channels 2121 after being U-turned, the liquid-phase refrigerant is attached to the refrigerant side offset fin 2301, and stays. The liquid-phase refrigerant moves downward in the gravity direction due to a gas-liquid density difference, and is congregated in the refrigerant outlet portion 2121b.
As described above, the flow of refrigerant flowing in the refrigerant flow channel 2121 is U-turned. As a result, after the refrigerant diffused once is congregated in the refrigerant flow channel 2121 before being U-turned, the refrigerant can be further diffused in the refrigerant flow channel 2121 after being U-turned. Further, the heat exchanging unit 2012 is disposed in a state where the plate stacking direction intersects with the gravity direction whereby the liquid-phase refrigerant can be separated by the gas-liquid density difference. With the above configuration, the heat transfer performance can be improved by ensuring the flow path area (effective heat transfer surface) of the refrigerant flow channel 2121 in which the gas-phase refrigerant flows. For that reason, the heat exchanging performance can be improved.
The present disclosure is not limited to the above-mentioned embodiments, and may have various modifications as described below without departing from the gist of the present disclosure.
For example, in the auxiliary systems 30, 50, and 70, a heat medium such as oil may be circulated instead of the coolant mainly containing water.
The fin 41f may be disposed in only the refrigerant passages 41rf for the refrigerant. In that case, any fin may not be provided, or a fin with no slit may be provided in the water passages 41wt for water.
In the above embodiments, a part of the connection members is provided by a pipe-shaped connector. Instead, all of the connection members may be provided by block joints.
In the above seventeenth embodiment, the cooling water is used as the heat medium. However, the heat medium is not limited to this example. For example, the refrigerant is employed as the heat medium, and the respective refrigerants may perform the heat exchange with each other in the heat exchanging unit 2012.
In the seventeenth embodiment, the heat exchanging unit 2012 is arranged in a state where the widthwise direction of the refrigerant flow channels 2121 is in parallel to the gravity direction. However, the arrangement direction of the heat exchanging unit 2012 is not limited to this example. For example, the heat exchanging unit 2012 is arranged in a state where the plate stacking direction intersects with the gravity direction with the results that the liquid-phase refrigerant is congregated on a lower side in the gravity direction due to the gas-liquid density difference, and the effective heat transfer surface can be ensured in the refrigerant flow channels 2121.
In the seventeenth embodiment, the refrigerant flow channels 2121 and the coolant flow channels 2122 are alternately stacked on each other in the plate stacking direction one by one. For example, the refrigerant flow channels 2121 and the coolant flow channels 2122 may be alternately stacked on each other in the plate stacking direction by multiple paths.
In the seventeenth embodiment, the heat exchanger 2010 is configured so that the flow of refrigerant and the flow of coolant are U-turned once, but may be configured so that the flow of refrigerant and the flow of coolant are U-turned by multiple times.
The heat exchanger 2010 may be configured so that the flow of refrigerant and the flow of coolant are not U-turned. In that case, the heat exchanging unit 2012 may be disposed in an arbitrary orientation.
In the seventeenth embodiment, the heat exchanger 2010 is configured so that the flow of refrigerant and the flow of coolant are in opposite directions to each other (counter flow). Alternatively, the heat exchanger 2010 may be configured so that the flow of refrigerant and the flow of coolant are in the same directions as each other (parallel flow).
| Number | Date | Country | Kind |
|---|---|---|---|
| JP2013-037466 | Feb 2013 | JP | national |
| JP2013-191695 | Sep 2013 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2014/000901 | 2/21/2014 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2014/132602 | 9/4/2014 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 3282334 | Stahlheber | Nov 1966 | A |
| 3860065 | Schauls | Jan 1975 | A |
| 4282927 | Simmons | Aug 1981 | A |
| 4804041 | Hasegawa | Feb 1989 | A |
| 4815532 | Sasaki | Mar 1989 | A |
| 4869316 | Yoshida | Sep 1989 | A |
| 5099912 | Tajima et al. | Mar 1992 | A |
| 5560425 | Sugawara | Oct 1996 | A |
| 5845505 | Galus | Dec 1998 | A |
| 6338384 | Sakaue | Jan 2002 | B1 |
| 6340053 | Wu | Jan 2002 | B1 |
| 6394178 | Yoshida et al. | May 2002 | B1 |
| 6415855 | Gerard | Jul 2002 | B2 |
| 6739385 | Brenner | May 2004 | B2 |
| 7469554 | Martins | Dec 2008 | B2 |
| 8418752 | Otahal | Apr 2013 | B2 |
| 9651315 | Cui | May 2017 | B2 |
| 20010010262 | Komoda | Aug 2001 | A1 |
| 20010054499 | Gerard | Dec 2001 | A1 |
| 20020066552 | Komoda | Jun 2002 | A1 |
| 20030010483 | Ikezaki | Jan 2003 | A1 |
| 20050241814 | Hendrix et al. | Nov 2005 | A1 |
| 20050274504 | Torigoe | Dec 2005 | A1 |
| 20060169445 | Sato | Aug 2006 | A1 |
| 20090032231 | Komoda et al. | Feb 2009 | A1 |
| 20100025025 | Tomochika | Feb 2010 | A1 |
| 20100193169 | Yamada | Aug 2010 | A1 |
| 20110239697 | Styles et al. | Oct 2011 | A1 |
| 20110290462 | Andersson et al. | Dec 2011 | A1 |
| 20120031593 | Uno | Feb 2012 | A1 |
| 20120118542 | Kanzaka et al. | May 2012 | A1 |
| 20120234523 | Jouanny et al. | Sep 2012 | A1 |
| 20120234532 | Kuo | Sep 2012 | A1 |
| 20130146257 | Kim et al. | Jun 2013 | A1 |
| 20150083379 | Ito | Mar 2015 | A1 |
| Number | Date | Country |
|---|---|---|
| 19805439 | Aug 1999 | DE |
| 10228263 | Jan 2004 | DE |
| 779481 | Jun 1997 | EP |
| 2846736 | May 2004 | FR |
| S62131196 | Jun 1987 | JP |
| S63173685 | Nov 1988 | JP |
| H0364365 | Jun 1991 | JP |
| H04155191 | May 1992 | JP |
| H05001890 | Jan 1993 | JP |
| H07310958 | Nov 1995 | JP |
| H09166363 | Jun 1997 | JP |
| H10185462 | Jul 1998 | JP |
| H11248392 | Sep 1999 | JP |
| 2000337784 | Dec 2000 | JP |
| 2001116485 | Apr 2001 | JP |
| 2001241800 | Sep 2001 | JP |
| 2002168591 | Jun 2002 | JP |
| 2003185375 | Jul 2003 | JP |
| 2003343993 | Dec 2003 | JP |
| 2004108644 | Apr 2004 | JP |
| 2005147572 | Jun 2005 | JP |
| 2005337528 | Dec 2005 | JP |
| 2007183071 | Jul 2007 | JP |
| 2008082650 | Apr 2008 | JP |
| 2009036468 | Feb 2009 | JP |
| 2010078286 | Apr 2010 | JP |
| 2010216793 | Sep 2010 | JP |
| 2010216795 | Sep 2010 | JP |
| 2011002120 | Jan 2011 | JP |
| 2011002122 | Jan 2011 | JP |
| 2011002146 | Jan 2011 | JP |
| 2011052884 | Mar 2011 | JP |
| 2011214826 | Oct 2011 | JP |
| 2012107784 | Jun 2012 | JP |
| 2012112591 | Jun 2012 | JP |
| 2013506809 | Feb 2013 | JP |
| 5194011 | May 2013 | JP |
| 2013518240 | May 2013 | JP |
| 2013119382 | Jun 2013 | JP |
| 20120002075 | Jan 2012 | KR |
| WO-2008023732 | Feb 2008 | WO |
| Entry |
|---|
| International Search Report and Written Opinion (in Japanese with English Translation) for PCT/JP2014/000901, dated May 20, 2014; ISA/JP. |
| Number | Date | Country | |
|---|---|---|---|
| 20160010929 A1 | Jan 2016 | US |
