JP2017020680A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To downsize a heat exchanger.SOLUTION: A heat exchanger 50 comprises: a condensing part 52 condensing a cooling medium; an evaporation part 51 evaporating the cooling medium; and an expansion part 53 decompressing and expanding the cooling medium passing through the condensing part 52 and feeding the resultant cooling medium into the evaporation part 51, the heat exchanger 50 being an integral heat exchanger 50 in which the condensing part 52, the expansion part 53, and the evaporation part 51 are stacked, and the expansion part 53 being provided between the condensing part 52 and the evaporation part 51.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a heat exchanger.

  Conventionally, a heat exchanger in which an upper heat exchange part and a lower heat exchange part are arranged in the vertical direction, the upper heat exchange part functions as an evaporator during cooling operation, and the lower heat exchange part functions as a condenser is disclosed in Patent Literature 1 is disclosed.

JP 2012-117751 A

  However, in the above heat exchanger, an expansion device is provided outside the upper heat exchange unit and the lower heat exchange unit, and a space for disposing the expansion device must be secured. The heat exchanger becomes large.

  This invention is invented in view of such a point, and it aims at miniaturizing a heat exchanger.

  A heat exchanger according to an aspect of the present invention includes a condensing unit that condenses a cooling medium, an evaporating unit that evaporates the cooling medium, an expansion unit that decompresses and expands the cooling medium that has passed through the condensing unit, and flows into the evaporating unit. The heat exchanger is an integrated heat exchanger in which a condensing unit, an expansion unit, and an evaporation unit are stacked, and the expansion unit is provided between the condensing unit and the evaporation unit. .

  According to this aspect, the expansion unit is provided between the condensing unit and the evaporation unit, and the condensing unit, the expansion unit, and the expansion unit are stacked without stacking the condensing unit, the expansion unit, and the evaporation unit. Can be integrated, and the heat exchanger can be downsized.

It is a schematic block diagram of a vehicle air conditioner. It is a perspective view of an integrated heat exchanger. FIG. 3 is a sectional view taken along line III-III in FIG. 2. It is IV-IV sectional drawing of FIG. FIG. 5 is a VV cross-sectional view of FIG. 2. It is the figure which looked at the expansion part from the chiller side. It is a perspective view of an aperture plate.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  The configuration of the embodiment of the present invention will be described with reference to FIG. FIG. 1 is an overall configuration diagram of a vehicle air conditioner 100 according to the present embodiment.

  The vehicle air conditioner 100 is an air conditioner mounted on a vehicle 1 having an engine stop function for stopping the engine 9 when the vehicle stops or travels, such as a hybrid vehicle (HEV). The vehicle 1 includes an engine 9 that is used for driving wheels and generating electric power, and a radiator 8 that cools the engine 9 with circulating cooling water.

  The vehicle air conditioner 100 includes a heat pump unit 4 as a refrigeration cycle that cools and dehumidifies air flowing through the air passage 2, and a heater unit 6 that warms the air flowing through the air passage 2.

  The air sucked from the air inlet flows through the air passage 2. The air path 2 can suck outside air outside the passenger compartment and inside air inside the passenger compartment. The air that has passed through the air passage 2 is guided into the passenger compartment.

  The heat pump unit 4 includes a refrigerant circulation circuit 41 that circulates refrigerant, an electric compressor 42 that is driven by an electric motor (not shown) and compresses the refrigerant, and refrigerant that is compressed by the electric compressor 42 during cooling. An outdoor heat exchanger 43 that dissipates heat and condenses, an expansion valve 44 that decompresses and expands the condensed refrigerant, and an evaporator 45 that cools the air flowing through the air passage 2 using the refrigerant that has expanded and the temperature has decreased. .

  The electric compressor 42 is, for example, a vane-type rotary electric compressor, but a scroll-type electric compressor may be used. The rotational speed of the electric compressor 42 is controlled by a command signal from a controller (not shown).

  An accumulator 46 is provided upstream of the electric compressor 42. The accumulator 46 temporarily accumulates the surplus of the refrigerant sent from the evaporator 45 and sends only the gaseous refrigerant to the electric compressor 42.

  The outdoor heat exchanger 43 during cooling cools and liquefies the refrigerant by exchanging heat with the outside air. The outdoor heat exchanger 43 includes a main outdoor heat exchanger 43a that liquefies gaseous refrigerant, a liquid tank 43b that stores liquid refrigerant, and a supercooling outdoor heat exchanger 43c that further cools the liquid refrigerant.

  The expansion valve 44 expands the liquid refrigerant cooled by the outdoor heat exchanger 43. The expansion valve 44 has a temperature sensing cylinder (not shown) attached to the outlet side of the evaporator 45, and the opening degree is automatically adjusted so that the degree of superheat of the refrigerant on the outlet side of the evaporator 45 is maintained at a predetermined value. Adjusted.

  The evaporator 45 performs heat exchange between the liquid refrigerant decompressed by the expansion valve 44 and the air flowing through the air passage 2. The evaporator 45 is provided in the air passage 2 and cools and dehumidifies the air flowing through the air passage 2. In the evaporator 45, the liquid refrigerant evaporates by the heat of the air flowing through the air passage 2, and becomes a gaseous refrigerant. The gaseous refrigerant evaporated by the evaporator 45 is supplied again to the electric compressor 42 via the accumulator 46.

  Further, the heat pump unit 4 has an integrated heat exchanger 50. The integrated heat exchanger 50 will be described in detail with reference to FIGS.

  FIG. 2 is a perspective view of the integrated heat exchanger 50. 3 is a cross-sectional view taken along the line III-III in FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. 5 is a cross-sectional view taken along the line V-V in FIG. FIG. 6 is a view of the inflating portion 53 viewed from the chiller 51 side with the chiller side plate 53a removed. FIG. 7 is a perspective view of the diaphragm plate 59.

  The integrated heat exchanger 50 is a box-shaped heat exchanger. The integrated heat exchanger 50 includes a chiller 51 that absorbs heat from cooling water in an engine cooling circuit 60 to be described later, and a refrigerant that absorbs heat in the chiller 51 and is compressed by the electric compressor 42 in a heater circuit 70 to be described later. A capacitor 52 that radiates heat to the cooling water and an expansion portion 53 that decompresses and expands the refrigerant that has passed through the capacitor 52 are stacked.

  The integrated heat exchanger 50 includes a refrigerant inflow pipe 52 a for flowing the refrigerant discharged from the electric compressor 42 into the condenser 52, a refrigerant discharge pipe 51 a for discharging the refrigerant from the chiller 51, and a first flow through which cooling water flows into the condenser 52. 1st cooling water inflow pipe 52b, 1st cooling water discharge pipe 52c which discharges cooling water from condenser 52, 2nd cooling water inflow pipe 51b which flows cooling water into chiller 51, and 2nd which discharges cooling water from chiller 51 And a cooling water discharge pipe 51c.

  As shown in FIG. 3, the capacitor 52 is formed by laminating a plurality of plates 54a via spacers 55a. An end plate 56 to which the refrigerant inflow pipe 52a, the first cooling water inflow pipe 52b, and the first cooling water discharge pipe 52c are attached is disposed at the upper end of the condenser 52.

  In the capacitor 52, the plate 54a and the spacer 55a are stacked, and the end plate 56 is disposed at the upper end, so that the first coolant channel 52d through which the coolant flows and the first coolant channel 52e through which the coolant flows are stacked in the stacking direction. Are formed alternately. Further, as shown in FIG. 4, the capacitor 52 includes a first refrigerant inflow hole 52f through which refrigerant flows from the refrigerant inflow pipe 52a into the first refrigerant flow path 52d, and an expansion section 53 to be described later from the first refrigerant flow path 52d. A first refrigerant discharge hole 52g for discharging the refrigerant is formed in the first cooling water inflow hole 52h through which cooling water flows from the first cooling water inflow pipe 52b to the first cooling water flow path 52e, as shown in FIG. A first cooling water discharge hole 52i for discharging cooling water from the first cooling water flow path 52e to the first cooling water discharge pipe 52c is formed.

  The first refrigerant inflow hole 52f and the first refrigerant discharge hole 52g do not communicate with the first cooling water flow path 52e. Further, the first cooling water inflow hole 52h and the first cooling water discharge hole 52i do not communicate with the first refrigerant flow path 52d. As a method for preventing such communication, there are a method in which a spacer is sandwiched between plates, a method in which unevenness is applied to a plate by press molding, and the like.

  The condenser 52 exchanges heat between the refrigerant flowing through the first refrigerant flow path 52d and the cooling water flowing through the first cooling water flow path 52e, and heats the cooling water with the refrigerant.

  As shown in FIG. 3, the chiller 51 is configured by laminating a plurality of plates 54b via spacers 55b. An end plate 57 to which the refrigerant discharge pipe 51a, the second cooling water inflow pipe 51b, and the second cooling water discharge pipe 51c are attached is disposed at the lower end of the chiller 51.

  In the chiller 51, the plate 54b and the spacer 55b are stacked, and the end plate 57 is disposed at the lower end, whereby the second coolant channel 51d through which the coolant flows and the second coolant channel 51e through which the coolant flows are stacked in the stacking direction. Are formed alternately. In addition, as shown in FIG. 4, the chiller 51 has a second refrigerant inflow hole 51f through which the refrigerant decompressed and expanded by the expansion portion 53 flows into the second refrigerant flow path 51d, and a refrigerant discharge from the second refrigerant flow path 51d. A second coolant discharge hole 51g for discharging the coolant is formed in the pipe 51a, and as shown in FIG. 3, a second coolant inlet hole for allowing the coolant to flow into the second coolant channel 51e from the second coolant inlet pipe 51b. 51h and the 2nd cooling water discharge hole 51i which discharges a cooling water from the 2nd cooling water flow path 51e to the 2nd cooling water discharge pipe 51c are formed.

  The second refrigerant inflow hole 51f and the second refrigerant discharge hole 51g do not communicate with the second cooling water flow path 51e. Further, the second cooling water inflow hole 51h and the second cooling water discharge hole 51i do not communicate with the second refrigerant flow path 51d. As a method for preventing such communication, there are a method in which a spacer is sandwiched between plates, a method in which unevenness is applied to a plate by press molding, and the like.

  The chiller 51 performs heat exchange between the refrigerant flowing through the second refrigerant channel 51d and the cooling water flowing through the second cooling water channel 51e, absorbs heat with the refrigerant, and evaporates the refrigerant.

  The inflating part 53 is sandwiched between a capacitor 52 and a chiller 51 as shown in FIG. The inflating portion 53 is formed by disposing a spacer 58 on the chiller side plate 53a, disposing a diaphragm plate 59 inside the spacer 58, and overlapping a capacitor side plate 53b thereon.

  As shown in FIGS. 6 and 7, the diaphragm plate 59 is formed with a linear diaphragm groove 59a on the surface on the chiller 51 side, and a plurality of holes 59b are formed around the diaphragm groove 59a.

  In the expansion part 53, the throttle part 53c is formed by the throttle groove 59a and the chiller side plate 53a. The throttle part 53c is an orifice structure formed so that the width is shorter than the length, and the refrigerant flowing through the throttle part 53c is subjected to pressure loss by making the throttle part 53c longer.

  In the expansion portion 53, a refrigerant inflow portion 53d and a refrigerant discharge portion 53e are formed by the capacitor side plate 53b, the spacer 58, the chiller side plate 53a, and the throttle plate 59 on both ends in the extending direction of the throttle groove 59a.

  The refrigerant inflow portion 53d communicates with the first refrigerant discharge hole 52g of the capacitor 52, and the refrigerant flows in from the first refrigerant discharge hole 52g. The refrigerant inflow portion 53d communicates with the throttle portion 53c and allows the refrigerant to flow into the throttle portion 53c.

  The refrigerant discharge part 53e communicates with the throttle part 53c, and the refrigerant flows from the throttle part 53c. The refrigerant that has passed through the throttle portion 53c expands under reduced pressure in the refrigerant discharge portion 53e. The refrigerant discharge part 53e communicates with the second refrigerant inflow hole 51f of the chiller 51, and causes the refrigerant to flow into the second refrigerant inflow hole 51f.

  In the expansion part 53, the diaphragm plate 59, the capacitor side plate 53b, and the spacer 58 are in close contact, and the diaphragm plate 59, the chiller side plate 53a, and the spacer 58 are in close contact, and the refrigerant inflow part 53d and the refrigerant discharge part 53e Communicates only through the aperture 53c.

  The aperture plate 59 forms a closed space 53f by the inner wall of the hole 59b, the capacitor side plate 53b, and the chiller side plate 53a, and this space 53f has a heat insulating function between the capacitor 52 and the chiller 51. Therefore, heat conduction between the capacitor 52 and the chiller 51 is suppressed. Further, heat conduction to the refrigerant flowing through the throttle portion 53c is also suppressed.

  The shape of the throttle groove 59a is a straight line. However, the shape is not limited to this, and any shape may be used as long as it causes pressure loss to the refrigerant and can be decompressed and expanded in the refrigerant discharge portion 53e. For example, the throttle groove 59a is formed to meander. May be.

  Returning to FIG. 1, the heat pump unit 4 includes a three-way valve 48 that switches between a state in which the refrigerant compressed by the electric compressor 42 is guided to the integrated heat exchanger 50 and a state in which the refrigerant is guided to the evaporator 45.

  The three-way valve 48 is switched by a command signal from the controller. When the three-way valve 48 is switched so as to guide the refrigerant compressed by the electric compressor 42 to the evaporator 45, the refrigerant passes through the outdoor heat exchanger 43, the expansion valve 44, the evaporator 45, and the accumulator 46 and again becomes the electric compressor 42. To be supplied. On the other hand, when the three-way valve 48 is switched to a state in which the refrigerant compressed by the electric compressor 42 is guided to the integrated heat exchanger 50, the refrigerant passes through the condenser 52 and the chiller 51 and then passes through the return flow path 49. The electric compressor 42 is supplied again via the accumulator 46.

  The heater unit 6 includes an engine cooling circuit 60 that cools the engine 9 with cooling water, a heater circuit 70 that heats the heater core 75 that heats the air guided to the passenger compartment of the vehicle 1 through the air passage 2, and the shut-off state. And a three-way valve 7 that shuts off the communication between the engine cooling circuit 60 and the heater circuit 70 when switched.

  The engine cooling circuit 60 includes a cooling water circulation passage 63 through which cooling water circulates, a water pump 61 that circulates the cooling water in the cooling water circulation passage 63, and a chiller 51. The coolant circulation passage 63 circulates coolant in the engine 9 of the vehicle 1. The cooling water circulation passage 63 can also circulate cooling water to the radiator 8 of the vehicle 1. The engine cooling circuit 60 may include an exhaust heat recovery device that warms the cooling water using the exhaust heat of the engine 9.

  The heater circuit 70 includes a cooling water circulation passage 73 through which the cooling water circulates, a water pump 71 that circulates the cooling water in the cooling water circulation passage 73, a condenser 52, and a heater core 75 disposed in the air passage 2. Have.

  The three-way valve 7 is switched by a command signal from the controller. When the three-way valve 7 is switched to the communication state, the communication passage 65 communicates and the cooling water circulation passage 63 and the cooling water circulation passage 73 communicate. In this case, the cooling water heated by the engine 9 passes through the three-way valve 7 and is guided to the heater core 75. On the other hand, when the three-way valve 7 is switched to the shut-off state, the communication passage 65 is shut off, and the communication between the coolant circulation passage 63 and the coolant circulation passage 73 is shut off. In this case, the cooling water circulates independently in the cooling water circulation passage 63 and the cooling water circulation passage 73. Instead of the three-way valve 7, an on-off valve that switches the communication passage 65 between a communication state and a cutoff state may be used as a cutoff mechanism.

  A mix door 76 is provided upstream of the heater core 75 in the air path 2 to adjust the flow rate of the air flowing through the air path 2 between the air guided to the heater core 75 and the air bypassing the heater core 75. The mix door 76 operates in response to a command signal from the controller.

  Next, the operation of this embodiment will be described.

  In the vehicle air conditioner 100, the three-way valve 7 blocks the cooling water circulation passage 63 and the cooling water circulation passage 73, and the heat pump heating mode in which the heat pump unit 4 operates, and the three-way valve 7 includes the cooling water circulation passage 63 and the cooling water circulation passage 73. The heating operation is performed in any one of the engine heating mode for communicating with the engine.

<Heat pump heating mode>
The operation in the heat pump heating mode is performed in a state where the temperature of the engine 9 is relatively low. In the heat pump heating mode, the three-way valve 48 is switched to a state in which the refrigerant is guided to the integrated heat exchanger 50. The three-way valve 7 is switched to the cutoff state.

  In the heat pump heating mode, the cooling water circulates independently in the cooling water circulation passage 63 and the cooling water circulation passage 73. Accordingly, cooling water for cooling the engine 9 flows through the chiller 51 of the integrated heat exchanger 50, and cooling water flowing through the heater core 75 flows through the condenser 52 of the integrated heat exchanger 50.

  In the heat pump unit 4, the refrigerant discharged from the electric compressor 42 passes through the integrated heat exchanger 50, passes through the return channel 49, and is returned to the electric compressor 42 through the accumulator 46.

  In the condenser 52 of the integrated heat exchanger 50, the high-temperature refrigerant discharged from the electric compressor 42 flows into the first refrigerant flow path 52d via the refrigerant inflow pipe 52a, and the cooling water flowing through the heater core 75 flows into the first cooling water flow. It flows into the first cooling water flow path 52e through the inlet pipe 52b. In the condenser 52, the cooling water absorbs heat from the refrigerant, the cooling water is heated, and the refrigerant is cooled. The heated cooling water is discharged to the heater core 75 through the first cooling water discharge pipe 52c. The cooled refrigerant flows into the expansion part 53 through the first refrigerant discharge hole 52g.

  The integrated heat exchanger 50 is configured by stacking the capacitor 52, the expansion unit 53, and the chiller 51 so that the expansion unit 53 is sandwiched between the capacitor 52 and the chiller 51. Accordingly, the refrigerant discharged from the capacitor 52 flows into the expansion unit 53 without going through the external circuit, and the refrigerant discharged from the expansion unit 53 flows into the chiller 51 without going through the external circuit.

  In the chiller 51, the refrigerant decompressed and expanded by the expansion portion 53 flows into the second refrigerant flow path 51d via the second refrigerant inflow hole 51f, and the cooling water passing through the engine 9 passes through the second cooling water inflow pipe 51b. It flows into the second cooling water channel 51e. In the chiller 51, the refrigerant absorbs heat from the cooling water and evaporates. The evaporated refrigerant is discharged from the refrigerant discharge pipe 51a. The cooling water is discharged from the second cooling water discharge pipe 51c.

  Thus, in the heat pump heating mode, the heat of the cooling water flowing through the cooling water circulation passage 63 is recovered by the chiller 51, and the cooling water flowing through the cooling water circulation passage 73 is heated by the condenser 52 using the recovered heat. And the air in the air path 2 is warmed with the heater core 75 using the heated cooling water.

<Engine heating mode>
The operation in the engine heating mode is performed in a state where the temperature of the cooling water is higher than that in the heat pump heating mode. In the engine heating mode, the operation of the electric compressor 42 is stopped, and the refrigerant does not circulate in the heat pump unit 4. The three-way valve 7 is switched to the communication state.

  Thereby, the cooling water circulation passage 63 and the cooling water circulation passage 73 communicate with each other, and the cooling water heated by the engine 9 is guided to the heater core 75. And the air in the air path 2 is warmed with the heater core 75 using the cooling water to which the heat of the engine 9 was transmitted.

  The effect of the embodiment of the present invention will be described.

  The condenser 52, the expansion part 53, and the chiller 51 are stacked to constitute the integrated heat exchanger 50, and the expansion part 53 is provided between the capacitor 52 and the chiller 51. As a result, the refrigerant can be decompressed and expanded and supplied from the capacitor 52 to the chiller 51 without using an external circuit. Therefore, the heat exchanger can be reduced in size.

  The expansion plate 53 is formed between the condenser 52 and the chiller 51 by forming the diaphragm plate 59 in which the diaphragm groove 59a for forming the diaphragm 53c is formed. Thereby, the integrated heat exchanger 50 can be assembled easily and a heat exchanger can be reduced in size.

  A space 53f is formed by the inner wall of the hole 59b formed in the aperture plate 59, the capacitor side plate 53b, and the chiller side plate 53a. Since the space 53f has a heat insulating function, heat conduction between the capacitor 52 and the chiller 51 can be suppressed. Further, by forming the hole 59b in the aperture plate 59 to form the space 53f, a heat insulating function can be imparted to the aperture plate 59 with a simple configuration.

  By providing a hole 59b around the throttle groove 59a that forms the throttle part 53c and forming the space 53f, heat conduction to the refrigerant flowing through the throttle part 53c is suppressed, and the temperature of the refrigerant flowing through the throttle part 53c increases. This can be suppressed and the heat absorption efficiency of the refrigerant in the chiller 51 can be improved.

  An aperture groove 59a is provided in the aperture plate 59 on the chiller 51 side. Even if heat is radiated from the coolant flowing through the throttle groove 59a to the coolant flowing through the chiller 51, the coolant and the coolant flowing through the second coolant channel 51d exchange heat, and the coolant absorbs heat. That is, even when heat is radiated from the refrigerant flowing through the throttle groove 59a, the heat is again absorbed by the refrigerant. Thus, by providing the throttle groove 59a in the throttle plate 59 on the chiller 51 side, heat loss, that is, energy loss can be reduced.

  By providing the throttle groove 59a in a straight line, the length of the throttle portion 53c can be shortened, the heat conduction from the condenser 52 and the chiller 51 to the refrigerant flowing through the throttle portion 53c is suppressed, and the refrigerant flowing through the throttle portion 53c. It is possible to suppress the temperature of the chiller 51 from increasing, and to improve the heat absorption efficiency of the refrigerant in the chiller 51.

  In the chiller 51, by performing heat exchange between the cooling water that has cooled the engine 9 and the refrigerant, the heat of the cooling water can be used for heating even when the temperature of the engine is low during heating.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  A recess may be provided on the back side of the throttle groove 59a, that is, on the capacitor 52 side to suppress heat conduction from the capacitor 52 to the refrigerant flowing through the throttle portion 53c.

  In the above embodiment, the diaphragm groove 59a is formed in the diaphragm plate 59 on the chiller 51 side. However, the present invention is not limited to this, and may be formed in the diaphragm plate 59 on the capacitor 52 side.

4: Heat pump unit 6: Heater unit 9: Engine 50: Integrated heat exchanger 51: Chiller (evaporator)
52: Condenser (condensing part)
53: Expansion part 53a: Chiller side plate 53b: Capacitor side plate 53c: Restriction part 53f: Space (heat insulation part)
59: Aperture plate (plate)
59a: throttle groove (groove)
59b: Hole 60: Engine cooling circuit (cooling water circuit)

Claims (9)

A heat exchanger comprising a condensing unit for condensing a cooling medium, an evaporating unit for evaporating the cooling medium, and an expansion unit for expanding the cooling medium passing through the condensing unit under reduced pressure and flowing into the evaporating unit. And
The heat exchanger is an integrated heat exchanger in which the condensing unit, the expansion unit, and the evaporation unit are stacked.
The expansion part is provided between the condensing part and the evaporation part.
A heat exchanger characterized by that. The heat exchanger according to claim 1,
The expansion portion includes a plate in which a groove that forms a throttle portion that decompresses and expands the cooling medium is formed.
A heat exchanger characterized by that. The heat exchanger according to claim 2,
The expansion part includes a heat insulating part that suppresses heat conduction between the condensing part and the evaporation part,
A heat exchanger characterized by that. The heat exchanger according to claim 3,
The plate is formed with holes or recesses in the stacking direction,
The heat insulating portion is a space formed by using the hole or the inner wall of the concave portion.
A heat exchanger characterized by that. The heat exchanger according to claim 4,
The space is formed around the groove;
A heat exchanger characterized by that. A heat exchanger according to any one of claims 2 to 5,
The groove is formed in the plate on the evaporation unit side,
A heat exchanger characterized by that. The heat exchanger according to any one of claims 2 to 6,
The groove is formed in a straight line,
A heat exchanger characterized by that. A heat exchanger according to any one of claims 1 to 7,
The condensing unit and the evaporating unit perform heat exchange between the cooling medium and water.
A heat exchanger characterized by that. The heat exchanger according to claim 8,
The water is cooling water that flows through a cooling water circuit that cools the engine.
A heat exchanger characterized by that.

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