WO2014132602A1 - 積層型熱交換器 - Google Patents
積層型熱交換器 Download PDFInfo
- Publication number
- WO2014132602A1 WO2014132602A1 PCT/JP2014/000901 JP2014000901W WO2014132602A1 WO 2014132602 A1 WO2014132602 A1 WO 2014132602A1 JP 2014000901 W JP2014000901 W JP 2014000901W WO 2014132602 A1 WO2014132602 A1 WO 2014132602A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- heat medium
- heat
- plate
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
- F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/02—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the heat-exchange media travelling at an angle to one another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0246—Arrangements for connecting header boxes with flow lines
- F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/007—Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/10—Particular pattern of flow of the heat exchange media
Definitions
- This disclosure relates to a stacked heat exchanger that exchanges heat between a refrigerant and a heat medium in a refrigeration cycle.
- Patent Documents 1-6 disclose a stacked heat exchanger.
- Patent Document 1 discloses a water-cooled stacked heat exchanger that can be used as a condenser.
- Patent Document 7 describes a stacked heat exchanger for exchanging heat between a high-temperature fluid and a low-temperature fluid, and a plurality of substantially flat plate-shaped heat transfer plates are overlapped at intervals to obtain a heat transfer plate. A high-temperature fluid channel and a low-temperature fluid channel are alternately formed between them.
- Patent Document 7 an uneven shape is set on the heat transfer plate, and the unevenness of adjacent heat transfer plates is brazed and joined. Thereby, the heat transfer area can be increased by the concavo-convex shape portion, and heat exchange between the high temperature fluid and the low temperature fluid can be promoted.
- the flow path shapes of the high-temperature fluid flow path and the low-temperature fluid flow path are defined by the concavo-convex portions, so the flow paths of the high-temperature fluid flow path and the low-temperature fluid flow path The shape is the same. For this reason, it becomes difficult to arbitrarily set the heat transfer area, the cross-sectional area of the flow path, etc. according to the physical properties of the high temperature fluid and the low temperature fluid to optimize the heat transfer characteristics and the pressure loss characteristics.
- One of the purposes of the present disclosure is to provide a stacked heat exchanger that exhibits high heat exchange performance.
- Another object of the present disclosure is to provide a stacked heat exchanger that can achieve high pressure resistance.
- Another object of the present disclosure is to provide a stacked heat exchanger that can change the internal flow path in various ways.
- Another object of the present disclosure is to provide a highly miniaturized stacked heat exchanger for a refrigeration cycle.
- Another object of the present disclosure 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 stacked heat exchanger is stacked so as to form a flat refrigerant passage for the refrigerant flowing in the refrigeration cycle and a flat heat medium passage for the heat medium exchanging heat with the refrigerant. And having a core portion including a plurality of plates.
- the stacked heat exchanger includes a connection member that provides an inlet and an outlet for flowing a refrigerant in the refrigerant passage, and a connection member that provides an inlet and an outlet for flowing a heat medium in the heat medium passage, And a connecting member having an inlet and an outlet set so that the heat medium flowing in the heat medium passage is opposed to the refrigerant flowing.
- the core portion includes at least an offset-type fin provided in the refrigerant passage.
- 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.
- the stacked heat exchanger includes a heat exchange unit that exchanges heat between the refrigerant of the refrigeration cycle and the heat medium.
- the heat exchange part is formed by laminating and joining a plurality of plate-like members to each other, and a plurality of refrigerant flow paths through which a refrigerant flows and a heat medium flow between the plurality of plate-like members.
- a plurality of heat medium flow paths are formed.
- the plurality of refrigerant channels and the plurality of heat medium channels are arranged side by side in the stacking direction of the plurality of plate-like members.
- Each of the plurality of refrigerant channels and the plurality of heat medium channels is provided with an inner fin that joins adjacent plate members and promotes heat exchange between the refrigerant and the heat medium.
- Inner fins provided in the refrigerant flow path are refrigerant side offset fins, and a large number of partially raised parts are formed in the refrigerant flow direction, and the adjacent raised parts are adjacent to each other in the refrigerant flow direction. Are offset from each other.
- Inner fins provided in the heat medium flow path are heat medium side offset fins, and a large number of partially raised parts are formed in the flow direction of the heat medium and adjacent to the flow direction of the heat medium. The cut and raised portions are offset from each other.
- the refrigerant flow path height which is the length in the stacking direction of the plate members in the refrigerant flow path, is equal to the refrigerant side fin height Frh, which is the length in the stack direction of the plate members in the refrigerant side offset fin.
- the heat medium flow path height which is the length in the laminating direction of the plate member in the heat medium flow path, is equal to the heat medium side fin height Fwh, which is the length in the laminating direction of the plate member in the heat medium side offset fin. .
- the refrigerant side fin height Frw and the heat medium side fin height Fwh are set so as to satisfy the relationship of 0.14 ⁇ Frh / (Frh + Fwh) ⁇ 0.49.
- the stacked heat exchanger includes a heat exchange unit that exchanges heat between the refrigerant of the refrigeration cycle and the heat medium.
- the heat exchange part is formed by laminating and joining a plurality of plate-like members to each other, and a plurality of refrigerant flow paths through which a refrigerant flows and a heat medium flow between the plurality of plate-like members.
- a plurality of heat medium flow paths are formed.
- the plurality of refrigerant channels and the plurality of heat medium channels are arranged side by side in the stacking direction of the plurality of plate-like members.
- Each of the plurality of refrigerant channels and the plurality of heat medium channels is provided with an inner fin that joins adjacent plate members and promotes heat exchange between the refrigerant and the heat medium.
- Inner fins provided in the refrigerant flow path are refrigerant side offset fins, and a large number of partially raised parts are formed in the refrigerant flow direction, and the adjacent raised parts are adjacent to each other in the refrigerant flow direction. Are offset from each other.
- Inner fins provided in the heat medium flow path are heat medium side offset fins, and a large number of partially raised parts are formed in the flow direction of the heat medium and adjacent to the flow direction of the heat medium. The cut and raised portions are offset from each other.
- the heat exchange part is arranged so that the stacking direction of the plate-like members intersects the direction of gravity, and the heat exchange part has a U-turn part that makes a U-turn the flow of the refrigerant flowing through the refrigerant flow path. .
- the refrigerant after gathering the refrigerant once diffused in the refrigerant flow path before the U-turn by providing a U-turn part that makes the U-turn the flow of the refrigerant flowing through the refrigerant flow path in the heat exchange part,
- the refrigerant can be further diffused in the refrigerant flow path after the U-turn.
- the heat exchange unit so that the stacking direction intersects the direction of gravity, the liquid phase refrigerant can be separated by the gas-liquid density difference.
- the flow passage area (effective heat transfer surface) through which the gas-phase refrigerant flows in the refrigerant flow passage can be ensured, and the heat transfer performance can be improved. For this reason, it becomes possible to improve heat exchange performance.
- 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.
- the thermal system 10 provides heating and / or cooling.
- 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.
- 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 disposed 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.
- 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.
- 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.
- the heat exchanger 40 includes a core part 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.
- 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 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.
- the connection members 43 and 44 are refrigerant connection members and correspond to first connection members.
- the connection members 45 and 46 are heat medium connection members and correspond to second connection members.
- 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 figure 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.
- FIG. 4 illustrates a cross section taken along line IV-IV illustrated in FIG. In this figure, hatching is omitted for clarity.
- 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 41f 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.
- 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 edge 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.
- 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.
- 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 directions opposite to each other 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 41b 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.
- 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.
- 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.
- the core plate 41c has openings for providing the through passages 41ro and 41wo, but does not have openings for providing 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.
- 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.
- the partition plate 41c is closed without opening at least one of them.
- a U-turn channel is formed in the core portion 41 by forming at least one closed portion in the partition plate 41c.
- the U-turn channel is a channel that also extends in the horizontal direction perpendicular to the stacking direction of the plates, and is positioned so that the U-shape is laid down.
- the core portion 41 extends toward one of the lateral directions orthogonal to the stacking direction of the core plates, then extends to the stacking direction of the core plates, and further orthogonal to the stacking direction of the core plates.
- a U-shaped channel extending toward the other side in the lateral direction is formed. According to this configuration, multistage flow paths are formed in the stacking direction.
- 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.
- 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.
- 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.
- 2nd joint part 43b, 44b suppresses those deformation
- 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.
- the fin 41f 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 41f is a wave-shaped 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 fin 41f provides 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.
- 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.
- the refrigerant phase change efficiently occurs on the plate surface of the fin 41f.
- the condensation of the refrigerant is promoted.
- the evaporation of the liquid refrigerant is promoted.
- the refrigerant RF flows in the heat exchanger 40 as indicated by solid arrows.
- 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.
- 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.
- 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.
- 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.
- 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.
- a counter flow is obtained in one group.
- 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.
- 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 blocking portion that blocks the through passages 41ri, 41ro, 41wi, 41wo extending from the connection members 43, 44, 45, 46.
- 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, 45, 46.
- connection members 43 and 44 and the connection members 45 and 46 can be dispersedly arranged on both end surfaces 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.
- 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.
- This embodiment is a modification based on the preceding embodiment.
- the counter flow is formed in the entire core portion 41.
- a counter flow is formed in a part of the core portion 41.
- the heat exchanger 40 has a connecting member 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.
- 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.
- 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.
- the heat exchanger 40 has a connection member 43 and a connection member 46 on one end face. 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.
- 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.
- 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.
- 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.
- 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 heat exchange between water and refrigerant.
- 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.
- 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.
- the water of the auxiliary system 50 is cooled by the refrigeration cycle 20.
- 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.
- the heat exchanger 40 supplies the supercooled refrigerant to the decompressor 22.
- the heat exchanger 740 includes connection members 43 and 44 for the refrigerant inlet and outlet. 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.
- 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.
- the partition plate 741c divides the plurality of passages 41rf for the refrigerant into two groups.
- the partition plate 741c arranges the two groups of passages 41rf in series.
- the partition plate 741c completely divides the plurality of passages 41wt for water into two groups and does not communicate these groups.
- the front stage 40a and the rear stage 40b are partitioned in the core portion 41 and formed separately.
- 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.
- This embodiment is a modification based on the preceding embodiment.
- the water WT (C) of the second auxiliary system 50 is supplied to the rear stage 40b.
- the heat exchanger 60 is also provided with a front stage 60a and a rear stage 60b.
- assistant system 70 which provides heat exchange between the back
- 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.
- 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.
- 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.
- the water in 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.
- the water in the auxiliary system 70 cools the refrigerant on the high-pressure side of the refrigeration cycle 20.
- 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.
- the water in the auxiliary system 70 heats the refrigerant on the low pressure side of the refrigeration cycle 20.
- the refrigerant sucked into the compressor 21 is overheated.
- internal heat exchange of the refrigeration cycle 20 is provided via the auxiliary system 70.
- 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.
- 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).
- 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.
- the heat exchanger 1040 has 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.
- a part of the heat exchanger 1040 configured as a water-refrigerant heat exchanger is provided with an internal heat exchange between the high-temperature high-pressure refrigerant RF (H) and the low-temperature low-pressure refrigerant RF (C). 1040b can be provided.
- 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.
- the core parts 41 and 61 are provided with back
- This provides a two-stage heat exchange.
- 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.
- the second heat medium can be the heat medium WT (H) heat-exchanged with the high-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.
- the second heat medium can be the refrigerant RF (C) on the low pressure side of the refrigeration cycle.
- 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.
- 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.
- 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.
- the refrigeration cycle 20 illustrated in FIG. 25 is employed.
- the refrigeration cycle 20 employs a heat exchanger on the low pressure side, that is, a stacked heat exchanger that is a water-refrigerant heat exchanger only for the heat exchanger 60.
- the refrigeration cycle 20 includes an air-cooled heat exchanger 24.
- the heat exchanger 24 functions as a radiator.
- a water-refrigerant heat exchanger may be adopted only for the low-pressure side heat exchanger.
- 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.
- the heat exchanger 60 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.
- 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.
- 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 decompressor 22.
- the decompressor 22 cannot perform the decompression function.
- the high-temperature and high-pressure refrigerant is supplied to the heat exchanger 60.
- a bypass passage including the switching valve 27, the decompressor 28, and the heat exchanger 29 is provided.
- the switching valve 27 is switched so that the refrigerant flows through the bypass passage.
- the heat exchanger 29 functions as an evaporator.
- the heat exchanger 60 can be selectively functioned as a radiator or an evaporator.
- the water of the auxiliary system 50 can be cooled or heated by the refrigeration cycle 20.
- 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.
- 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.
- 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.
- the heat exchanger 2010 shown in FIGS. 30 and 31 constitutes the refrigeration cycle of the vehicle air conditioner.
- the heat exchanger 2010 heats the high-pressure side refrigerant and cooling water (heat medium) of the refrigeration cycle to condense the high-pressure side refrigerant, or the low-pressure side refrigerant and cooling water (heat medium) of the refrigeration cycle.
- This is an evaporator that exchanges heat to evaporate the low-pressure side refrigerant.
- cooling water for example, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid can be used.
- ethylene glycol antifreeze (LLC) is used as the cooling water.
- the heat exchanger 2010 is integrally formed by laminating and joining a large number of plate-like members 2011.
- the laminating direction of the plate-like member 2011 (vertical direction in the example of FIG. 30) is referred to as the plate laminating direction
- one end side in the plate laminating direction (the upper end side in the example of FIG. 30) is referred to as the one end side of the plate laminating direction.
- the other end side in the plate lamination direction (lower end side in the example of FIG. 30) is referred to as the other end side in the plate lamination direction.
- the plate-like member 2011 is an elongated, substantially rectangular plate material.
- a specific material for example, a double-sided clad material in which a brazing material is clad on both surfaces of an aluminum core material is used.
- a protruding portion 2111 is formed that protrudes in a substantially plate-stacking direction (in other words, a direction substantially orthogonal to the plate surface of the plate-like member 2011).
- a large number of the plate-like members 2011 are joined to each other by brazing, with the overhanging portions 2111 being stacked on each other.
- the large number of plate-like members 2011 are arranged so that the protruding tips of the overhanging portions 2111 face the same side (substantially downward in the example of FIG. 30).
- a large number of plate-like members 2011 form a heat exchange portion 2012, a first tank space 2013 for refrigerant, a second tank space 2014 for refrigerant, a first tank space 2015 for cooling water, and a second tank space 2016 for cooling water.
- the heat exchanging unit 2012 includes a plurality of refrigerant channels 2121 and a plurality of cooling water channels 2122.
- the plurality of refrigerant channels 2121 and the plurality of cooling water channels 2122 are formed between a large number of plate-like members 2011.
- the longitudinal directions of the refrigerant flow path 2121 and the cooling water flow path 2122 coincide with the longitudinal direction of the plate-like member 2011.
- the refrigerant flow path 2121 and the cooling water flow path 2122 are alternately stacked and arranged (parallel arrangement) one by one in the plate stacking direction.
- the plate-like member 2011 serves as a partition wall that partitions the coolant channel 2121 and the cooling water channel 2122. Heat exchange between the refrigerant flowing through the refrigerant flow path 2121 and the cooling water flowing through the cooling water flow path 2122 is performed via the plate-like member 2011.
- the first tank space 2013 for refrigerant and the first tank space 2015 for cooling water are arranged on one side (left side in the example of FIG. 30) of the refrigerant flow path 2121 and the cooling water flow path 2122 with respect to the heat exchange unit 2012.
- the second tank space 2014 for refrigerant and the second tank space 2016 for cooling water are arranged on the other side of the refrigerant flow path 2121 and the cooling water flow path 2122 (on the right side in the example of FIG. 30) with respect to the heat exchange unit 2012.
- the refrigerant first tank space 2013 and the refrigerant second tank space 2014 perform distribution and collection of the refrigerant to the plurality of refrigerant flow paths 2121.
- the first tank space for cooling water 2015 and the second tank space for cooling water 2016 distribute and collect the cooling water to the plurality of cooling water flow paths 2122.
- the first tank space 2013 for refrigerant, the second tank space for refrigerant 2014, the first tank space for cooling water 2015, and the second tank space for cooling water 2016 are the four corners of the plate-like member 2011 (in the example of FIG. It is comprised by the communicating hole formed in the four corners.
- the first tank space 2013 for refrigerant and the second tank space 2014 for refrigerant are provided at two corners on the diagonal line among the four corners of the substantially rectangular plate-like member 2011, and the remaining A cooling water first tank space 2015 and a cooling water second tank space 2016 are provided at two corners.
- the first joint 2021 and the first cooling water pipe 2022 are attached to the first endmost plate-like member 2011A that is located closest to one end side in the plate stacking direction among the many plate-like members 2011 constituting the heat exchange unit 2012. ing.
- the first joint 2021 is a member for joining refrigerant pipes, and forms the refrigerant inlet 2101 of the heat exchanger 2010.
- the first cooling water pipe 2022 forms a cooling water outlet 2102 of the heat exchanger 2010.
- the second joint 2023 and the second cooling water pipe 2024 are attached to the second endmost plate-like member 2011B located on the other end side in the plate stacking direction among the many plate-like members 2011 constituting the heat exchange unit 2012. It has been.
- the second joint 2023 is a member for joining refrigerant pipes and forms a refrigerant outlet 2103 of the heat exchanger 2010.
- the second cooling water pipe 2024 forms a cooling water inlet 2104 of the heat exchanger 2010.
- the refrigerant inlet 2101 and the refrigerant outlet 2103 communicate with the first tank space 2013 for refrigerant.
- the cooling water outlet 2102 and the cooling water inlet 2104 communicate with the first tank space 2015 for cooling water.
- a large number of plate-like members 2011 constituting the heat exchanging portion 2012 protrude toward one end side or the other end side in the plate stacking direction at the four corners of the plate-like member 2011. And a substantially cylindrical protrusion 2011f.
- a first tank space 2013 for refrigerant, a second tank space for refrigerant 2014, a first tank space for cooling water 2015, and a second tank space for cooling water 2016 are formed by the protrusions 2011f.
- the central plate-like member 2011C located at a substantially central portion in the plate stacking direction closes the protruding portion 2011f constituting the first tank space 2013 for refrigerant. It has a blocking part 2011g. Thereby, the first tank space 2013 for refrigerant 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 central plate member 2011C.
- the refrigerant flowing in from the refrigerant inlet 2101 moves from the refrigerant first tank space 2013 side to the refrigerant second tank space 2014 side in the refrigerant flow path 2121 on one end side in the plate stacking direction. Then, the refrigerant flows in the refrigerant flow path 2121 at the other end side in the plate stacking direction from the refrigerant second tank space 2014 side toward the refrigerant first tank space 2013 side and flows out from the refrigerant outlet 2103. That is, the heat exchanger 2010 is configured such that the flow of the soot refrigerant makes a U-turn once. At this time, the closing part 2011g of the central plate-like member 2011C of the present embodiment corresponds to a U-turn part.
- the protruding portion 2011f constituting the first tank space 2015 for cooling water is closed.
- the 1st tank space 2015 for cooling water is divided into two spaces in the board lamination direction.
- the cooling water flowing in from the cooling water inlet 2104 passes through the cooling water flow path 2122 on the other end side in the plate stacking direction from the cooling water first tank space 2015 side to the cooling water first.
- the cooling water flow path 2122 on one end side in the plate stacking direction flows from the second tank space for cooling water 2016 side toward the first tank space for cooling water 2015 side to exit the cooling water. 2102 flows out. That is, the heat exchanger 2010 is configured such that the flow of the cooling water makes a U-turn once.
- the heat exchanger 2010 is configured such that the refrigerant flow and the cooling water flow are in opposite directions (opposite flow).
- the offset fin 2030 is an inner fin that is interposed between the plate-like members 2011 and promotes heat exchange between the refrigerant and the heat medium.
- the offset fin 2030 is a plate-like member in which a cut and raised portion 2030a that is partially cut and raised is formed. A large number of cut-and-raised portions 2030a are formed in a direction F1 (that is, the longitudinal direction of the plate-like member 2011) parallel to the flow direction of the refrigerant and the cooling water.
- cut-and-raised portions 2030a adjacent to each other in the direction F1 parallel to the flow direction of the refrigerant and the cooling water are offset from each other.
- the large number of cut-and-raised portions 2030a are staggered in a direction F1 parallel to the refrigerant and cooling water flow directions.
- the offset fin 2030 for example, a double-sided clad material in which a brazing material is clad on both sides of an aluminum core is used.
- the offset fin 2030 is joined to both adjacent plate-like members 2011 by brazing.
- the offset fin 2030 constitutes an inner wall that joins adjacent plate-like members 2011 and crosses the coolant channel 2121 and the cooling water channel 2122 in the plate stacking direction. Further, the length of the refrigerant flow path 2121 and the cooling water flow path 2122 in the plate stacking direction (hereinafter referred to as flow path height) is the plate stacking direction of the offset fins 2030 disposed in the refrigerant flow path 2121 and the cooling water flow path 2122, respectively. Is equal to the length of
- offset fins 2030 are arranged in the coolant channel 2121 and the cooling water channel 2122, respectively.
- the offset fins 2030 arranged in the heat exchange unit 2012 are referred to as refrigerant-side offset fins 2301
- the offset fins 2030 arranged in the cooling water channel 2122 are cooling water. This is referred to as a side offset fin 2302.
- the length of the refrigerant side offset fin 2301 in the plate stacking direction is referred to as the fin height Frh of the refrigerant side offset fin 2301.
- the length of the cooling water side offset fin 2302 in the plate stacking direction is referred to as the fin height Fwh of the cooling water side offset fin 2302.
- the height Frh of the refrigerant side offset fin 2301 is lower than the height Fwh of the cooling water side offset fin 2302. For this reason, the flow path height of the refrigerant flow path 2121 is lower than the flow path height of the cooling water flow path 2122.
- the present inventor examined the heat transfer performance and the change in pressure loss when the height Frh of the refrigerant-side offset fin 2301 was changed.
- the alternate long and short dash line indicates the pressure loss of the refrigerant
- the alternate long and two short dashes line indicates the pressure loss of the cooling water
- the solid line indicates the heat transfer performance between the cooling water and the refrigerant.
- the ratio of the fin height occupied by the refrigerant-side offset fin 2301 is in the range of 0.1 or more and 0.5 or less, thereby improving the heat transfer performance between the refrigerant and the cooling water. It can be about 80% or more of the maximum value.
- the ratio of the fin height occupied by the refrigerant side offset fin 2301 is set to be larger than 0.14 and smaller than 0.49, that is, to satisfy the relationship of 0.14 ⁇ Frh / (Frh + Fwh) ⁇ 0.49.
- the heat transfer performance between the refrigerant and the cooling water can be improved while reducing the pressure loss of the refrigerant and the cooling water.
- the fin heights of the refrigerant side offset fin 2301 and the cooling water side offset fin 2302 are set to 0.14 ⁇ Frh / (Frh + Fwh) ⁇ 0.49. It is effective to satisfy the relationship.
- coolant side offset fin 2301 is set to 1/80 or less of the refrigerant flow path length L, ie, L / 80 or less.
- the present inventor examined the change in refrigerant pressure loss when the shape of the refrigerant flow path 2121 was changed.
- the length of the refrigerant flow path 2121 in the refrigerant flow direction (hereinafter referred to as the refrigerant flow path length) L is orthogonal to both the refrigerant flow direction and the plate stacking direction in the refrigerant flow path 2121.
- a ratio (L / W) to a length W in a direction (hereinafter referred to as a width direction of the refrigerant flow path 2121) is defined as an aspect ratio.
- FIG. 36 shows the relationship between the aspect ratio of the refrigerant flow path 2121 or the cooling water flow path 2122 and the pressure loss when the segment length S of the refrigerant side offset fin 2301 is set to L / 80 or less. At this time, the fin height of the refrigerant side offset fin 2301 is set to 1.5 mm.
- the solid line indicates the relationship between the aspect ratio of the refrigerant flow path 2121 and the pressure loss
- the broken line indicates the relationship between the aspect ratio of the cooling water flow path 2122 and the pressure loss.
- the cooling water Since the cooling water is highly viscous, it diffuses in the cooling water flow path 2122 with the viscosity of the cooling water itself. For this reason, the pressure loss of the cooling water in the cooling water channel 2122 depends on the channel length. Therefore, as shown by the broken line in FIG. 36, the pressure loss of the cooling water increases as the aspect ratio of the cooling water channel 2122 increases.
- the segment length S of the refrigerant-side offset fin 2301 is set to L / 80 or less, and the aspect ratio of the refrigerant flow path 2121 is set to 1.3 or more. Can be suppressed, and the pressure loss of the refrigerant can be reduced.
- the pressure loss increases as the flow path length increases in the region where the aspect ratio of the refrigerant flow path 2121 is 1.3 or more.
- the pressure loss of the refrigerant is preferably within 1.5 times the minimum pressure loss.
- the COP is 5% worse than the maximum COP.
- the aspect ratio of the refrigerant flow path 2121 increases, the size of the heat exchanger 2010 increases. Therefore, it is desirable that the aspect ratio of the refrigerant flow path 2121 be 4 or less in order to suppress the decrease in COP and to make the physique of the heat exchanger 2010 compact.
- the heat exchange part 2012 of this embodiment is arrange
- the heat exchange unit 2012 is arranged so that the width direction of the refrigerant channel 2121 is parallel to the direction of gravity.
- the refrigerant condenses and evaporates by exchanging heat with the cooling water.
- the thinner the liquid film on the heat transfer surface the higher the heat transfer coefficient.
- the refrigerant flows from the refrigerant inflow section 2121 a that causes the refrigerant to flow into the refrigerant flow path 2121 toward the refrigerant outflow section 2121 b that causes the refrigerant to flow out from the refrigerant flow path 2121. .
- the gas-phase refrigerant is likely to flow through a portion where the liquid-phase refrigerant is not retained, so that a drift occurs. Then, once a drift occurs, it is difficult to improve, so the drift remains in all the refrigerant flow paths 2121 and the heat transfer coefficient decreases.
- the liquid-phase refrigerant adheres to the refrigerant-side offset fin 2301 and stays on the lower side in the gravity direction due to the gas-liquid density difference. And gather at the refrigerant outflow portion 2121b. Then, in the refrigerant flow path 2121 after the U-turn, the gas-liquid two-phase refrigerant is diffused again from the refrigerant inflow portion 2121a.
- the liquid-phase refrigerant adheres and stays on the refrigerant-side offset fin 2301, but moves downward in the gravitational direction due to the gas-liquid density difference, and the refrigerant outflow portion 2121b. Gather in
- the flow of the refrigerant flowing through the refrigerant flow path 2121 causes the U-turn to collect the refrigerant once diffused in the refrigerant flow path 2121 before the U-turn, and then the refrigerant flow path 2121 after the U-turn The refrigerant can be further diffused. Furthermore, by disposing the heat exchange unit 2012 so that the plate stacking direction intersects the direction of gravity, the liquid phase refrigerant can be separated by the gas-liquid density difference. As described above, the flow passage area (effective heat transfer surface) through which the gas-phase refrigerant flows in the refrigerant flow passage 2121 can be secured, and the heat transfer performance can be improved. For this reason, it becomes possible to improve heat exchange performance.
- the auxiliary systems 30, 50 and 70 may circulate a heat medium such as oil instead of the cooling water mainly composed of water.
- 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.
- connection members are provided by a tubular connector.
- all connecting members may be provided by block joints.
- the heat medium is not limited to this.
- a refrigerant may be employed as the heat medium, and the heat exchange unit 2012 may exchange heat between the refrigerants.
- the heat exchange unit 2012 is arranged so that the width direction of the refrigerant flow path 2121 is parallel to the gravity direction, but the arrangement direction of the heat exchange unit 2012 is not limited to this.
- the refrigerant flow path 2121 collects the liquid-phase refrigerant on the lower side in the gravitational direction due to the gas-liquid density difference, and the effective heat transfer surface. Can be secured.
- the refrigerant flow paths 2121 and the cooling water flow paths 2122 are alternately stacked one by one in the plate stacking direction.
- a plurality of refrigerant flow paths 2121 and cooling water flow paths 2122 are provided in the plate stacking direction. They may be alternately stacked one by one.
- the heat exchanger 2010 is configured such that the refrigerant flow and the cooling water flow make a U-turn once, but the refrigerant flow and the cooling water flow make a U-turn a plurality of times. May be configured.
- the heat exchanger 2010 may be configured so that the refrigerant flow and the cooling water flow do not make a U-turn.
- the heat exchange unit 2012 may be arranged in an arbitrary direction.
- the heat exchanger 2010 is configured such that the refrigerant flow and the cooling water flow are in opposite directions (opposite flow), but the refrigerant flow and the cooling water flow are different from each other. You may be comprised so that it may become the mutually same direction (parallel flow).
Abstract
Description
図1に図示されるように、第1実施形態は、熱システム10を開示する。熱システム10は、車両に搭載されている。熱システム10は、車両用の空調装置、または車両に搭載された機器の温度調節装置を提供する。空調装置として利用される場合、熱システム10は、暖房、および/または冷房を提供する。温度調節装置として利用される場合、熱システム10は、加熱用の熱源、および/または冷却用の低温源を提供する。熱システム10は、冷凍サイクル20を有する。冷凍サイクル20は、冷媒の蒸気を圧縮することにより低温と高温とを提供する蒸気圧縮式の冷凍サイクル20である。冷媒は、第1の熱媒体とも呼ばれる。さらに、熱システム10は、冷凍サイクル20の冷媒と熱交換する熱媒体が流れる補助系統30を有する。補助系統30は、熱媒体として水を主成分とする冷却水を循環させる。冷却水は、第2の熱媒体とも呼ばれる。補助系統30は、冷凍サイクル20の放熱器と熱的に結合された高温系統、または第1補助系統とも呼ぶことができる。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、コア部41内の全体において対向流を形成した。これに代えて、この実施形態では、コア部41内の一部において対向流が形成される。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、区画プレート41c、241cを用いた。この実施形態では、区画プレートを用いない。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。図12に図示されるように、熱交換器40は、一方の端面に、接続部材43を有する。さらに、熱交換器40は、他方の端面に、接続部材245、246と、接続部材344とを有する。この実施形態では、区画プレートが用いられない。このため、コア部41内に形成された複数の通路41rfのすべては、接続部材43、344の間において並列に接続される。接続部材43、344が両面に分散配置されるから、コア部41内には、S字形の冷媒のための流路が形成される。この実施形態でも、コア部41の全体において対向流が提供される。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。図13に図示されるように、熱交換器40は、一方の端面に、接続部材245、246と、接続部材344とを有する。さらに、熱交換器40は、同じ端面に、冷媒の入口のための接続部材543を有する。この実施形態では、区画プレートが用いられない。このため、コア部41内に形成された複数の通路41rfのすべては、接続部材543、344の間において並列に接続される。接続部材543、344が一方の端面に集中配置されるから、コア部41内には、積層方向に沿うU字形の冷媒のための流路が形成される。この実施形態でも、コア部41の全体において対向流が提供される。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、コア部41の外周部において、水通路に対応する位置においてコアプレート41a、41bが3重に重ねられた。この実施形態では、冷媒通路に対応する位置においてコアプレート41a、41bが3重に重ねられる。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、熱交換器40は、補助系統30だけによって冷却される。これに代えて、この実施形態では、複数の補助系統30、50によって冷却される熱交換器740が採用される。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、第2の補助系統50の水WT(C)を後段40bに供給した。これに代えて、この実施形態では、熱交換器60にも前段60aと後段60bとを設ける。さらに、この実施形態では、後段40bと後段60bとの間において熱交換を提供する第3の補助系統70を採用する。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、補助系統70の水、すなわち冷媒とは異なる熱媒体を介して冷凍サイクル20の内部熱交換を提供した。これに代えて、この実施形態では、冷凍サイクル20の冷媒を用いて直接的な内部熱交換が提供される。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、熱交換器960に内部熱交換器を一体的に構成した。これに代えて、この実施形態では、熱交換器1040に内部熱交換器を一体的に構成する。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、熱交換器40と熱交換器60とを互いに離れた位置に別々の部品として配置した。これに代えて、この実施形態では、単一の部品として設けられた熱交換器80のコア部は、冷凍サイクル20の高圧側の冷媒が供給される高圧側の熱交換部分1140と、冷凍サイクル20の低圧側の冷媒が供給される低圧側の熱交換部分1160とを有する。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。この実施形態では、図25に図示される冷凍サイクル20が採用される。冷凍サイクル20は、低圧側の熱交換器、すなわち熱交換器60だけに水-冷媒熱交換器である積層型熱交換器を採用する。冷凍サイクル20は、空冷式の熱交換器24を備える。熱交換器24は放熱器として機能する。このように、低圧側の熱交換器だけに、水-冷媒熱交換器を採用してもよい。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。この実施形態では、図26に図示される冷凍サイクル20が採用される。冷凍サイクル20は、可逆式の冷凍サイクルである。冷凍サイクル20は、冷媒の循環方向を切換える切換弁25を備える。よって、冷凍サイクル20は、冷却のための冷却運転と、加熱のための加熱運転(ヒートポンプ運転)とを選択的に実行可能である。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。この実施形態では、図27に図示される冷凍サイクル20が採用される。冷凍サイクル20は、熱交換器60を冷凍サイクル20における高圧側または低圧側に選択的に位置付けるバイパス式の冷凍サイクルである。冷凍サイクル20は、冷却のための冷却運転と、加熱のための加熱運転(ヒートポンプ運転)とを選択的に実行可能である。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、冷凍サイクル20の高圧部分に熱交換器40だけを配置した。これに加えて、高圧部分に他の熱交換器を追加的に設けてもよい。図28は、追加的な熱交換器24a、24b、24cを例示する。これらの少なくともひとつを採用することができる。熱交換器24aは、冷媒の流れにおいて、熱交換器40と並列に配置されている。熱交換器24bは、冷媒の流れにおいて、熱交換器40より上流側に直列に配置されている。熱交換器24cは、冷媒の流れにおいて、熱交換器40より下流側に直列に配置されている。
この実施形態は、先行する実施形態を基礎的形態とする変形例である。上記実施形態では、冷凍サイクル20の低圧部分に熱交換器60だけを配置した。これに加えて、冷圧部分に他の熱交換器を追加的に設けてもよい。図29は、追加的な熱交換器23a、23b、23cを例示する。これらの少なくともひとつを採用することができる。熱交換器23aは、冷媒の流れにおいて、熱交換器60と並列に配置されている。熱交換器23bは、冷媒の流れにおいて、熱交換器60より上流側に直列に配置されている。熱交換器23cは、冷媒の流れにおいて、熱交換器60より下流側に直列に配置されている。
第17実施形態について図30~36に基づいて説明する。図30、図31に示す熱交換器2010は、車両用空調装置の冷凍サイクルを構成している。熱交換器2010は、冷凍サイクルの高圧側冷媒と冷却水(熱媒体)とを熱交換して高圧側冷媒を凝縮させる凝縮器、または冷凍サイクルの低圧側冷媒と冷却水(熱媒体)とを熱交換して低圧側冷媒を蒸発させる蒸発器である。
本開示は上述の実施形態に限定されることなく、本開示の趣旨を逸脱しない範囲内で、以下のように種々変形可能である。
Claims (22)
- 冷凍サイクルに流される冷媒のための扁平な冷媒通路(41rf)、およびこの冷媒と熱交換する熱媒体のための扁平な熱媒体通路(41wt)を形成するように積層して配置された複数のプレート(41a、41b、641b、41c、241c、741c、41d、41e、61e)を含むコア部(41、61)を有する積層型熱交換器において、
前記冷媒通路(41rf)に冷媒を流すための入口および出口を提供する第一接続部材(43、543、44、344、63、64)と、
前記熱媒体通路(41wt)に熱媒体を流すための入口および出口を提供する第二接続部材であって、前記冷媒通路(41rf)に流される冷媒に対して前記熱媒体通路(41wt)に流される熱媒体が対向流となるように前記入口および前記出口が設定された第二接続部材(45、46、245、246、745、746、47、48、65、66、67、68、967、968)とを備え、
前記コア部は、
少なくとも前記冷媒通路(41rf)に設けられたオフセット型のフィン(41f)を備える積層型熱交換器。 - 前記コア部は、
前記冷媒通路および前記熱媒体通路を形成する複数のコアプレート(41a、41b、641b、41c、241c、741c)と、
前記コアプレートの積層体の両端に設けられ、前記コアプレートより厚いエンドプレート(41d、41e、61e)とを備える請求項1に記載の積層型熱交換器。 - 前記コアプレートは、
前記コア部における前記冷媒通路および/または前記熱媒体通路を複数の群に分割するとともに、それらの群を直列に連通する区画プレート(41c、241c、741c)を含む請求項2に記載の積層型熱交換器。 - 前記区画プレートは、前記第一接続部材と前記第二接続部材の少なくともひとつから延びる貫通通路(41ri、41ro、41wi、41wo)を閉塞する閉塞部を有する請求項3に記載の積層型熱交換器。
- 前記区画プレート以外の前記コアプレート(41a、41b)は、前記第一接続部材と前記第二接続部材の少なくともひとつから延びる貫通通路(41ri、41ro、41wi、41wo)を提供する開口部を有する請求項4に記載の積層型熱交換器。
- 前記コア部は、前記コアプレートの積層方向に対して直交する横方向に沿ってUターン状の流路を形成する請求項3から請求項5のいずれかに記載の積層型熱交換器。
- 前記コアプレートは、前記コア部の外周に位置付けられて互いに重ねられる外縁筒状部分(41a2、41b2)を有する請求項2から請求項6のいずれかに記載の積層型熱交換器。
- 前記外縁筒状部分(41a2、41b2)は前記コア部の外周において少なくとも2重に重ねられている請求項7に記載の積層型熱交換器。
- 前記外縁筒状部分(41a2、41b2)は前記コア部の外周において部分的に3重に重ねられている請求項8に記載の積層型熱交換器。
- 前記コア部は、前記熱媒体を第1熱媒体として利用することにより前記冷媒と前記第1熱媒体との間の熱交換を提供する前段(40a、60a)と、
前記前段において熱交換した前記冷媒と前記第1熱媒体とは異なる温度をもつ第2熱媒体との間の熱交換を提供する後段(40b、60b)とを備える請求項1から請求項9のいずれかに記載の積層型熱交換器。 - 前記前段および前記後段に供給される前記冷媒は、前記冷凍サイクルの高圧側の冷媒であり、
前記第2熱媒体は前記冷凍サイクルの低圧側の冷媒と熱交換された熱媒体(WT(C))である請求項10に記載の積層型熱交換器。 - 前記前段および前記後段に供給される前記冷媒は、前記冷凍サイクルの低圧側の冷媒であり、
前記第2熱媒体は前記冷凍サイクルの高圧側の冷媒と熱交換された熱媒体(WT(H))である請求項10に記載の積層型熱交換器。 - 前記前段および前記後段に供給される前記冷媒は、前記冷凍サイクルの低圧側の冷媒であり、
前記第2熱媒体は前記冷凍サイクルの高圧側の冷媒(RF(H))である請求項10に記載の積層型熱交換器。 - 前記前段および前記後段に供給される前記冷媒は、前記冷凍サイクルの高圧側の冷媒であり、
前記第2熱媒体は前記冷凍サイクルの低圧側の冷媒(RF(C))である請求項10に記載の積層型熱交換器。 - 前記第一接続部材と前記第二接続部材の少なくともひとつは、
前記冷媒または前記熱媒体を流すための通路(41ri)の周囲に設けられ前記コア部に接合された第1接合部(43a、44a)と、
前記コア部の積層方向の端面において、前記第1接合部より中央寄りの位置に設けられ前記コア部に接合された第2接合部(43b、44b)とを備える請求項1から請求項14のいずれかに記載の積層型熱交換器。 - 前記冷媒通路には、前記冷凍サイクルの高圧側の冷媒、および前記冷凍サイクルの低圧側の冷媒が選択的に供給される請求項1から請求項15のいずれかに記載の積層型熱交換器。
- 前記コア部は、
前記冷凍サイクルの高圧側の冷媒が供給される高圧側熱交換部分(1140)と、
前記冷凍サイクルの低圧側の冷媒が供給される低圧側熱交換部分(1160)とを有する請求項1から請求項16のいずれかに記載の積層型熱交換器。 - 前記高圧側熱交換部分(1140)の端部に配置されたプレート(41e)と、
前記低圧側熱交換部分(1160)の端部に配置されたプレート(61e)とが背中合わせに配置され接合されている請求項17に記載の積層型熱交換器。 - 冷凍サイクルの冷媒と熱媒体とを熱交換させる熱交換部(2012)を備え、
前記熱交換部(2012)は、複数の板状部材(2011)が互いに積層されて接合されることによって形成されており、
前記複数の板状部材(2011)同士の間には、前記冷媒が流れる複数の冷媒流路(2121)、および前記熱媒体が流れる複数の熱媒体流路(2122)が形成され、
前記複数の冷媒流路(2121)および前記複数の熱媒体流路(2122)は、前記複数の板状部材(2011)の積層方向に並んで配置されており、
前記複数の冷媒流路(2121)および前記複数の熱媒体流路(2122)には、それぞれ、隣り合う前記板状部材(2011)同士を接合し、かつ前記冷媒と前記熱媒体との間での熱交換を促進させるインナーフィン(2301、2302)が設けられており、
前記冷媒流路(2121)に設けられた前記インナーフィンは、部分的に切り起こされた切り起こし部(2030a)が前記冷媒の流れ方向に多数形成されるとともに、前記冷媒の流れ方向に隣り合う前記切り起こし部(2030a)同士が互いにオフセットされている冷媒側オフセットフィン(2301)であり、
前記熱媒体流路(2122)に設けられた前記インナーフィンは、部分的に切り起こされた切り起こし部(2030a)が前記熱媒体の流れ方向に多数形成されるとともに、前記熱媒体の流れ方向に隣り合う前記切り起こし部(2030a)同士が互いにオフセットされている熱媒体側オフセットフィン(2302)であり、
前記冷媒流路(2121)における前記板状部材(2011)の積層方向の長さである冷媒流路高さは、前記冷媒側オフセットフィン(2301)における前記板状部材(2011)の積層方向の長さである冷媒側フィン高さFrhと等しくなっており、
前記熱媒体流路(2122)における前記板状部材(2011)の積層方向の長さである熱媒体流路高さは、前記熱媒体側オフセットフィン(2302)における前記板状部材(2011)の積層方向の長さである熱媒体側フィン高さFwhと等しくなっており、
前記冷媒側フィン高さFrwおよび前記熱媒体側フィン高さFwhが、0.14<Frh/(Frh+Fwh)<0.49の関係を満たすように設定されている積層型熱交換器。 - 前記冷媒流路(2121)における前記冷媒の流れ方向の長さLと、前記冷媒流路(2121)における前記冷媒の流れ方向および前記板状部材(2011)の積層方向の双方に直交する方向の長さWとの比であるアスペクト比(L/W)が、1.3以上に設定されており、
前記冷媒側オフセットフィン(2301)の前記切り起こし部(2030a)における前記冷媒の流れ方向の長さSが、L/80以下に設定されている請求項19に記載の積層型熱交換器。 - 前記熱交換部(2012)は、前記板状部材(2011)の積層方向が重力方向と交差するように配置されており、
前記熱交換部(2012)は、前記冷媒流路(2121)を流通する前記冷媒の流れをUターンさせるUターン部(2011g)を有している請求項19または20に記載の積層型熱交換器。 - 冷凍サイクルの冷媒と熱媒体とを熱交換させる熱交換部(2012)を備え、
前記熱交換部(2012)は、複数の板状部材(2011)が互いに積層されて接合されることによって形成されており、
前記複数の板状部材(2011)同士の間には、前記冷媒が流れる複数の冷媒流路(2121)、および前記熱媒体が流れる複数の熱媒体流路(2122)が形成され、
前記複数の冷媒流路(2121)および前記複数の熱媒体流路(2122)は、前記複数の板状部材(2011)の積層方向に並んで配置されており、
前記複数の冷媒流路(2121)および前記複数の熱媒体流路(2122)には、それぞれ、隣り合う前記板状部材(2011)同士を接合し、かつ前記冷媒と前記熱媒体との間での熱交換を促進させるインナーフィン(2301、2302)が設けられており、
前記冷媒流路(2121)に設けられた前記インナーフィンは、部分的に切り起こされた切り起こし部(2030a)が前記冷媒の流れ方向に多数形成されるとともに、前記冷媒の流れ方向に隣り合う前記切り起こし部(2030a)同士が互いにオフセットされている冷媒側オフセットフィン(2301)であり、
前記熱媒体流路(2122)に設けられた前記インナーフィンは、部分的に切り起こされた切り起こし部(2030a)が前記熱媒体の流れ方向に多数形成されるとともに、前記熱媒体の流れ方向に隣り合う前記切り起こし部(2030a)同士が互いにオフセットされている熱媒体側オフセットフィン(2302)であり、
前記熱交換部(2012)は、前記板状部材(2011)の積層方向が重力方向と交差するように配置されており、
前記熱交換部(2012)は、前記冷媒流路(2121)を流通する前記冷媒の流れをUターンさせるUターン部(2011g)を有している積層型熱交換器。
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FR3045809A1 (fr) * | 2015-12-21 | 2017-06-23 | Valeo Systemes Thermiques | Echangeur thermique, notamment pour vehicule automobile |
WO2017109355A1 (fr) * | 2015-12-21 | 2017-06-29 | Valeo Systemes Thermiques | Échangeur thermique, notamment pour vehicule automobile |
CN108443962A (zh) * | 2018-02-09 | 2018-08-24 | 青岛海尔空调器有限总公司 | 用于环形空调室内机的换热器及环形空调室内机 |
CN108443962B (zh) * | 2018-02-09 | 2024-02-23 | 青岛海尔空调器有限总公司 | 用于环形空调室内机的换热器及环形空调室内机 |
WO2021002474A1 (ja) * | 2019-07-02 | 2021-01-07 | 株式会社ティラド | 熱交換器 |
CN113950605A (zh) * | 2019-07-02 | 2022-01-18 | 株式会社T.Rad | 热交换器 |
Also Published As
Publication number | Publication date |
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CN105074375B (zh) | 2018-05-15 |
DE112014001028T5 (de) | 2016-01-07 |
US20160010929A1 (en) | 2016-01-14 |
US10962307B2 (en) | 2021-03-30 |
CN105074375A (zh) | 2015-11-18 |
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