WO2013080535A1 - 熱交換器 - Google Patents
熱交換器 Download PDFInfo
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- WO2013080535A1 WO2013080535A1 PCT/JP2012/007629 JP2012007629W WO2013080535A1 WO 2013080535 A1 WO2013080535 A1 WO 2013080535A1 JP 2012007629 W JP2012007629 W JP 2012007629W WO 2013080535 A1 WO2013080535 A1 WO 2013080535A1
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- WIPO (PCT)
- Prior art keywords
- tube
- refrigerant
- fluid
- heat exchange
- space
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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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00321—Heat exchangers for air-conditioning devices
- B60H1/00328—Heat exchangers for air-conditioning devices of the liquid-air type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00321—Heat exchangers for air-conditioning devices
- B60H1/00342—Heat exchangers for air-conditioning devices of the liquid-liquid type
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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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
- F28D1/0435—Combination of units extending one behind the other
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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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
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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
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
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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
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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
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over 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
- F28F2009/0285—Other particular headers or end plates
- F28F2009/0287—Other particular headers or end plates having passages for different heat exchange media
Definitions
- This disclosure relates to a composite heat exchanger configured to be able to exchange heat between three types of fluids.
- a composite heat exchanger configured to exchange heat between three types of fluids.
- heat exchanger disclosed in Patent Document 1 heat exchange between the refrigerant of the refrigeration cycle apparatus and outdoor air (outside air) and heat exchange between the refrigerant and the coolant that cools the engine are performed.
- a composite heat exchanger configured so as to be able to do this.
- the configuration is complicated and easy to increase in size. Therefore, the applicant of the present application has previously described Japanese Patent Application Nos. 2010-145011 and 2010-251119.
- the tubes are arranged in two rows in the air (third fluid) flow direction, and the refrigerant (first fluid) and the coolant (second fluid) flow using the tubes arranged in the two rows.
- the structure which makes U-turn is proposed.
- the pressure loss of the internal fluid in the entire plurality of tubes disposed on the upstream side of the third fluid is different from the pressure loss of the internal fluid in the entire plurality of tubes disposed on the downstream side of the third fluid.
- the fluid distribution is biased.
- This indication aims at providing the heat exchanger which can adjust the amount of heat exchange between three types of fluids appropriately in view of the above-mentioned point.
- the heat exchanger includes a plurality of first tubes through which the first fluid flows, and a plurality of second tubes through which the second fluid flows, and the first fluid and the second fluid are stacked.
- a heat exchange unit that exchanges heat between the first fluid and the third fluid, a first tank space that communicates with the first tube and collects the first fluid from the first tube or distributes the first fluid to the first tube, and a second tube
- a tank part having a second tank space that communicates and collects the second fluid from the second tube or distributes it to the second tube, and is formed between adjacent tubes of the first tube and the second tube;
- a third fluid passage through which the three fluids circulate, and a third fluid passage, which promote heat exchange between the first fluid and the third fluid and heat exchange between the second fluid and the third fluid
- an outer fin that enables heat transfer between the second fluid flowing through the two tubes, and the heat exchanging portion has an upstream heat exchanging portion and a flow direction of the third fluid with respect to the up
- the first tube is disposed in both the upstream heat exchange unit and the downstream heat exchange unit
- the second tube is composed of the upstream heat exchange unit and the downstream heat exchange unit disposed on the downstream side of Arranged in at least one of the downstream heat exchange sections, the upstream heat exchange section and the downstream heat exchange section are portions where the first tubes overlap in the flow direction of the third fluid, and the flow direction of the third fluid
- the first tube and the second tube are arranged so that both of the portions overlap each other, and the tank portion closes the first tank space and the second tank space from the first and second tube sides.
- Has a plate member arranged The plate member is formed with a first fluid communication passage for communicating the first tank space and the first tube, and a second fluid communication passage for communicating the second tank space and the second tube by the through holes.
- the plurality of first tubes of the upstream heat exchange section is the upstream first tube group
- the plurality of first tubes of the downstream heat exchange section is the downstream first tube group
- the upstream first tube The pressure loss of the first fluid among the group and the downstream first tube group becomes the high pressure loss side first tube group, and the pressure of the first fluid among the upstream first tube group and the downstream first tube group
- the one where the loss is reduced is the low pressure loss side first tube group
- the flow path resistance between the high pressure loss side first tube group and the first tank space is between the low pressure loss side first tube group and the first tank space. It is smaller than the channel resistance between them.
- the first fluid in the flow path between the first tank space and the first tube, the first fluid can flow more easily to the high pressure loss side first tube group than to the low pressure loss side first tube group. Can be prevented from being biased, and as a result, the amount of heat exchange between the three types of fluids can be adjusted appropriately.
- the reason for the difference in pressure loss between the first tube of the upstream heat exchange section and the first tube of the downstream heat exchange section is that when the individual first tubes are viewed, the first of the upstream heat exchange section is the first.
- circulates the 1st tube of a downstream heat exchange part are mentioned.
- the pressure loss is larger than when the first fluid flowing through the first tube is in a liquid phase state.
- the difference in pressure loss may be caused by the difference in the structure (shape, total length, flow path area, etc.) of the first tube in the upstream heat exchange section and the first tube in the downstream heat exchange section.
- the difference between the flow area in the entire upstream first tube group and the flow area in the entire downstream first tube group that is, the sum of the flow areas in the individual first tubes The difference between them has the greatest influence on the difference in pressure loss of the first fluid in the upstream and downstream first tube groups. Therefore, if the number of first tubes constituting the upstream first tube group is smaller than, for example, the downstream first tube group, the upstream first tube group is the high pressure loss side first tube group, and the downstream side first tube group is the downstream side first tube group.
- One tube group is a low pressure loss side first tube group.
- the upstream first tube group is the low pressure loss side first tube group
- the downstream side first tube group is One tube group is a high pressure loss side first tube group.
- the first tank space is connected to the inlet side of the first tube and distributes the first fluid.
- An outlet side first tank space connected to the outlet side of the tube and collecting the first fluid, and the flow path resistance between the high pressure loss side first tube group and the inlet side first tank space is low pressure loss.
- the flow path resistance between the side first tube group and the inlet side first tank space may be smaller.
- the inlet side first tank space may be disposed closer to the high pressure loss side first tube group than the low pressure loss side first tube group in the flow direction of the third fluid.
- the opening that opens toward the first tube of the communication passage that communicates the inlet-side first tank space and the high-pressure-loss-side first tube group is at least partially perpendicular to the opening end surface of the first tube. It may be provided so as to overlap with the opening end face.
- the first fluid can be vigorously flowed into the first tubes constituting the high pressure loss side first tube group using the dynamic pressure of the first fluid. Therefore, for example, it is possible to suppress a large amount of the first fluid from flowing toward the low pressure loss side first tube group.
- the first tube in the heat exchanger of the second example, may be arranged so that the first fluid flowing through the first tube has a flow velocity component in the direction of gravity,
- the first fluid may be a refrigerant.
- the first fluid that has exchanged heat with the third fluid at least once in the heat exchange section may be introduced into the inlet-side first tank space, and the inlet-side first tank space may include the high-pressure loss side first tube group. It may be arranged on the top.
- the heat exchanger functions as an evaporator or a condenser, as described above, if the first fluid exchanges heat with the third fluid once in the heat exchange section, the gas and the It is in a state composed of two phases of liquid.
- the liquid component contained in the first fluid is more susceptible to gravity than gas, most of the first fluid is in the inlet-side first tank space. It is easy to flow into the first tube connected to the upstream side in the first fluid flow direction. Therefore, when the inlet-side first tank space is arranged on the high-pressure loss side first tube group, the inlet-side first tank space is on the low-pressure loss side first tube group where the first fluid easily flows.
- the first fluid is biased on the upstream side of the first fluid flow in the inlet-side first tank space and flows into the first tube.
- the first fluid can be uniformly supplied to the plurality of first tubes connected to the inlet-side first tank space.
- the heat exchanger includes a plurality of first tubes through which the first fluid flows and a plurality of second tubes through which the second fluid flows, and the first fluid and the second fluid are stacked.
- a heat exchange unit that exchanges heat between the first fluid and the third fluid, a first tank space that communicates with the first tube and collects the first fluid from the first tube or distributes the first fluid to the first tube, and a second tube
- a tank part having a second tank space that communicates and collects the second fluid from the second tube or distributes it to the second tube, and is formed between adjacent tubes of the first tube and the second tube;
- a third fluid passage through which the three fluids circulate, and a third fluid passage, which promote heat exchange between the first fluid and the third fluid and heat exchange between the second fluid and the third fluid
- an outer fin that enables heat transfer between the second fluid flowing through the two tubes, and the heat exchanging portion has an upstream heat exchanging portion and a flow direction of the third fluid with respect to the upstream
- the first tube is disposed in both the upstream heat exchange unit and the downstream heat exchange unit
- the second tube is composed of the upstream heat exchange unit and the downstream heat exchange unit disposed on the downstream side of Arranged in at least one of the downstream heat exchange sections, the upstream heat exchange section and the downstream heat exchange section are portions where the first tubes overlap in the flow direction of the third fluid, and the flow direction of the third fluid
- the first tube and the second tube are arranged so that both of the portions overlap each other, and the tank portion closes the first tank space and the second tank space from the first and second tube sides.
- Has a plate member arranged The plate member is formed with a first fluid communication passage for communicating the first tank space and the first tube, and a second fluid communication passage for communicating the second tank space and the second tube by the through holes.
- the first tube in which the pressure loss of the first fluid increases becomes the high pressure loss side first tube
- the flow path resistance between the high pressure loss side first tube and the first tank space is the same as that of the low pressure loss side first tube and the first tube. It is smaller than the flow path resistance between the tank space.
- the first fluid can easily flow to the first tube on the high pressure loss side, it is possible to suppress the occurrence of bias in the distribution of the fluid, and thus appropriately adjust the amount of heat exchange between the three types of fluids. be able to.
- the ratio of the number of the first tubes to the total number of the first tubes and the second tubes constituting the upstream heat exchange unit may be different.
- the first tank space and the second tank space are formed to extend in the stacking direction of the first tube and the second tube, You may arrange
- the first tank space is disposed closer to the low pressure loss side first tube than the high pressure loss side first tube in the flow direction of the third fluid, and the second tank space is low pressure in the flow direction of the third fluid. It may be arranged closer to the high pressure loss side first tube than the loss side first tube.
- the plate member communicates the high pressure loss side first passage and the first tank space, and the low pressure loss side first tube and the first tank space.
- the low pressure loss side communication path may be formed, and the flow resistance of the high pressure loss side communication path is smaller than the flow resistance of the low pressure loss side communication path, whereby the high pressure loss side first tube and the first tank.
- the flow path resistance between the spaces may be smaller than the flow path resistance between the low pressure loss side first tube and the first tank space.
- the plate member is formed with a through hole constituting the high pressure loss side communication path and a through hole constituting the low pressure loss side communication path. Also good. Since the hole area of the through hole constituting the high pressure loss side communication path is larger than the hole area of the through hole constituting the low pressure loss side communication path, the flow resistance of the high pressure loss side communication path is reduced. It may be smaller than the flow path resistance of the passage.
- the first tank space and the second tank space are formed to extend in the stacking direction of the first tube and the second tube, You may arrange
- the first tank space is disposed closer to the high pressure loss side first tube than the low pressure loss side first tube in the flow direction of the third fluid, and the second tank space is positioned on the high pressure loss side first in the flow direction of the third fluid.
- the heat exchanger includes a plurality of first tubes through which the first fluid flows, and a plurality of second tubes through which the second fluid flows, and the first fluid and the second fluid are stacked.
- a heat exchange unit that exchanges heat between the first fluid and the third fluid, a first tank space that communicates with the first tube and collects the first fluid from the first tube or distributes the first fluid to the first tube, and a second tube
- a tank part having a second tank space that communicates and collects the second fluid from the second tube or distributes it to the second tube, and is formed between adjacent tubes of the first tube and the second tube;
- a third fluid passage through which the three fluids circulate, and a third fluid passage, which promote heat exchange between the first fluid and the third fluid and heat exchange between the second fluid and the third fluid
- an outer fin that enables heat transfer between the second fluid flowing through the two tubes, and the heat exchanging portion has an upstream heat exchanging portion and a flow direction of the third fluid with respect to the up
- the first tube is disposed in both the upstream heat exchange unit and the downstream heat exchange unit
- the second tube is composed of the upstream heat exchange unit and the downstream heat exchange unit disposed on the downstream side of Arranged in at least one of the downstream heat exchange sections, the upstream heat exchange section and the downstream heat exchange section are portions where the first tubes overlap in the flow direction of the third fluid, and the flow direction of the third fluid
- the first tube space and the second tank space are formed so as to extend in the stacking direction of the first tube and the second tube. , How the third fluid flows Are arranged side by side, and the first tank space is located at an equal distance from the first tube of the upstream heat exchange section and the first tube of the downstream heat exchange section at a position in the flow direction of the third fluid.
- the ratio of the number of tubes occupied by the first tube of the downstream heat exchange section is different from the total number of tubes of the first tube and the second tube constituting the downstream heat exchange section.
- the first fluid can be more easily flowed to the high-pressure loss side first tube than in the case where the first tank space is arranged at a position that does not overlap the virtual straight line.
- production can be suppressed and by extension, the heat exchange amount between three types of fluids can be adjusted appropriately.
- the first tank space is connected to the inlet side of the first tube, and the inlet-side first tank space that distributes the first fluid;
- An outlet side first tank space that is connected to the outlet side of the tube and collects the first fluid may be configured.
- the position of the inlet-side first tank space in the flow direction of the third fluid overlaps with a virtual straight line that is equidistant from the first tube of the upstream heat exchange unit and the first tube of the downstream heat exchange unit.
- the plurality of first tubes of the upstream heat exchange section may be an upstream first tube group, and the plurality of first tubes of the downstream heat exchange section may be a downstream first tube group.
- the one where the pressure loss of the first fluid increases becomes the high pressure loss first tube group
- One tube group having the smaller pressure loss of the first fluid may be the low pressure loss side first tube group.
- the inlet side first tank space may be arranged closer to the high pressure loss side first tube group than the low pressure loss side first tube group.
- the opening that opens toward the first tube of the communication path that connects the inlet-side first tank space and the high-pressure loss-side first tube group has at least a portion thereof in a direction perpendicular to the opening end surface of the first tube. It may be provided so as to overlap the opening end face.
- the first tube may be arranged such that the first fluid flowing through the first tube has a flow velocity component in the direction of gravity, and the first fluid may be a refrigerant.
- the first fluid that has exchanged heat with the third fluid at least once in the third fluid passage may be introduced into the inlet-side first tank space. You may arrange
- the heat exchanger in any one of the second, third, and tenth heat exchangers, may be used as an evaporator that evaporates the first fluid, and the outlet side first tank The space may be disposed closer to the low pressure loss side first tube group than the high pressure loss side first tube group in the flow direction of the third fluid.
- the tank portion is arranged so that the first fluid can easily flow into the outlet side first tank space from the low pressure loss side first tube group in which the first fluid flows more easily than the high pressure loss side first tube group. Is easy to configure.
- the pressure loss difference of the first fluid between the high pressure loss side first tube group and the low pressure loss side first tube group is caused by the difference in the number of stacked first tubes in each first tube group. If so, it is easy to increase the overall cross-sectional area of the flow path from the low pressure loss side first tube group to the outlet side first tank space having a large number of layers. And a tank part can be constituted so that the 1st fluid can easily flow into the outlet side 1st tank space by enlarging the channel cross-sectional area as a whole. If the tank portion is configured in this manner, the pressure loss of the first fluid can be reduced as a whole heat exchanger, and the heat exchange performance of the heat exchanger can be improved.
- the number of first tubes included in the high pressure loss side first tube group is the low pressure loss side. It may be at least as compared with the first tube group.
- the high pressure loss side first tube group is an upstream side first tube group, and the low pressure The loss side first tube group may be the downstream side first tube group.
- the temperature difference between the first fluid and the third fluid is likely to be larger in the upstream heat exchange section than in the downstream heat exchange section, so the amount of heat exchange in the upstream heat exchange section and the downstream The amount of heat exchange in the side heat exchange section is appropriately adjusted.
- the first tank space may be configured as a pair.
- the heat exchanging unit may include three or more first fluid paths, and each first fluid path may include one or two or more first tubes interposed between a pair of first tank spaces. Good.
- the first fluid paths may be connected in series in the flow path of the first fluid, and each first fluid path is in the direction of gravity with respect to other first fluid paths adjacent in the flow path. It may flow in the opposite direction.
- the first fluid path may include an upward flow first fluid path in which the first fluid flows upward in the gravitational direction, and the upward flow is about the stacking width of the first tubes constituting the first fluid path in the stacking direction of the first tubes.
- the first fluid path may be smaller than any first fluid path that is adjacent in the flow path of the first fluid.
- the flow path of the first fluid is narrowed according to the fact that the laminated width of the first tubes constituting the upward flow first fluid path is small. Therefore, the flow rate of the upward flow in which the first fluid flows upward in the direction of gravity in the first tube is increased, and for example, it is possible to raise the first fluid vigorously against the weight of the liquid component contained in the first fluid. It is. As a result, the first fluid can easily flow through each first tube evenly.
- the heat exchanger functions as, for example, a condenser
- the first fluid in the first tube has a high pressure and a low flow rate, and thus the effect of the fourteenth example becomes remarkable.
- the tank unit may further include a third tank space extending in the stacking direction of the second tubes, and the first tank space, The two tank space and the third tank space may be arranged side by side in the flow direction of the third fluid.
- An in-tank communication path that connects the first tank space and the third tank space may be formed inside the tank portion.
- the heat exchanger in the heat exchanger of the fifteenth example, is outside the tank unit and is located on the opposite side of the first tube and the second tube with respect to the tank unit.
- a connector for connecting the refrigerant pipe may be further provided, and the connector may be formed with a connector communication path that communicates the internal space of the connector with the first tank space.
- the tank unit may include a third tank space extending in the stacking direction of the second tubes, and the first tank space, the second tank The tank space and the third tank space may be arranged side by side in the flow direction of the third fluid.
- the heat exchanger may further include a connector for connecting a refrigerant pipe at a portion outside the tank portion and on the opposite side of the first tube and the second tube with respect to the tank portion.
- a first connector communication path that communicates the internal space of the connector with the first tank space and a second connector communication path that communicates the internal space with the third tank space may be formed.
- the first fluid and the second fluid may be a heat medium that circulates in different fluid circulation circuits.
- the heat exchanger can be shared by a plurality of fluid circulation circuits, and it becomes easy to reduce the installation space of the heat exchanger.
- the heat exchanger may be a heat exchanger used as an evaporator for evaporating a refrigerant in a vapor compression refrigeration cycle
- the first fluid may be a refrigerant of the refrigeration cycle
- the second fluid may be a heat medium that absorbs heat from an external heat source
- the third fluid may be air.
- the upstream heat exchange section has a larger temperature difference between the refrigerant and air than the downstream heat exchange section, and the vaporization of the refrigerant is promoted. As a result, the refrigerant becomes difficult to be distributed to the first tube of the upstream heat exchange section.
- the present disclosure it is possible to facilitate the flow of the refrigerant to the first tube of the upstream heat exchange unit where the pressure loss increases due to the vaporization of the refrigerant. It is possible to suppress the occurrence of bias due to the arrangement of the first tube in the flow direction, and thus it is possible to appropriately adjust the amount of heat exchange between the three types of fluids of the refrigerant, the heat medium, and air.
- the heat exchanger may be a heat exchanger used as a condenser for condensing a refrigerant in a vapor compression refrigeration cycle
- the first fluid may be a refrigerant of the refrigeration cycle
- the second fluid may be a heat medium that absorbs heat from an external heat source
- the third fluid may be air.
- the heat exchanger When the heat exchanger is used as a condenser in this way, when the temperature of the heat medium becomes high, condensation (liquefaction) of the refrigerant in the first tube is impaired and more refrigerant flows in the gas phase state. The pressure loss of the refrigerant increases, and as a result, the refrigerant distribution tends to be biased between the first tube of the upstream heat exchange section and the first tube of the downstream heat exchange section.
- the refrigerant easily flows through the first tube in which the refrigerant pressure loss increases. Therefore, it is possible to suppress the occurrence of bias in the distribution of the refrigerant due to the arrangement of the first tube in the flow direction of the third fluid. As a result, heat exchange between the three types of fluids of the refrigerant, the heat medium, and air The amount can be adjusted appropriately.
- the heat exchanger may be a heat exchanger applied to a vehicle cooling system, and the first fluid generates heat during operation.
- the heat medium that has absorbed the amount of heat of the first in-vehicle device, the second fluid may be the heat medium that has absorbed the heat amount of the second in-vehicle device that generates heat during operation, and the third fluid may be air.
- the heat exchanger may be a heat exchanger used as an evaporator for evaporating the first fluid
- the number of second tubes included in the exchange unit may be larger than that in the downstream heat exchange unit. You may defrost by distribute
- frost formation on the heat exchanger is suppressed by the heat of the second fluid. Since the second fluid flows more preferentially to the upstream side in the flow direction of the third fluid that tends to form frost than the downstream side, for example, the second fluid flows evenly on the upstream side and the downstream side. In comparison, frost formation can be further suppressed, and efficient heat exchange can be realized.
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (C) It is sectional drawing of the part by which the connector is arrange
- (A) It is sectional drawing of the part with which the tube for refrigerant
- (B) It is sectional drawing of the part with which the tube for refrigerant
- (C) It is sectional drawing of the part by which the connector is arrange
- FIGS. 1 to 3 are overall configuration diagrams of the vehicle air conditioner 1 according to the first embodiment.
- the vehicle air conditioner 1 is applied to a so-called hybrid vehicle that obtains a driving force for traveling a vehicle from an internal combustion engine (engine) and a traveling electric motor MG.
- the hybrid vehicle operates or stops the engine in accordance with the traveling load of the vehicle, etc., obtains driving force from both the engine and the traveling electric motor MG, or travels when the engine is stopped. It is possible to switch the running state where the driving force is obtained only from the MG. Thereby, in a hybrid vehicle, vehicle fuel consumption can be improved compared to a normal vehicle that obtains driving force for vehicle travel only from the engine.
- the heat pump cycle 10 is a vapor compression refrigeration cycle that functions in the vehicle air conditioner 1 to heat or cool the air blown into the vehicle interior, which is the space to be air conditioned. Therefore, the heat pump cycle 10 switches the refrigerant flow path, heats the vehicle interior blown air that is a heat exchange target fluid to heat the vehicle interior, and heats the vehicle interior blown air.
- a cooling operation (cooling operation) for cooling the room can be executed.
- a defrosting operation is performed to melt and remove frost attached to the outdoor heat exchange unit 16 of the composite heat exchanger 70 described later that functions as an evaporator that evaporates the refrigerant during the heating operation. You can also.
- the flow of the refrigerant during each operation is indicated by a solid line arrow.
- a normal chlorofluorocarbon refrigerant is employed as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured.
- This refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.
- the compressor 11 is disposed in the engine room, sucks the refrigerant in the heat pump cycle 10 and compresses and discharges the refrigerant.
- a fixed capacity compressor 11a having a fixed discharge capacity is fixed by the electric motor 11b. It is an electric compressor to drive.
- various compression mechanisms such as a scroll compression mechanism and a vane compression mechanism can be employed as the fixed capacity compressor 11a.
- the electric motor 11b has its operation (the number of rotations) controlled by a control signal output from an air conditioning control device, which will be described later, and may employ either an AC motor or a DC motor. And the refrigerant
- the refrigerant discharge port of the compressor 11 is connected to the refrigerant inlet side of the indoor condenser 12 as a use side heat exchanger.
- the indoor condenser 12 is disposed in the casing 31 of the indoor air conditioning unit 30 of the vehicle air conditioner 1 and heats the high-temperature and high-pressure refrigerant that circulates inside the vehicle and the air blown into the vehicle interior after passing through the indoor evaporator 20 described later. It is a heat exchanger for heating to be exchanged.
- the detailed configuration of the indoor air conditioning unit 30 will be described later.
- the fixed outlet 13 for heating is connected to the refrigerant outlet side of the indoor condenser 12 as decompression means for heating operation for decompressing and expanding the refrigerant flowing out of the indoor condenser 12 during the heating operation.
- the heating fixed throttle 13 an orifice, a capillary tube or the like can be adopted.
- the refrigerant inlet side of the outdoor heat exchanger 16 of the composite heat exchanger 70 is connected to the outlet side of the heating fixed throttle 13.
- a fixed throttle bypass passage 14 is connected to the refrigerant outlet side of the indoor condenser 12 to guide the refrigerant flowing out of the indoor condenser 12 to the outdoor heat exchanger 16 side by bypassing the heating fixed throttle 13. Yes.
- the fixed throttle bypass passage 14 is provided with an on-off valve 15a for opening and closing the fixed throttle bypass passage 14.
- the on-off valve 15a is an electromagnetic valve whose opening / closing operation is controlled by a control voltage output from the air conditioning control device.
- the pressure loss that occurs when the refrigerant passes through the on-off valve 15a is extremely small compared to the pressure loss that occurs when the refrigerant passes through the fixed throttle 13. Accordingly, the refrigerant that has flowed out of the indoor condenser 12 flows into the outdoor heat exchanger 16 via the fixed throttle bypass passage 14 when the on-off valve 15a is open, and when the on-off valve 15a is closed. Flows into the outdoor heat exchanger 16 through the heating fixed throttle 13.
- the on-off valve 15a can switch the refrigerant flow path of the heat pump cycle 10. Accordingly, the on-off valve 15a of the present embodiment functions as a refrigerant flow path switching unit.
- Such refrigerant flow switching means includes a refrigerant circuit connecting the outlet side of the indoor condenser 12 and the inlet side of the fixed throttle 13 for heating, the outlet side of the indoor condenser 12 and the inlet side of the fixed throttle bypass passage 14.
- An electric three-way valve or the like that switches the refrigerant circuit that connects the two may be employed.
- the outdoor heat exchanger 16 is a heat exchanger that exchanges heat between the refrigerant circulating in the heat exchanger 70 and the outside air blown from the blower fan 17.
- This outdoor heat exchange unit 16 is disposed in the engine room and functions as an evaporating heat exchange unit that evaporates the low-pressure refrigerant and exerts an endothermic effect during heating operation, and dissipates heat to dissipate the high-pressure refrigerant during cooling operation. Functions as a heat exchanger.
- the blower fan 17 is an electric blower in which the operating rate, that is, the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device.
- a radiator unit 43 described later that exchanges heat between the outdoor heat exchange unit 16 described above and the coolant that cools the traveling electric motor MG and the outside air blown from the blower fan 17. are integrated.
- the blower fan 17 of the present embodiment constitutes an outdoor blower that blows outside air toward both the outdoor heat exchange unit 16 and the radiator unit 43.
- the detailed configuration of the composite heat exchanger 70 in which the outdoor heat exchanger 16 and the radiator 43 are integrally configured will be described later.
- An electrical three-way valve 15b is connected to the outlet side of the outdoor heat exchange unit 16.
- the operation of the three-way valve 15b is controlled by a control voltage output from the air-conditioning control device, and constitutes a refrigerant flow path switching unit together with the above-described on-off valve 15a.
- the three-way valve 15b is switched to a refrigerant flow path that connects an outlet side of the outdoor heat exchange unit 16 and an inlet side of an accumulator 18 described later during heating operation, and the outdoor heat exchange unit 16 during cooling operation. Is switched to a refrigerant flow path connecting the outlet side of the cooling and the inlet side of the cooling fixed throttle 19.
- the cooling fixed throttle 19 is a pressure reducing means for cooling operation that decompresses and expands the refrigerant that has flowed out of the outdoor heat exchanger 16 during the cooling operation, and the basic configuration thereof is the same as that of the heating fixed throttle 13.
- the refrigerant inlet side of the indoor evaporator 20 is connected to the outlet side of the cooling fixed throttle 19.
- the indoor evaporator 20 is disposed in the casing 31 of the indoor air conditioning unit 30 on the upstream side of the air flow with respect to the indoor condenser 12, and exchanges heat between the refrigerant circulating in the interior and the air blown into the vehicle interior, It is a heat exchanger for cooling which cools vehicle interior blowing air.
- the inlet side of the accumulator 18 is connected to the refrigerant outlet side of the indoor evaporator 20.
- the accumulator 18 is a gas-liquid separator for a low-pressure side refrigerant that separates the gas-liquid refrigerant flowing into the accumulator 18 and stores excess refrigerant in the cycle.
- the suction side of the compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 18. Accordingly, the accumulator 18 functions to prevent the compressor 11 from being compressed by suppressing the suction of the liquid phase refrigerant into the compressor 11.
- the temperature of the coolant flowing out from the radiator unit 43 of the heat exchanger 70 becomes lower than the temperature of the refrigerant flowing out of the outdoor heat exchange unit 16 of the heat exchanger 70. Yes.
- the degree of supercooling of the refrigerant flowing out of the outdoor heat exchange unit 16 can be increased. Can be improved.
- the temperature of the coolant inside the radiator 43 of the heat exchanger 70 is higher than the temperature of the refrigerant flowing out from the outdoor heat exchange unit 16 of the heat exchanger 70 during the heating operation. ing.
- the outdoor heat exchange unit 16 functions as an evaporating heat exchange unit that evaporates the low-pressure refrigerant and exerts an endothermic effect
- the refrigerant is heated by absorbing the amount of heat of the coolant, and the refrigerant Evaporation is promoted.
- the indoor air-conditioning unit 30 is disposed inside the instrument panel (instrument panel) at the foremost part of the vehicle interior, and a blower 32, the above-described indoor condenser 12, the indoor evaporator 20 and the like are provided in a casing 31 that forms the outer shell thereof. Is housed.
- the casing 31 forms an air passage for vehicle interior air that is blown into the vehicle interior, and is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.
- An inside / outside air switching device 33 that switches and introduces vehicle interior air (inside air) and outside air is disposed on the most upstream side of the air flow inside the casing 31.
- the inside / outside air switching device 33 is formed with an inside air introduction port for introducing inside air into the casing 31 and an outside air introduction port for introducing outside air. Furthermore, inside / outside air switching device 33 is provided with an inside / outside air switching door that continuously adjusts the opening area of the inside air introduction port and the outside air introduction port to change the air volume ratio between the inside air volume and the outside air volume. Has been.
- a blower 32 that blows air sucked through the inside / outside air switching device 33 toward the vehicle interior is disposed on the downstream side of the air flow of the inside / outside air switching device 33.
- the blower 32 is an electric blower that drives a centrifugal multiblade fan (sirocco fan) with an electric motor, and the number of rotations (the amount of blown air) is controlled by a control voltage output from the air conditioning control device.
- the indoor evaporator 20 and the indoor condenser 12 are arranged in this order with respect to the flow of the air blown into the vehicle interior.
- the indoor evaporator 20 is disposed upstream of the indoor condenser 12 in the flow direction of the air blown into the vehicle interior.
- An air mix door 34 for adjusting the air pressure is disposed. Further, on the downstream side of the air flow of the indoor condenser 12, the blown air heated by exchanging heat with the refrigerant in the indoor condenser 12 and the blown air that is not heated bypassing the indoor condenser 12 are mixed. A mixing space 35 is provided.
- an air outlet is arranged for blowing the conditioned air mixed in the mixing space 35 into the vehicle interior that is the space to be cooled.
- this air outlet a face air outlet that blows air-conditioned air toward the upper body of the passenger in the passenger compartment, a foot air outlet that blows air-conditioned air toward the feet of the passenger, and the inner surface of the front window glass of the vehicle.
- a defroster outlet (both not shown) is provided to blow air-conditioned air toward the front.
- the temperature of the conditioned air mixed in the mixing space 35 is adjusted by adjusting the ratio of the air volume that the air mix door 34 passes through the indoor condenser 12, and the temperature of the conditioned air blown out from each outlet is adjusted. Is adjusted. That is, the air mix door 34 constitutes a temperature adjusting means for adjusting the temperature of the conditioned air blown into the vehicle interior.
- the air mix door 34 functions as a heat exchange amount adjusting means for adjusting the heat exchange amount between the refrigerant discharged from the compressor 11 and the air blown into the vehicle interior in the indoor condenser 12 constituting the use side heat exchanger. Fulfill.
- the air mix door 34 is driven by a servo motor (not shown) whose operation is controlled by a control signal output from the air conditioning control device.
- a face door for adjusting the opening area of the face outlet, a foot door for adjusting the opening area of the foot outlet, and the defroster outlet respectively.
- a defroster door (none of which is shown) for adjusting the opening area is arranged.
- These face doors, foot doors, and defroster doors constitute the outlet mode switching means for switching the outlet mode, and their operation is controlled by a control signal output from the air conditioning controller via a link mechanism or the like. Driven by a servo motor (not shown).
- the coolant circulation circuit 40 in which the coolant as the second fluid, which is a different kind of material from the refrigerant used in the heat pump cycle 10, circulates will be described.
- the coolant circulation circuit 40 is a fluid circulation circuit different from the heat pump cycle 10 as shown in FIGS.
- the coolant circulation circuit 40 includes a coolant (heat medium) in a coolant passage formed inside the above-described traveling electric motor MG (external heat source), which is one of in-vehicle devices that generate heat during operation. ) Is a coolant circulation circuit that circulates a coolant (for example, an ethylene glycol aqueous solution) and cools the traveling electric motor MG.
- a coolant for example, an ethylene glycol aqueous solution
- the coolant circulation circuit 40 includes a coolant pump 41, an electric three-way valve 42, a radiator 43 of the composite heat exchanger 70, a bypass passage 44 that bypasses the radiator 43 and allows the coolant to flow. Has been placed.
- the coolant pump 41 is an electric pump that pumps the coolant to the coolant passage formed in the electric motor MG for traveling in the coolant circulation circuit 40, and is rotated by a control signal output from the air conditioning control device. The number (flow rate) is controlled. Therefore, the coolant pump 41 functions as a cooling capacity adjusting means for adjusting the cooling capacity by changing the flow rate of the coolant that cools the traveling electric motor MG.
- the three-way valve 42 is connected to the inlet side of the coolant pump 41 and the outlet side of the radiator section 43 to allow the coolant to flow into the radiator section 43, and the inlet side of the coolant pump 41 and the bypass passage 44.
- the coolant circuit is switched by connecting the outlet side of the coolant and flowing the coolant around the radiator 43.
- the operation of the three-way valve 42 is controlled by a control voltage output from the air conditioning control device, and constitutes a circuit switching means for the coolant circuit.
- the three-way valve 42 also functions as a coolant inflow control means for controlling the amount of coolant flowing into the radiator 43 by switching the coolant circuit.
- the coolant circulation circuit 40 of this embodiment as shown by the broken line arrows in FIG. 1 and the like, the coolant is circulated in the order of the coolant pump 41 ⁇ the traveling electric motor MG ⁇ the radiator unit 43 ⁇ the coolant pump 41.
- the coolant circuit and the coolant circuit that circulates the coolant in the order of coolant pump 41 ⁇ traveling electric motor MG ⁇ bypass passage 44 ⁇ coolant pump 41 can be switched.
- the coolant does not radiate heat at the radiator unit 43, and the temperature To raise. That is, when the three-way valve 42 is switched to a coolant circuit that causes the coolant to flow around the radiator 43, the amount of heat (heat generation amount) of the traveling electric motor MG is stored in the coolant. .
- the temperature of the coolant flowing out from the radiator 43 of the heat exchanger 70 is equal to or lower than a predetermined reference temperature (65 ° C. in this embodiment).
- a predetermined reference temperature 65 ° C. in this embodiment.
- the radiator unit 43 is disposed in the engine room and functions as a heat-dissipating heat exchange unit that exchanges heat between the coolant and the outside air blown from the blower fan 17. As described above, the radiator unit 43 constitutes the composite heat exchanger 70 together with the outdoor heat exchange unit 16.
- FIG. 4 is a perspective view of the heat exchanger 70 of the first embodiment
- FIG. 5 is an exploded view of the heat exchanger 70.
- FIG. 6 is a schematic perspective view for explaining the refrigerant flow and the coolant flow in the heat exchanger 70.
- the flow of the refrigerant in the heat pump cycle 10 is indicated by a solid line
- the flow of the coolant in the coolant circulation circuit 40 is indicated by a dashed arrow.
- FIG. 7A and FIG. 8A are cross-sectional views taken along line AA in FIG. 6, and FIGS. 7B and 8B are cross-sectional views taken along line BB in FIG. ) And FIG. 8 (c) are CC cross-sectional views of FIG. 6, and FIGS. 7 (d) and 8 (d) are DD cross-sectional views of FIG. 7 indicates the refrigerant flow, and the broken line arrow in FIG. 8 indicates the coolant flow.
- 9A is a cross-sectional view taken along the line EE in FIG. 7, and FIG. 9B is a cross-sectional view taken along the line FF in FIG.
- the composite heat exchanger 70 is provided with a plurality of tubes through which the refrigerant or the coolant flows, and is arranged on both ends of the plurality of tubes to circulate each tube.
- a so-called tank and tube type heat exchanger structure having a pair of collecting and distributing tanks for collecting or distributing the refrigerant or the cooling liquid is provided.
- the composite heat exchanger 70 includes a refrigerant tube 16a (first tube) in which a refrigerant as a first fluid flows and cooling in which a coolant as a second fluid flows.
- the composite heat exchanger 70 includes an upstream heat exchanging portion 71 configured by alternately stacking the refrigerant tubes 16a and the coolant tubes 43a.
- the upstream heat exchanging unit 71 exchanges heat between the refrigerant flowing through the refrigerant tube 16a and the air as the third fluid flowing around the refrigerant tube 16a (outside air blown from the blower fan 17) and the coolant. It is a heat exchange part which heat-exchanges the cooling fluid which distribute
- the downstream side heat exchange part 72 comprised by laminating
- the downstream heat exchange unit 72 is a heat exchange unit that exchanges heat between the refrigerant that flows through the refrigerant tube 16a and the air that flows around the refrigerant tube 16a (outside air blown from the blower fan 17).
- the refrigerant tube 16a and the coolant tube 43a flat tubes having a flat cross-sectional shape perpendicular to the longitudinal direction of the tube are employed. More specifically, as the refrigerant tube 16a, a tube having a flat multi-hole cross-sectional shape formed by extrusion is employed. Further, as the coolant tube 43a, a tube having a flat two-hole cross section formed by bending a single plate material is employed.
- the refrigerant tubes 16a and the coolant tubes 43a constituting the upstream heat exchange section 71 are alternately stacked with predetermined intervals so that the flat surfaces of the outer surfaces are parallel to each other and face each other. Has been.
- the refrigerant tubes 16a constituting the downstream heat exchanging section 72 are also stacked and arranged with a predetermined interval. This predetermined interval is equal to each other in both the upstream heat exchange section 71 and the downstream heat exchange section 72.
- the refrigerant tube 16a constituting the upstream heat exchange section 71 is disposed between the coolant tubes 43a, and the coolant tube 43a is disposed between the refrigerant tubes 16a.
- the refrigerant tube 16a constituting the downstream heat exchange part 72 and the refrigerant tube 16a or the coolant tube 43a constituting the upstream heat exchange part 71 are in the flow direction of the outside air blown by the blower fan 17. Are arranged so as to overlap each other.
- the refrigerant tubes 16a and the coolant tubes 43a are alternately arranged one by one, so the total number of the refrigerant tubes 16a and the sum of the coolant tubes 43a are the same.
- the number is the same.
- the ratio of the number of tubes occupied by the refrigerant tubes 16a of the upstream heat exchange section 71 with respect to the total number of the refrigerant tubes 16a and the coolant tubes 43a constituting the upstream heat exchange section 71 (hereinafter referred to as upstream)
- upstream the ratio of the number of tubes occupied by the refrigerant tubes 16a of the upstream heat exchange section 71 with respect to the total number of the refrigerant tubes 16a and the coolant tubes 43a constituting the upstream heat exchange section 71 (hereinafter referred to as upstream)
- the side number ratio) is 0.5.
- the total number of the coolant tubes 43 a included in the upstream heat exchange unit 71 is larger than that of the downstream heat exchange unit 72.
- downstream heat exchanging section 72 is configured only by the refrigerant tube 16a.
- the ratio of the number of tubes occupied by the refrigerant tubes 16a of the downstream heat exchange section 72 with respect to the total number of the refrigerant tubes 16a and the coolant tubes 43a constituting the downstream heat exchange section 72 (hereinafter referred to as downstream).
- the side number ratio) is 1.
- the upstream number ratio is smaller than the downstream number ratio.
- the heat exchanger 70 a space formed between the refrigerant tube 16a and the coolant tube 43a constituting the upstream heat exchange section 71, and an adjacent refrigerant tube 16a constituting the downstream heat exchange section 72.
- the space formed therebetween forms an outside air passage 70a (a third fluid passage) through which the outside air blown by the blower fan 17 flows.
- outside air passage 70a heat exchange between the refrigerant and the outside air and heat exchange between the cooling liquid and the outside air are promoted, and the refrigerant and the cooling liquid flowing through the refrigerant tube 16a constituting the upstream heat exchanging portion 71 are promoted.
- Outer fins 50 are arranged to enable heat transfer between the coolant flowing through the tubes 43a and heat transfer between the refrigerants flowing through the adjacent refrigerant tubes 16a constituting the downstream heat exchange section 72. Yes.
- the outer fin 50 a corrugated fin obtained by bending a metal thin plate having excellent heat conductivity into a wave shape is adopted. By being joined to both the tube 16a and the coolant tube 43a, heat transfer between the coolant tube 16a and the coolant tube 43a is enabled. Furthermore, the outer fin 50 is joined to the adjacent refrigerant tubes 16a constituting the downstream heat exchange section 72, thereby enabling heat transfer between the adjacent refrigerant tubes 16a.
- the stacked heat exchange unit 70 includes an upstream tank unit 73 extending in the stacking direction of the refrigerant tube 16a and the coolant tube 43a constituting the upstream heat exchange unit 71, and a refrigerant constituting the downstream heat exchange unit 72.
- the downstream tank part 74 extended in the lamination direction of the tube 16a for an operation is provided.
- the upstream tank unit 73 is disposed on both ends in the longitudinal direction of the refrigerant tube 16 a and the coolant tube 43 a of the upstream heat exchange unit 71, and the downstream tank unit 74 is connected to the refrigerant tube 16 a of the downstream heat exchange unit 72. It arrange
- the upstream tank portion 73 is formed with a coolant space 76 (second tank space) for collecting or distributing coolant flowing through the coolant tube 43a constituting the upstream heat exchanging portion 71.
- the downstream tank portion 74 is formed with a refrigerant space 77 (first tank space) for collecting or distributing the refrigerant flowing through the refrigerant tubes 16a constituting the downstream heat exchange portion 72.
- the refrigerant space 77 connected to one end of the refrigerant tube 16a is a refrigerant space 771 (first tube) on the refrigerant tube inlet side for distributing the refrigerant. It is an inlet side first tank space on the inlet side).
- the refrigerant space 77 connected to the other end (the tube outlet side, the upper side in FIG. 5) of the refrigerant tube 16a is a refrigerant space 772 (first tube outlet) on the refrigerant tube outlet side that collects refrigerant. Side outlet side first tank space).
- the upstream tank portion 73 and the downstream tank portion 74 are integrally formed.
- the one in which the upstream tank portion 73 and the downstream tank portion 74 are integrated is referred to as a header tank 75 (tank portion).
- the header tank 75 includes a header plate 751 to which both the refrigerant tubes 16a and the coolant tubes 43a arranged in two rows in the flow direction of the outside air are fixed, and an intermediate plate member 752 (plate member fixed to the header plate 751). ), And a tank forming member 753.
- the tank forming member 753 is fixed to the header plate 751 and the intermediate plate member 752 to form the above-described cooling liquid space 76 and refrigerant space 77 therein. Specifically, the tank forming member 753 is formed in a double mountain shape (W shape) when viewed from the longitudinal direction by pressing a flat metal.
- W shape double mountain shape
- FIG. 9 is a cross-sectional view of the header tank 75 disposed on one end side in the longitudinal direction of the refrigerant tube 16a and the coolant tube 43a (the lower side in FIG. 4). Since the configuration of the header tank 75 disposed on the other end side in the longitudinal direction (the upper side in FIG. 4) of the refrigerant tube 16a and the coolant tube 43a is the same as that in FIG. 9, the illustration is omitted.
- FIG. 9A shows a cross section in which the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72 overlap in the flow direction X of the outside air.
- FIG. 9B shows a cross section in which the coolant tube 43a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72 overlap in the flow direction X of the outside air.
- the intermediate plate member 752 is disposed in the header tank 75 so as to close the coolant space 76 and the coolant space 77 from the coolant tube 16a and coolant tube 43a side.
- the intermediate plate member 752 has the refrigerant tubes 16a of the upstream heat exchange section 71 and the refrigerant tubes.
- An upstream refrigerant communication path 752a (first fluid communication path) that communicates with the space 77, and a downstream refrigerant communication path 752b (first fluid communication) that communicates the refrigerant tube 16a of the downstream heat exchange section 72 and the refrigerant space 77. 1 fluid communication passage) is formed.
- an upstream refrigerant tube group 16b (upstream first tube group) constituted by a plurality of refrigerant tubes 16a of the upstream heat exchange section 71 and a plurality of downstream heat exchange sections 72 are provided.
- the number of stacked refrigerant tubes 16a constituting the upstream refrigerant tube group 16b is , Less than the downstream refrigerant tube group 16c.
- the pressure loss of the refrigerant flowing through the upstream refrigerant tube group 16b is reduced to the downstream refrigerant tube group. Greater than 16c.
- the upstream refrigerant tube group 16b and the downstream refrigerant tube group 16c the one in which the refrigerant pressure loss increases is called a high pressure loss refrigerant tube group (high pressure loss side first tube group), and If the one where the pressure loss of the refrigerant is reduced is called a low pressure loss side refrigerant tube group (low pressure loss side first tube group), the upstream refrigerant tube group 16b corresponds to the high pressure loss side refrigerant tube group, The downstream refrigerant tube group 16c corresponds to the low pressure loss refrigerant tube group.
- the upstream refrigerant tube group 16b is on the high pressure loss side with respect to the downstream refrigerant tube group 16c, and the number of stacked refrigerant tubes 16a constituting the upstream refrigerant tube group 16b. This is because there is less than the downstream refrigerant tube group 16c. Therefore, the upstream side refrigerant tube group 16b may be referred to as a small number of refrigerant side tube group (low number of laminated side first tube group) on the side where the number of laminated refrigerant tubes 16a is small.
- the downstream refrigerant tube group 16c may be referred to as a multi-stack number side refrigerant tube group (multi-stack number side first tube group) on the side where the number of refrigerant tubes 16a is large.
- each of the refrigerant tube groups 16b and 16c is formed by arranging the refrigerant tubes 16a in one row, and may be called a refrigerant tube row (first tube row).
- the upstream heat exchange unit 71 has a larger temperature difference between the refrigerant and the air than the downstream heat exchange unit 72, and the vaporization of the refrigerant is promoted. Therefore, the pressure loss of the refrigerant increases when viewed from the individual refrigerant tubes 16a.
- the difference in the refrigerant flow area affects the pressure loss of the refrigerant much more than the difference in the state of the refrigerant flowing in the refrigerant tube 16a.
- the upstream heat exchange unit 71 has a refrigerant and air ratio compared to the downstream heat exchange unit 72. Since the temperature difference increases and vaporization of the refrigerant is promoted, the pressure loss increases. Therefore, in this case, the refrigerant tube 16a of the upstream heat exchange section 71 can be expressed as a high pressure loss side first tube, and the refrigerant tube 16a of the downstream heat exchange section 72 is expressed as a low pressure loss side first tube. can do. Further, the upstream side refrigerant communication path 752a can be expressed as a high pressure loss side communication path, and the downstream side refrigerant communication path 752b can be expressed as a low pressure loss side communication path.
- the upstream refrigerant communication path 752a is formed linearly between the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant space 77.
- the upstream side refrigerant communication passage 752a is formed in an oblique linear shape with respect to the thickness direction of the intermediate plate member 752 (the vertical direction in FIG. 9A).
- the downstream refrigerant communication passage 752b is formed in a shape that bends between the refrigerant tube 16a of the downstream heat exchange section 72 and the refrigerant space 77. Therefore, the flow resistance of the upstream refrigerant communication passage 752a is smaller than the flow resistance of the downstream refrigerant communication passage 752b.
- the intermediate plate member 752 has the cooling of the upstream heat exchange unit 71.
- the coolant communication path 752c (second fluid communication path) that connects the liquid tube 43a and the refrigerant space 77, and the refrigerant communication that connects the refrigerant tube 16a of the downstream heat exchange section 72 and the refrigerant space 77.
- a passage 752d is formed.
- the intermediate plate member 752 is close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16 a and the coolant tube 43 a (upper side in FIG. 9).
- the three plate members of the first plate member 801, the second plate member 802, and the third plate member 803 are stacked toward the side (the lower side in FIG. 9).
- the first plate member 801 has two through holes 801a and 801b penetrating the front and back, and the second plate member 802 has one through hole 802a penetrating the front and back.
- the third plate member 803 is formed with one through hole 803a penetrating the front and back surfaces thereof.
- one through hole 801 a communicates with the refrigerant tube 16 a of the upstream heat exchange unit 71, and the other through hole 801 b communicates with the downstream heat exchange unit 72. It communicates with the refrigerant tube 16a.
- the through hole 802a of the second plate member 802 communicates with both of the two through holes 801a and 801b of the first plate member 801.
- the through hole 803a of the third plate member 803 communicates with the through hole 802a of the second plate member 802, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication passage 752a is configured by one through hole 801a of the first plate member 801 and the through holes 802a and 803a of the second and third plate members 802 and 803, and the other of the first plate member 801
- the downstream side refrigerant communication passage 752b is configured by the through hole 801b and the through holes 802a and 803a of the second and third plate members 802 and 803.
- the first plate member 801 has two through holes 801c and 801d penetrating the front and back
- the second plate member 802 has two through holes 802c penetrating the front and back
- 802d is formed
- the third plate member 803 is formed with two through holes 803c and 803d penetrating the front and back.
- one through hole 801c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 801d is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- one through hole 802c communicates with one through hole 801c of the first plate member 801, and the other through hole 802d is the other of the first plate member 801.
- the through-hole 801d is communicated with.
- one through hole 803c communicates with one through hole 802c of the second plate member 802 and the cooling liquid space 76, and the other through hole 803d is the first through hole 803d.
- the other plate member 802 communicates with the other through hole 802 d and the refrigerant space 77.
- the through-holes 801c, 802c, 803c of the first to third plate members 801-803 form the upstream side coolant communication path 752c, and the through holes 801d, 802d, 803d of the first to third plate members 801-803 are formed.
- the downstream side refrigerant communication passage 752d is configured.
- the cooling tank 43a is provided with cooling on one end side in the longitudinal direction (right side in FIG. 4) of the upstream tank portion 73 disposed on one end side in the longitudinal direction (lower side in FIG. 4).
- a cooling liquid inflow pipe 434 through which the cooling liquid flows into the liquid space 76 is connected.
- the other end in the longitudinal direction (left side in FIG. 4) of the upstream tank portion 73 disposed on one end in the longitudinal direction of the coolant tube 43a is closed by a closing member.
- the coolant flows out from the coolant space 76 to one end in the longitudinal direction (right side in FIG. 4) of the upstream tank portion 73 disposed on the other longitudinal end of the coolant tube 43a (upper side in FIG. 4).
- a coolant outflow pipe 435 is connected.
- the other end in the longitudinal direction (left side in FIG. 4) of the upstream tank portion 73 disposed on the other end in the longitudinal direction of the coolant tube 43a is closed by a closing member.
- the refrigerant is caused to flow into the refrigerant space 77 on one end side in the longitudinal direction (right side in FIG. 4) of the downstream tank portion 74 disposed on one end side in the longitudinal direction of the refrigerant tube 16a (lower side in FIG. 4).
- a refrigerant inflow pipe 164 is connected.
- the other end in the longitudinal direction (left side in FIG. 4) of the downstream tank portion 74 disposed on one end in the longitudinal direction of the refrigerant tube 16a is closed by a closing member.
- Refrigerant outflow that causes the refrigerant to flow out of the refrigerant space 77 on one end side in the longitudinal direction (right side in FIG. 4) of the downstream tank portion 74 disposed on the other longitudinal end side (upper side in FIG. 4) of the refrigerant tube 16a.
- a pipe 165 is connected.
- the other end in the longitudinal direction (left side in FIG. 4) of the downstream tank portion 74 disposed on the other end in the longitudinal direction of the refrigerant tube 16a is closed by a closing member.
- the upstream tank portion 73 disposed on one end side in the longitudinal direction of the coolant tube 43a (lower side in FIG. 4) is referred to as a first upstream tank portion 730a, and the other end side in the longitudinal direction of the coolant tube 43a.
- the upstream tank portion 73 disposed on (the upper side in FIG. 4) is referred to as a second upstream tank portion 730b.
- downstream tank portion 74 disposed on one end side in the longitudinal direction of the refrigerant tube 16a (lower side in FIG. 4) is referred to as a first downstream tank portion 740a, and the other end side in the longitudinal direction of the refrigerant tube 16a (see FIG. 4) is referred to as a second downstream tank portion 740b.
- the refrigerant that has flowed into the refrigerant space 77 of the first downstream tank portion 740 a via the refrigerant inflow pipe 164 flows into the refrigerant tube 16a of the downstream heat exchange section 72 via the refrigerant communication passages 752b and 752d formed in the intermediate plate member 752, and the refrigerant tube 16a is moved upward from the lower side in FIG. It flows toward.
- the refrigerant that has flowed out of the refrigerant tube 16a of the downstream heat exchange section 72 gathers in the refrigerant space 77 of the second downstream tank section 740b via the refrigerant communication paths 752b and 752d formed in the intermediate plate member 752.
- the refrigerant that has flowed out of the refrigerant tube 16a of the upstream heat exchange section 71 is collected in the refrigerant space 77 of the second downstream tank section 740b via the refrigerant communication path 752a formed in the intermediate plate member 752.
- the refrigerant gathered in the refrigerant space 77 of the second downstream side tank portion 740b flows from the left side to the right side in FIG. 6 and flows out from the refrigerant outflow pipe 165.
- the liquid flows into the cooling liquid tube 43a of the upstream heat exchange section 71 via the cooling liquid communication path 752c formed in the intermediate plate member 752, and the inside of the cooling liquid tube 43a from the lower side of FIG. Flows upward.
- the coolant that has flowed out of the coolant tube 43a of the upstream heat exchange section 71 enters the coolant space 76 of the second upstream tank section 730b via the coolant communication path 752c formed in the intermediate plate member 752. Gather.
- the coolant gathered in the coolant space 76 of the second upstream tank portion 730b flows from the left side to the right side in FIG. 6 and flows out from the coolant outlet pipe 435.
- the outdoor heat exchange unit 16 is configured by both the refrigerant tube 16a of the upstream heat exchange unit 71 and the refrigerant tube 16a of the downstream heat exchange unit 72, and the upstream heat exchange unit.
- the radiator portion 43 is constituted by the 71 coolant tube 43a.
- each of the refrigerant tube 16a, the coolant tube 43a, the header tank 75, and the outer fin 50 of the heat exchanger 70 described above are formed of the same metal material (in this embodiment, an aluminum alloy). Has been.
- the header plate 751 and the tank forming member 753 are fixed by caulking with the intermediate plate member 752 sandwiched therebetween.
- the entire heat exchanger 70 in the caulking and fixing state is put into a heating furnace and heated, the brazing material clad in advance on the surface of each component is melted, and further cooled until the brazing material is solidified again.
- the components are brazed together.
- the outdoor heat exchange part 16 and the radiator part 43 are integrated.
- the air conditioning control device is composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, performs various calculations and processing based on an air conditioning control program stored in the ROM, and is connected to the output side.
- the operation of various air conditioning control devices 11, 15a, 15b, 17, 41, 42, etc. is controlled.
- an inside air sensor that detects the temperature inside the vehicle
- an outside air sensor that detects outside air temperature
- a solar radiation sensor that detects the amount of solar radiation in the vehicle interior
- an outlet refrigerant temperature sensor for detecting the refrigerant temperature discharged from the compressor 11
- an outlet refrigerant temperature sensor 51 for detecting the refrigerant temperature Te on the outlet side of the outdoor heat exchanger 16
- an electric motor MG for running.
- Various air conditioning control sensor groups such as a coolant temperature sensor 52 as coolant temperature detecting means for detecting the coolant temperature Tw to be connected are connected.
- the coolant temperature sensor 52 detects the coolant temperature Tw pumped from the coolant pump 41. Of course, the coolant temperature Tw sucked into the coolant pump 41 is detected. Also good.
- an operation panel (not shown) disposed near the instrument panel in front of the passenger compartment is connected to the input side of the air conditioning control device, and operation signals from various air conditioning operation switches provided on the operation panel are input.
- various air conditioning operation switches provided on the operation panel there are provided an operation switch of a vehicle air conditioner, a vehicle interior temperature setting switch for setting the vehicle interior temperature, an operation mode selection switch, and the like.
- control means for controlling the electric motor 11b, the on-off valve 15a and the like of the compressor 11 is integrally configured to control these operations.
- the air conditioning control device the configuration (hardware and software) for controlling the operation of the compressor 11 constitutes the refrigerant discharge capacity control means, and the configuration for controlling the operations of the various devices 15a and 15b constituting the refrigerant flow path switching means.
- the configuration for controlling the operation of the three-way valve 42 constituting the control means and constituting the circuit switching means for the coolant constitutes the coolant circuit control means.
- the air conditioning control device of the present embodiment is configured to determine whether or not frost formation has occurred in the outdoor heat exchange unit 16 based on the detection signal of the above-described air conditioning control sensor group (frosting determination unit). have.
- the frost determination unit of the present embodiment the vehicle speed of the vehicle is a predetermined reference vehicle speed (20 km / h in the present embodiment) or less, and the outdoor heat exchanger 16 outlet side refrigerant temperature is When Te is 0 ° C. or lower, it is determined that frost formation has occurred in the outdoor heat exchanger 16.
- the operation of the vehicle air conditioner 1 of the present embodiment having the above configuration will be described.
- a heating operation for heating the vehicle interior and a cooling operation for cooling the vehicle interior can be performed, and a defrosting operation can be performed during the heating operation.
- the operation in each operation will be described below.
- Heating operation is started when the heating operation mode is selected by the selection switch while the operation switch of the operation panel is turned on. Then, during the heating operation, the defrosting operation is performed when it is determined by the frost determination unit that the outdoor heat exchange unit 16 has formed frost.
- the air conditioning controller closes the on-off valve 15a and switches the three-way valve 15b to a refrigerant flow path that connects the outlet side of the outdoor heat exchanger 16 and the inlet side of the accumulator 18,
- the coolant pump 41 is operated so as to pump a coolant having a predetermined flow rate, and the three-way valve 42 of the coolant circulation circuit 40 is switched to a coolant circuit in which the coolant flows around the radiator 43.
- the heat pump cycle 10 is switched to the refrigerant flow path through which the refrigerant flows as shown by the solid line arrows in FIG. 1, and the cooling liquid circulation circuit 40 is the cooling liquid circuit through which the cooling liquid flows as shown by the broken line arrows in FIG. Can be switched to.
- the air conditioning control device reads the detection signal of the air conditioning control sensor group and the operation signal of the operation panel with the configuration of the refrigerant flow path and the coolant circuit. And the target blowing temperature TAO which is the target temperature of the air which blows off into a vehicle interior is calculated based on the value of a detection signal and an operation signal.
- the operating state of various air conditioning control devices connected to the output side of the air conditioning control device is determined.
- the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11 is determined as follows. First, based on the target blowing temperature TAO, the target evaporator blowing temperature TEO of the indoor evaporator 20 is determined with reference to a control map stored in advance in the air conditioning control device.
- the blowing air temperature from the indoor evaporator 20 is changed using a feedback control method.
- a control signal output to the electric motor of the compressor 11 is determined so as to approach the target evaporator outlet temperature TEO.
- the target blowing temperature TAO For the control signal output to the servo motor of the air mix door 34, the target blowing temperature TAO, the blowing air temperature from the indoor evaporator 20, the discharge refrigerant temperature detected by the compressor 11 detected by the discharge refrigerant temperature sensor, and the like are used.
- the temperature of the air blown into the passenger compartment is determined so as to be a desired temperature for the passenger set by the passenger compartment temperature setting switch.
- the opening degree of the air mix door 34 may be controlled so that the total air volume of the vehicle interior air blown from the blower 32 passes through the indoor condenser 12. .
- control signals determined as described above are output to various air conditioning control devices. After that, until the operation of the vehicle air conditioner is requested by the operation panel, the above detection signal and operation signal are read at every predetermined control cycle ⁇ the target blowout temperature TAO is calculated ⁇ the operating states of various air conditioning control devices are determined -> Control routines such as control voltage and control signal output are repeated.
- the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12.
- the refrigerant that has flowed into the indoor condenser 12 exchanges heat with the vehicle interior blown air that has been blown from the blower 32 and passed through the indoor evaporator 20 to dissipate heat. Thereby, vehicle interior blowing air is heated.
- the high-pressure refrigerant flowing out of the indoor condenser 12 flows into the heating fixed throttle 13 and is decompressed and expanded because the on-off valve 15a is closed.
- the low-pressure refrigerant decompressed and expanded by the heating fixed throttle 13 flows into the outdoor heat exchange unit 16.
- the low-pressure refrigerant flowing into the outdoor heat exchange unit 16 absorbs heat from the outside air blown by the blower fan 17 and evaporates.
- the coolant circulation circuit 40 the coolant is switched to the coolant circuit that flows around the radiator 43, so that the coolant dissipates heat to the refrigerant circulating in the outdoor heat exchange unit 16,
- the liquid does not absorb heat from the refrigerant flowing through the outdoor heat exchange unit 16. That is, the cooling liquid does not thermally affect the refrigerant flowing through the outdoor heat exchange unit 16.
- the refrigerant flowing out of the outdoor heat exchange section 16 flows into the accumulator 18 because the three-way valve 15b is switched to the refrigerant flow path connecting the outlet side of the outdoor heat exchange section 16 and the inlet side of the accumulator 18. Gas-liquid separation. The gas-phase refrigerant separated by the accumulator 18 is sucked into the compressor 11 and compressed again.
- the vehicle interior air can be heated by the amount of heat of the refrigerant discharged from the compressor 11 by the indoor condenser 12 to heat the vehicle interior.
- the defrosting operation is executed when it is determined by the frosting determination means that frost formation has occurred in the outdoor heat exchange unit 16 during the heating operation.
- the air conditioning control device stops the operation of the compressor 11 and stops the operation of the blower fan 17. Accordingly, during the defrosting operation, the flow rate of the refrigerant flowing into the outdoor heat exchange unit 16 is reduced and the air volume of the outside air flowing into the outdoor air passage 70a is reduced as compared with the normal heating operation.
- the air-conditioning control device switches the three-way valve 42 of the coolant circulation circuit 40 to a coolant circuit that allows the coolant to flow into the radiator section 43 as indicated by the broken line arrows in FIG.
- the coolant circulation circuit 40 is switched to the coolant circuit through which the refrigerant flows as shown by the broken line arrows in FIG.
- the heat quantity of the coolant flowing through the coolant tube 43a of the radiator section 43 is transferred to the outdoor heat exchange section 16 through the outer fin 50, and the outdoor heat exchange section 16 is defrosted. That is, defrosting that effectively uses the waste heat of the traveling electric motor MG is realized.
- Air-cooling operation is started when the air-cooling operation mode is selected by the selection switch while the operation switch of the operation panel is turned on.
- the air conditioning control device opens the on-off valve 15a and switches the three-way valve 15b to a refrigerant flow path that connects the outlet side of the outdoor heat exchanger 16 and the inlet side of the cooling fixed throttle 19.
- the heat pump cycle 10 is switched to the refrigerant
- the coolant when the coolant temperature Tw becomes equal to or higher than the reference temperature, the coolant is switched to a coolant circuit that allows the coolant to flow into the radiator unit 43.
- the coolant is switched to a coolant circuit that flows around the radiator 43.
- the flow of the coolant when the coolant temperature Tw is equal to or higher than the reference temperature is indicated by a broken line arrow.
- the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12 and exchanges heat with the vehicle interior blown air that is blown from the blower 32 and passes through the indoor evaporator 20. Dissipate heat.
- the high-pressure refrigerant that has flowed out of the indoor condenser 12 flows into the outdoor heat exchanger 16 through the fixed throttle bypass passage 14 because the on-off valve 15a is open.
- the high-pressure refrigerant that has flowed into the outdoor heat exchange unit 16 further dissipates heat to the outside air blown by the blower fan 17.
- the refrigerant flowing out of the outdoor heat exchange unit 16 is switched to the refrigerant flow path where the three-way valve 15b is connected to the outlet side of the outdoor heat exchange unit 16 and the inlet side of the cooling fixed throttle 19, so that the cooling fixed
- the diaphragm 19 is expanded under reduced pressure.
- the refrigerant that has flowed out of the cooling fixed throttle 19 flows into the indoor evaporator 20, absorbs heat from the vehicle interior air blown by the blower 32, and evaporates. Thereby, vehicle interior blowing air is cooled.
- the refrigerant that has flowed out of the indoor evaporator 20 flows into the accumulator 18 and is separated into gas and liquid.
- the gas-phase refrigerant separated by the accumulator 18 is sucked into the compressor 11 and compressed again.
- the low-pressure refrigerant absorbs heat from the vehicle interior blown air and evaporates in the room evaporator 20, thereby cooling the vehicle interior blown air and cooling the vehicle interior.
- various operations can be performed by switching the refrigerant flow path of the heat pump cycle 10 and the coolant circuit of the coolant circulation circuit 40 as described above. Furthermore, in this embodiment, since the characteristic heat exchanger 70 mentioned above is employ
- a certain upstream number ratio is smaller than the downstream number ratio, which is the ratio of the number of tubes occupied by the refrigerant tubes 16a of the downstream heat exchange section 72 with respect to the total number of tubes constituting the downstream heat exchange section 72. ing.
- the upstream heat exchanging portion 71 is configured by alternately arranging the refrigerant tubes 16a and the coolant tubes 43a.
- the defrosting is performed by circulating the coolant having a temperature higher than that of the refrigerant through the coolant tube 43a and the coolant space 76.
- the coolant that functions as a heat source for performing defrosting flows more preferentially to the upstream side of the heat exchanger 70 in the flow direction X of the outside air that is easily frosted than the downstream side.
- frost formation can be further suppressed, and efficient heat exchange can be realized.
- the waste heat of the traveling electric motor MG is used to defrost the refrigerant tube 16a. It can be used effectively.
- the downstream side heat exchanging portion 72 is constituted only by the refrigerant tube 16a. For this reason, in the downstream heat exchange section 72, a sufficient amount of heat exchange between the refrigerant and the outside air can be ensured. Therefore, the heat exchanger 70 as a whole can appropriately secure the heat exchange amount between the refrigerant and the outside air.
- the outer fin 50 is arrange
- the outer fin 50 enables heat transfer between the refrigerant tube 16a and the coolant tube 43a.
- the amount of heat of the coolant can be reliably transferred through the refrigerant tube 16a through the outer fin 50, so that the waste heat of the travel electric motor MG is removed from the refrigerant tube 16a. Because of the frost, it can be used more effectively.
- the flow resistance of the upstream refrigerant communication passage 752a is smaller than the flow resistance of the downstream refrigerant communication passage 752b. It is possible to appropriately adjust the refrigerant distribution with respect to the refrigerant tube 16a of the section 71 and the refrigerant tube 16a of the downstream heat exchange section 72.
- the upstream side heat exchange unit 71 is more refrigerant than the downstream side heat exchange unit 72. Since the temperature difference between the air and the air increases and the vaporization of the refrigerant is promoted, the pressure loss increases. Therefore, the refrigerant tube 16a of the upstream heat exchange section 71 is less likely to distribute the refrigerant than the refrigerant tube 16a of the downstream heat exchange section 72.
- the first tube 16a of the upstream heat exchange section 71 is made by making the flow resistance of the upstream refrigerant communication passage 752a smaller than the flow resistance of the downstream refrigerant communication passage 752b. Since the flow path resistance between the refrigerant space 77 and the refrigerant space 77 is smaller than the flow path resistance between the first tube 16a of the downstream heat exchange section 72 and the refrigerant space 77, the upstream side where the pressure loss is large. It becomes easy for the refrigerant to flow into the refrigerant tube 16a of the heat exchanging portion 71, and as a result, the distribution of the refrigerant can be adjusted appropriately.
- the flow path resistance between the upstream refrigerant tube group 16b and one refrigerant space 77 is the downstream refrigerant tube group 16c and its one.
- the flow path resistance between the two refrigerant spaces 77 is smaller. That is, the flow resistance in the entire plurality of upstream refrigerant communication passages 752a connecting the upstream refrigerant tube group 16b and the one refrigerant space 77 is equal to the downstream refrigerant tube group 16c and the one refrigerant space.
- the flow resistance of the plurality of downstream side refrigerant communication passages 752b and 752d connecting to 77 is smaller.
- the distribution of the refrigerant to the refrigerant tube 16a of the upstream heat exchange unit 71 and the refrigerant tube 16a of the downstream heat exchange unit 72 can be adjusted more appropriately.
- the downstream refrigerant communication path 752d has a small flow path cross-sectional area due to a narrow width in the tube stacking direction (the depth direction in FIG. 9), and the flow resistance of the downstream refrigerant communication path 752d becomes the upstream refrigerant communication. It is larger than the passage 752a.
- the refrigerant in the refrigerant flow path between the refrigerant space 77 and the refrigerant tube 16a, the refrigerant can flow more easily to the upstream refrigerant tube group 16b than to the downstream refrigerant tube group 16c. It is possible to suppress the occurrence of bias, and thus the amount of heat exchange between the three types of fluids can be adjusted appropriately.
- the refrigerant as the first fluid and the coolant as the second fluid are heat media that circulate in different fluid circulation circuits, and the heat exchanger 70 is shared by the plurality of fluid circulation circuits 10 and 40. Yes. Therefore, it is easy to reduce the installation space for the heat exchanger 70 as compared to the case where a heat exchanger is provided for each fluid circulation circuit.
- the upstream refrigerant tube group 16b corresponds to the above-described high pressure loss side refrigerant tube group
- the downstream refrigerant tube group 16c corresponds to the above-described low pressure loss side refrigerant tube group.
- the number of refrigerant tubes 16a (the number of stacked layers) included in the upstream refrigerant tube group 16b is smaller than that of the downstream refrigerant tube group 16c. Accordingly, since the temperature difference between the outside air and the refrigerant is likely to be larger in the upstream heat exchange unit 71 than in the downstream heat exchange unit 72, the heat exchange amount in the upstream heat exchange unit 71 and the downstream heat exchange unit The heat exchange amount at 72 is appropriately adjusted.
- the upstream side refrigerant communication path 752a is formed linearly as compared with the downstream side refrigerant communication path 752b, thereby reducing the flow resistance of the upstream side refrigerant communication path 752a to the downstream side refrigerant communication path 752b.
- the flow area of the upstream refrigerant communication path 752a is larger than the flow area of the downstream refrigerant communication path 752b.
- the flow resistance of the upstream refrigerant communication passage 752a is made smaller than the flow resistance of the downstream refrigerant communication passage 752b.
- the flow area of the entire plurality of upstream refrigerant communication paths 752a is larger than the flow area of the plurality of downstream refrigerant communication paths 752b and 752d, thereby
- the channel resistance in the entire side refrigerant communication passage 752a is made smaller than the channel resistance in the entire downstream side refrigerant communication passages 752b and 752d.
- FIG. 10 (a) is a diagram corresponding to FIG. 9 (a)
- FIG. 10 (b) is a diagram corresponding to FIG. 9 (b).
- FIG. 10 the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (upper side in FIG. 10) (FIG. 10).
- 3 plate members of a first plate member 811, a second plate member 812, and a third plate member 813 are stacked.
- the first plate member 811 has two through holes 811a and 811b
- the second plate member 812 has two through holes 812a and 812b
- the third plate member 813 has One through hole 813a is formed.
- one through hole 811 a communicates with the refrigerant tube 16 a of the upstream heat exchange unit 71, and the other through hole 811 b communicates with the downstream heat exchange unit 72. It communicates with the refrigerant tube 16a.
- one through hole 812 a communicates with one through hole 811 a of the first plate member 811
- the other through hole 812 b is the other of the first plate member 811. It communicates with the through hole 811b.
- the hole area of one through hole 812a of the second plate member 812 is larger than the hole area of the other through hole 812b of the second plate member 812.
- the through hole 813a of the third plate member 813 communicates with both of the two through holes 812a and 812b of the second plate member 812, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication path 752a is configured by the one through hole 811a of the first plate member 811, the one through hole 812a of the second plate member 812, and the through hole 813a of the third plate member 813, and the first plate
- the other through-hole 811b of the member 811, the other through-hole 812b of the second plate member 812, and the through-hole 813a of the third plate member 813 constitute the downstream side refrigerant communication passage 752b.
- the flow resistance of the upstream side refrigerant communication path 752a is smaller than the flow path resistance of the downstream refrigerant communication path 752b.
- the first plate member 811 has two through holes 811c and 811d
- the second plate member 812 has two through holes. Holes 812c and 812d are formed, and two through holes 813c and 813d are formed in the third plate member 813.
- one through hole 811c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 811d is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- one through hole 812c communicates with one through hole 811c of the first plate member 811 and the other through hole 812d is the other of the first plate member 811.
- the through-hole 811d is communicated with.
- one through hole 813c communicates with one through hole 812c of the second plate member 812 and the cooling liquid space 76, and the other through hole 813d has the first through hole 813d.
- the other plate member 812 communicates with the other through hole 812 d and the refrigerant space 77.
- the through-holes 811c, 812c and 813c of the first to third plate members 811 to 813 constitute the upstream coolant communication path 752c, and the through-holes 811d, 812d and 813d of the first to third plate members 811 to 813 are formed.
- the downstream side refrigerant communication passage 752d is configured.
- the flow resistance of the upstream refrigerant communication path 752a is made larger than the flow resistance of the downstream refrigerant communication path 752b. May be made smaller.
- the flow resistance of the upstream refrigerant communication path 752a is reduced to the flow of the downstream refrigerant communication path 752b. It may be smaller than the road resistance.
- the flow resistance of the upstream refrigerant communication passage 752a is made smaller than the flow resistance of the downstream refrigerant communication passage 752b, so that the first tube 16a of the upstream heat exchange section 71 and Although the flow path resistance between the refrigerant space 77 is smaller than the flow path resistance between the first tube 16a of the downstream heat exchange section 72 and the refrigerant space 77, in the third embodiment, as shown in FIG. 11, the first tube 16a and the refrigerant of the upstream heat exchange section 71 are made by reversing the arrangement of the cooling liquid space 76 and the refrigerant space 77 with respect to the first and second embodiments. The flow path resistance between the first and second spaces 77 is made smaller than the flow path resistance between the first tube 16 a of the downstream heat exchange section 72 and the refrigerant space 77.
- the arrangement of the cooling liquid space 76 and the refrigerant space 77 is reversed with respect to the first and second embodiments, whereby the upstream refrigerant refrigerant is used.
- the flow path resistance between the tube group 16 b and the refrigerant space 77 is made smaller than the flow path resistance between the downstream refrigerant tube group 16 c and the refrigerant space 77.
- the refrigerant space 77 is arranged on the upstream side (the left side in FIG. 11) in the outside air flow direction X with respect to the coolant space 76.
- the refrigerant space 77 is arranged on the side closer to the refrigerant tube 16a of the upstream heat exchange section 71 than the cooling liquid space 76 in the flow direction X of the outside air, and the cooling liquid space 76 is arranged in the flow direction of the outside air.
- the refrigerant is disposed on the side closer to the refrigerant tube 16a in the heat exchange section 72 on the downstream side than the refrigerant space 77.
- FIG. 11A shows a cross section of a portion where the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72 overlap in the flow direction X of the outside air.
- FIG. 11B shows a cross section in which the coolant tube 43a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72 overlap in the flow direction X of the outside air.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (upper side in FIG. 11) (FIG. 11).
- the four plate members of the first plate member 821, the second plate member 822, the third plate member 823, and the fourth plate member 824 are stacked.
- the first plate member 821 has two through holes 821a and 821b, the second plate member 822 has one through hole 822a, and the third plate member 823 has one hole.
- a through hole 823 a is formed, and one through hole 824 a is formed in the fourth plate member 824.
- one through hole 821a communicates with the refrigerant tube 16a of the upstream heat exchange section 71, and the other through hole 821b communicates with the downstream heat exchange section 72. It communicates with the refrigerant tube 16a.
- the through hole 822a of the second plate member 822 communicates with both of the two through holes 821a and 821b of the first plate member 821.
- the through hole 823a of the third plate member 823 communicates with the through hole 822a of the second plate member 822.
- the through hole 824a of the fourth plate member 824 communicates with the through hole 823a of the third plate member 823, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication path 752a is configured by the one through hole 821a of the first plate member 821 and the through holes 822a, 823a, and 824a of the second to fourth plate members 822 to 824, and the first plate member 821
- the other side through hole 821b and the through holes 822a, 823a, and 824a of the second to fourth plate members 822 to 824 constitute the downstream side refrigerant communication path 752b.
- the first plate member 821 has two through holes 821c and 821b
- the second plate member 822 has one through hole 822c
- the third plate member 823 has one through hole.
- a through hole 823 c is formed, and one through hole 824 c is formed in the fourth plate member 824.
- one through hole 821c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 821b is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- the other through-hole 821b is the same as the above-described through-hole 821b in FIG. 11A, and is formed to extend in the tube stacking direction as shown in FIG.
- the through hole 822c of the second plate member 822 communicates with one through hole 821c of the first plate member 821.
- the through hole 823c of the third plate member 823 communicates with the through hole 822c of the second plate member 822.
- the through hole 824c of the fourth plate member 824 communicates with the through hole 823c of the third plate member 823, and further communicates with the coolant space 76.
- the upstream side coolant communication path 752c is constituted by the through holes 821c, 822c, 823c, and 824c of the first to fourth plate members 821 to 824, and the through hole 821b of the first plate member 821 and FIG.
- the intermediate plate member 752 is formed by stacking four plate members 821 to 824.
- two intermediate plate members 752 are provided.
- the plate members 831 and 832 are stacked.
- FIG. 13 (a) is a diagram corresponding to FIG. 11 (a)
- FIG. 13 (b) is a diagram corresponding to FIG. 11 (b).
- the intermediate plate member 752 includes a first plate member 831 on the side closer to the refrigerant tube 16a and the cooling liquid tube 43a (upper side in FIG. 13), a cooling liquid space 76, and a refrigerant space. And a second plate member 832 on the side close to 77 (the lower side in FIG. 13).
- the first plate member 831 has one through-hole 831a
- the second plate member 832 has one through-hole 832a.
- the through hole 831a of the first plate member 831 communicates with both the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72.
- the through hole 832 a of the second plate member 832 communicates with the through hole 831 a of the first plate member 831 and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication passage 752a and the downstream side refrigerant communication passage 752b are configured by the through hole 831a of the first plate member 831 and the through hole 832a of the second plate member 832.
- the first plate member 831 has two through holes 831c and 831a, and the second plate member 832 has one through hole 832c.
- one through hole 831 c communicates with the coolant tube 43 a of the upstream heat exchange unit 71, and the other through hole 831 a is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- the other through-hole 831a is the same as the above-described through-hole 831a in FIG. 13A, and the portion of the through-hole 813a on the downstream side in the outside air flow direction X extends in the tube stacking direction as shown in FIG. Is formed.
- the through hole 832c of the second plate member 832 extends obliquely with respect to the thickness direction of the second plate member 832 so that the one through hole 831c of the first plate member 821 communicates with the cooling liquid space 76. Is formed.
- the through-holes 831c and 832c of the first and second plate members 831 and 832 constitute an upstream side coolant communication path 752c, and the through-hole 831a of the first plate member 831 and the second plate shown in FIG.
- the downstream side refrigerant communication path 752d is configured by the through hole 832a of the member 832.
- the intermediate plate member 752 is configured by laminating two plate members 831 and 832.
- three intermediate plate members 752 are provided.
- the plate members 841, 842, and 843 are stacked.
- FIG. 15 (a) is a diagram corresponding to FIG. 13 (a), and FIG. 15 (b) is a diagram corresponding to FIG. 13 (b).
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (upper side in FIG. 15) (FIG. 15).
- 3 plate members of a first plate member 841, a second plate member 842, and a third plate member 843 are stacked.
- the first plate member 841 has one through hole 841a
- the second plate member 842 has one through hole 842a
- the third plate member 843 has one through hole. 843a is formed.
- the through hole 841a of the first plate member 841 communicates with both the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72.
- the through hole 842a of the second plate member 842 communicates with the through hole 841a of the first plate member 841.
- the through hole 843 a of the third plate member 843 communicates with the through hole 842 a of the second plate member 842, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication passage 752a and the downstream side refrigerant communication passage 752b are configured by the through hole 841a of the first plate member 841, the through hole 842a of the second plate member 842, and the through hole 843a of the third plate member 843.
- the Rukoto is configured by the through hole 841a of the first plate member 841, the through hole 842a of the second plate member 842, and the through hole 843a of the third plate member 843.
- the first plate member 841 has two through holes 841c and 841a
- the second plate member 842 has one through hole 842c
- the third plate member 843 has one through hole.
- a through hole 843c is formed.
- one through hole 841c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 841a is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- the other through-hole 841a is the same as the above-described through-hole 841a in FIG. 15A, and the portion of the through-hole 841a on the downstream side in the outside air flow direction X is the same as the through-hole 831a shown in FIG. Is formed extending in the tube stacking direction.
- the through hole 842c of the second plate member 842 communicates with one through hole 841c of the first plate member 841.
- the through hole 843c of the third plate member 843 communicates with one through hole 842c of the second plate member 842, and further communicates with the coolant space 76.
- the upstream side coolant communication passage 752c is constituted by the through holes 841c, 842c, 843c of the first to third plate members 841 to 843, and the through holes 841a of the first plate member 841 and the first holes shown in FIG. 2.
- the downstream side refrigerant communication passage 752d is configured by the through holes 842a and 843a of the third plate members 842 and 843.
- the refrigerant space 77 is more external than the cooling liquid space 76 on one end side in the longitudinal direction of the refrigerant tube 16 a and the coolant tube 43 a (lower side in FIG. 16).
- the refrigerant space 77 is arranged on the upstream side in the flow direction X of the refrigerant, and the refrigerant space 77 is flowed in the direction of the outside air from the coolant space 76 at the other longitudinal end of the refrigerant tube 16a and the coolant tube 43a (upper side in FIG. It is arranged downstream of X. In other words, the two refrigerant spaces 77 are diagonally arranged.
- the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72 overlap with each other in the flow direction X of the outside air.
- header tank 75 on the other end side in the longitudinal direction of the refrigerant tube 16a and the coolant tube 43a (the lower side in FIG. 16) will be described.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (the lower side in FIG. 16) (FIG. 16).
- the two plate members of the first plate member 851 and the second plate member 852 are stacked toward the upper side.
- the first plate member 851 has one through-hole 851a
- the second plate member 852 has one through-hole 852a.
- the through hole 851a of the first plate member 851 communicates with both the refrigerant tube 16a of the upstream heat exchange unit 71 and the refrigerant tube 16a of the downstream heat exchange unit 72.
- the through hole 852a of the second plate member 852 communicates with the through hole 851a of the first plate member 851, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication passage 752a and the downstream side refrigerant communication passage 752b are configured by the through hole 851a of the first plate member 851 and the through hole 852a of the second plate member 852.
- the first plate member 851 has two through holes 851c and 851d
- the second plate member 852 has two through holes 852c and 852d.
- one through hole 851c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 851d is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- one through hole 852c communicates with one through hole 851c of the first plate member 851, and further communicates with the cooling liquid space 76, and the other.
- the through hole 852 d communicates with the other through hole 851 d of the first plate member 851 and further communicates with the refrigerant space 77.
- one through hole 851c, 852c of the first and second plate members 851, 852 forms an upstream side coolant communication path 752c, and the other through hole 851d, 852d of the first, second plate members 851, 852.
- the downstream side refrigerant communication passage 752d is configured.
- the refrigerant space 77 is assumed to be equidistant from the refrigerant tube 16 a of the upstream heat exchange unit 71 and the refrigerant tube 16 a of the downstream heat exchange unit 72.
- the distribution of the refrigerant to the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72 is optimized.
- the refrigerant space 77 is formed so that the width dimension in the outside air flow direction X is larger than the coolant space 76.
- the refrigerant space 77 is disposed downstream of the coolant liquid space 76 in the flow direction X of the outside air, and the refrigerant tube 16a and the downstream heat of the upstream heat exchange section 71 in the longitudinal direction of the refrigerant tube 16a. It overlaps with both the refrigerant
- the refrigerant space 77 is arranged at a position overlapping the virtual straight line CL, the refrigerant space 77 does not overlap the virtual straight line CL, and the refrigerant tube 16a and the downstream side of the upstream heat exchanging unit 71 are arranged.
- the refrigerant tube 16a of the upstream heat exchange unit 71 and the refrigerant tube 16a of the downstream heat exchange unit 72 The distribution of the refrigerant with respect to the distribution can be suppressed. For this reason, the refrigerant
- the refrigerant tube 16 a of the upstream heat exchange unit 71 and the refrigerant tube 16 a of the downstream heat exchange unit 72 overlap in the flow direction X of the outside air.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (upper side in FIG. 17) (FIG. 17).
- the two plate members of the first plate member 861 and the second plate member 862 are stacked toward the lower side).
- the first plate member 861 has one through hole 861a
- the second plate member 862 has one through hole 862a.
- the through hole 861a of the first plate member 861 communicates with both the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72.
- the through hole 862a of the second plate member 862 communicates with the through hole 861a of the first plate member 861, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication passage 752a and the downstream side refrigerant communication passage 752b are configured by the through hole 861a of the first plate member 861 and the through hole 862a of the second plate member 862.
- the first plate member 861 has two through holes 861c and 861d
- the second plate member 862 has two through holes 862c and 862d.
- one through hole 861c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 861d is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- one through hole 862c communicates with one through hole 861c of the first plate member 861, and further communicates with the cooling liquid space 76, and the other The through hole 862 d communicates with the other through hole 861 d of the first plate member 861, and further communicates with the refrigerant space 77.
- one through hole 861c, 862c of the first and second plate members 861, 862 forms an upstream side coolant communication path 752c, and the other through hole 861d, 862d of the first, second plate members 861, 862.
- the downstream side refrigerant communication passage 752d is configured.
- the refrigerant space 77 is formed so that the width dimension in the flow direction X of the outside air is larger than the coolant liquid space 76, but in the eighth embodiment, as shown in FIG.
- the refrigerant space 77 is formed to have the same width dimension as the coolant space 76 in the flow direction X of the outside air.
- an empty space S is formed downstream of the refrigerant space 77 in the flow direction X of the outside air.
- This space S can be effectively used as a space for arranging devices such as connectors and modulators.
- FIG. 18A is a diagram corresponding to FIG. 17A
- FIG. 18B is a diagram corresponding to FIG. 17B.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (upper side in FIG. 18) (FIG. 18).
- the two plate members of the first plate member 871 and the second plate member 872 are stacked toward the lower side).
- the first plate member 871 has two through holes 871a and 871b, and the second plate member 872 has one through hole 872a.
- one through hole 871a communicates with the refrigerant tube 16a of the upstream heat exchange section 71, and the other through hole 871b is a refrigerant of the downstream heat exchange section 72.
- the tube 16a communicates.
- the through hole 872a of the second plate member 872 communicates with both of the two through holes 871a and 871b of the first plate member 871, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication path 752a is configured by the one through hole 871a of the first plate member 871 and the through hole 872a of the second plate member 872, and the other through hole 871b of the first plate member 871 and the second plate.
- the downstream side refrigerant communication path 752b is configured by the through hole 872a of the member 872.
- the first plate member 871 has two through holes 871c and 871d
- the second plate member 872 has two through holes 872c and 872d.
- one through hole 871c communicates with the coolant tube 43a of the upstream heat exchange section 71, and the other through hole 871d is the downstream heat exchange section 72. And the refrigerant tube 16a.
- one through hole 872c communicates with one through hole 871c of the first plate member 871, and further communicates with the coolant space 76, and the other
- the through hole 872d communicates with the other through hole 861d of the first plate member 871, and also communicates with the refrigerant space 77.
- the upstream side coolant communication passage 752c is configured by one through hole 871c, 872c of the first and second plate members 871, 872, and the other through hole 871d, 872d of the first, second plate member 871, 872.
- the downstream side refrigerant communication passage 752d is configured.
- a space S vacant on the downstream side in the flow direction X of the outside air from the coolant space 76 is formed.
- This space S can be effectively used as a space for arranging devices such as connectors and modulators.
- FIG. 19A is a diagram corresponding to FIG. 18A
- FIG. 19B is a diagram corresponding to FIG. 18B.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (the upper side in FIG. 19) (FIG. 19).
- the two plate members of the first plate member 881 and the second plate member 882 are laminated toward the lower side).
- the first plate member 881 has one through-hole 881a
- the second plate member 882 has one through-hole 882a.
- the through hole 881a of the first plate member 881 communicates with both the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72.
- the through hole 882a of the second plate member 882 communicates with the through hole 881a of the first plate member 881, and further communicates with the refrigerant space 77.
- the upstream side refrigerant communication path 752a and the downstream side refrigerant communication path 752b are configured by the through hole 881a of the first plate member 881 and the through hole 882a of the second plate member 882.
- the first plate member 881 has two through holes 881c and 881a, and the second plate member 882 has one through hole 882c.
- one through hole 881c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 881a is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- the other through-hole 881a is the same as the above-described through-hole 881a in FIG. 19A, and the through-hole 881a on the downstream side in the outside air flow direction X is the same as the through-hole 831a in FIG. It is formed extending in the tube stacking direction.
- the through hole 882c of the second plate member 882 communicates with one through hole 881c of the first plate member 881, and further communicates with the coolant space 76.
- the upstream side coolant communication path 752c is constituted by the through holes 881c and 882c of the first and second plate members 881 and 882, and the through hole 881a of the first plate member 881 and the second plate shown in FIG.
- the downstream side refrigerant communication path 752d is configured by the through hole 882a of the member 882.
- the second refrigerant space 78 (third tank space) is formed in the region where the space S is formed in the ninth embodiment.
- the tank forming member 753 is formed in a three-sided shape when viewed from the longitudinal direction, and the central portion of the peaks of the tank forming member 753 is joined to the intermediate plate member 752, whereby the first refrigerant A space 77, a coolant space 76, and a second refrigerant space 78 are partitioned.
- the first coolant space 77, the coolant space 76, and the second coolant space 78 are arranged in this order in the flow direction X of the outside air, and the coolant space 76 overlaps the virtual straight line CL. .
- FIG. 20A is a diagram corresponding to FIG. 19A
- FIG. 20B is a diagram corresponding to FIG. 19B.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (the upper side in FIG. 20) (FIG. 20).
- the two plate members of the first plate member 891 and the second plate member 892 are laminated toward the lower side).
- the first plate member 891 has one through hole 891a
- the second plate member 892 has two through holes 892a and 892b.
- the through hole 891a of the first plate member 891 communicates with both the refrigerant tube 16a of the upstream heat exchange section 71 and the refrigerant tube 16a of the downstream heat exchange section 72.
- one through hole 882a communicates with the through hole 891a of the first plate member 891, and also communicates with the first refrigerant space 77. Accordingly, the through-hole 891a of the first plate member 891 and the one through-hole 892a of the second plate member 892 constitute an upstream refrigerant communication path 752a and a downstream refrigerant communication path 752b.
- the other through hole 892b communicates with the through hole 891a of the first plate member 891, and also communicates with the second refrigerant space 78. Accordingly, the second refrigerant space 78 communicates with the downstream refrigerant communication passage 752b through the other through hole 892b of the second plate member 892.
- the first plate member 891 has two through holes 891c and 891d
- the second plate member 892 has two through holes 892c and 892d.
- one through hole 891c communicates with the coolant tube 43a of the upstream heat exchange unit 71, and the other through hole 891d is the downstream heat exchange unit 72. And the refrigerant tube 16a.
- one through hole 892c communicates with one through hole 891c of the first plate member 891, and also communicates with the coolant space 76.
- the other through hole 892d of the second plate member 892 communicates with the other through hole 891d of the first plate member 891, and also communicates with the second refrigerant space 78.
- the upstream side coolant communication path 752c is configured by one through-hole 891c, 892c of the first and second plate members 891, 892, and the other through-hole 891d, 892d of the first, second plate member 891, 892.
- the second refrigerant space 78 constitute a downstream refrigerant communication path 752d.
- the flow path from FIG. 20A to FIG. 20B is configured by the second refrigerant space 78
- the flow path is the same as the ninth embodiment.
- the flow passage area of the flow passage can be increased, and the pressure loss of the refrigerant in the downstream refrigerant communication passage 752d can be reduced.
- the eleventh embodiment In the eleventh embodiment, as shown in FIG. 21, the arrangement of the first refrigerant space 77 and the cooling liquid space 76 is reversed with respect to the tenth embodiment.
- the order of arrangement in the flow direction X of the outside air is the coolant space 76, the first coolant space 77, and the second coolant space 78, and the first coolant space 77 is virtual. It overlaps with the straight line (CL).
- FIG. 21A is a diagram corresponding to FIG. 20A
- FIG. 21B is a diagram corresponding to FIG.
- FIG. 21C shows a cross section in which the connector 92 for connecting the refrigerant pipe is arranged.
- the intermediate plate member 752 has a side close to the coolant space 76 and the coolant space 77 from the side close to the coolant tube 16a and the coolant tube 43a (the upper side in FIG. 21) (FIG. 21).
- the two plate members of the first plate member 901 and the second plate member 902 are laminated toward the lower side).
- the first plate member 901 has two through holes 901a and 901b
- the second plate member 902 has two through holes 902a and 902b.
- one through hole 901 a communicates with the refrigerant tube 16 a of the upstream heat exchange unit 71, and the other through hole 901 a serves as the downstream heat exchange unit 72. It communicates with the refrigerant tube 16a.
- one through hole 902a communicates with one through hole 901a of the first plate member 901 and further communicates with the first refrigerant space 77. Yes.
- the other through hole 902b communicates with the other through hole 901b of the first plate member 901 and further communicates with the second refrigerant space 78. Yes.
- one through hole 901a of the first plate member 901 and one through hole 902a of the second plate member 902 constitute an upstream refrigerant communication path 752a, and the other through hole 901b of the first plate member 901 and the first through hole 901b
- the downstream side refrigerant communication passage 752b is configured by the other through-hole 902b of the two-plate member 902.
- the hole diameter (hole area) of one through hole 902a of the second plate member 902 is smaller than the hole diameter (hole area) of the other through hole 902b of the second plate member 902.
- the first plate member 901 has two through holes 901c and 901d
- the second plate member 902 has two through holes 902c and 902d.
- one through hole 901 c communicates with the coolant tube 43 a of the upstream heat exchange part 71, and the other through hole 901 d is the downstream heat exchange part 72. And the refrigerant tube 16a.
- one through hole 902c communicates with one through hole 901c of the first plate member 901 and further communicates with the coolant space 76.
- the other through hole 902d of the second plate member 902 communicates with the other through hole 901d of the first plate member 901, and further communicates with the second refrigerant space 78.
- one through hole 901c, 902c of the first and second plate members 901, 902 forms an upstream side coolant communication path 752c, and the other through hole 901d, 902d of the first, second plate member 901, 902 is formed.
- the second refrigerant space 78 constitute a downstream refrigerant communication path 752d.
- the three-sided tank forming member 753 has a second plate member 902 (a portion between the first refrigerant space 77 and the second refrigerant space 78). It is separated from the intermediate plate member 752).
- an in-tank communication passage 91 that connects the first refrigerant space 77 and the second refrigerant space 78 is formed between the tank forming member 753 and the second plate member 902 (intermediate plate member 752).
- a connector 92 is attached to the outside of the tank forming member 753. Specifically, the connector 92 is disposed at an external part on the opposite side of the upstream heat exchange unit 71 and the downstream heat exchange unit 72 with respect to the header tank 75. The connector 92 is formed with a connector communication path 922 that connects the internal space 921 to the first refrigerant space 77.
- the refrigerant flow passage from FIG. 21A to FIG. 21B is configured by the second refrigerant space 78 as in the tenth embodiment, so that the downstream refrigerant communication is The pressure loss of the refrigerant in the passage 752d can be reduced.
- the design of the recessed shape of the portion between the first refrigerant space 77 and the second refrigerant space 78 in the tank forming member 753 is changed to increase the width of the in-tank communication passage 91.
- the flow path resistance between the first tube 16a of the downstream heat exchange section 72 and the refrigerant space 77 can be adjusted.
- the flow path resistance between the first tube 16a of the side heat exchange part 72 and the refrigerant space 77 can be adjusted.
- the size (cross-sectional area) of the first and second refrigerant spaces 77 and 78 is changed by changing the design of the shape of the portion forming the first and second refrigerant spaces 77 and 78 in the tank forming member 753.
- the flow path resistance between the first tube 16a of the downstream side heat exchanging portion 72 and the refrigerant space 77 can also be adjusted by changing the above.
- the in-tank communication passage 91 is abolished with respect to the eleventh embodiment, and the connector 92 has an internal space 921 and a second refrigerant space 78.
- a second connector communication path 923 for communication is formed.
- the refrigerant tube 16a and the downstream heat exchange of the upstream heat exchange unit 71 are changed. Since the easiness of the flow of the refrigerant in the refrigerant tube 16a of the portion 72 can be changed, the distribution of the refrigerant can be appropriately adjusted.
- the design of the hole diameter (hole area) of the two through holes 902a and 902b of the second plate member 902 and the size of the first and second refrigerant spaces 77 and 78 (by changing the cross-sectional area, it is possible to adjust the flow path resistance between the first tube 16a of the downstream heat exchange section 72 and the refrigerant space 77.
- the first coolant space 77 forms a coolant space 76 and a second coolant space 78, as shown in FIGS.
- the tank forming members 753d and 753e are different from the tank forming member 753.
- FIG. 23 is an exploded perspective view of the header tank 75
- FIG. 24 is a cross-sectional view corresponding to FIG. 22A
- FIG. 25 corresponds to FIG. It is sectional drawing.
- the tank forming member 753 forms the coolant space 76 and the second coolant space 78, but does not form the first coolant space 77. Instead, a second tank forming member 753d and a third tank forming member 753e are provided, and the second tank forming member 753d and the third tank forming member 753e are provided with a space for cooling liquid in the flow direction X of the outside air.
- a first refrigerant space 77 is formed between 76 and the second refrigerant space 78.
- each of the second tank forming member 753d and the third tank forming member 753e has a U-shaped cross-sectional shape, and the second tank forming member 753d and the third tank forming member 753e are mutually connected.
- the first refrigerant space 77 is formed by combining the concave surfaces facing each other.
- the second tank forming member 753d includes a flow path connecting portion 753f protruding to the side facing the second plate member 902, and the through hole 753g overlapping the through hole 902a of the second plate member 902 is the flow path connecting portion. 753f. Then, the flow path connecting portion 753f is in contact with and joined to the plate surface of the second plate member 902 facing the flow path connecting portion 753f, so that the through hole 753g of the second tank forming member 753d and the second plate member 902 are joined.
- the through holes 902a communicate with each other. Note that an escape hole 753h is formed in the first tank forming member 753 in order to avoid interference with the flow path connecting portion 753f.
- the upstream side refrigerant communication path 752a includes a through hole 901a of the first plate member 901, a through hole 902a of the second plate member 902, and a through hole 753g of the second tank forming member 753d. Consists of.
- the configurations of the downstream side refrigerant communication passages 752b and 752d and the upstream side coolant communication passage 752c are the same as those in the twelfth embodiment.
- FIG. 26 is a schematic perspective view for explaining the refrigerant flow and the coolant flow in the heat exchanger 70 of the present embodiment.
- the coolant inflow pipe 434 is connected to one end in the longitudinal direction (left side in FIG. 26) of the second upstream tank portion 730b disposed on one end in the longitudinal direction of the coolant tube 43a (upper side in FIG. 26). .
- the coolant outflow pipe 435 is connected to the other end in the longitudinal direction of the second upstream tank portion 730b (the right side in FIG. 26). Both longitudinal ends of the first upstream tank portion 730a are closed by a closing member.
- the refrigerant outflow pipe 165 is connected to one end in the longitudinal direction (left side in FIG. 26) of the second downstream tank portion 740b arranged on one end in the longitudinal direction (upper side in FIG. 26) of the refrigerant tube 16a.
- the refrigerant inflow piping 164 is connected to the other end in the longitudinal direction of the second downstream tank portion 740b (the right side in FIG. 26). Both ends of the first downstream tank portion 740a in the longitudinal direction are closed by a closing member.
- an upstream partition member 732 that partitions the coolant space 76 into two in the longitudinal direction of the second upstream tank portion 730b is disposed.
- a space communicating with the cooling liquid inflow piping 434 is referred to as a first cooling liquid space 76a and is referred to as a cooling liquid outflow piping.
- a space communicating with 435 is referred to as a second coolant space 76b.
- a downstream partition member 742 that partitions the refrigerant space 77 into two in the longitudinal direction of the second downstream tank portion 740b is disposed in the second downstream tank portion 740b.
- a space communicating with the refrigerant inflow pipe 164 is referred to as a first refrigerant space 77a and communicates with the refrigerant outflow pipe 165.
- the space is referred to as a second refrigerant space 77b.
- a part of the refrigerant flowing into the first refrigerant space 77a of the second downstream tank portion 740b via the refrigerant inflow pipe 164 is formed in the intermediate plate member 752. It flows into the refrigerant
- the refrigerant that has flowed out of the refrigerant tube 16a of the downstream heat exchange section 72 gathers in the refrigerant space 77 of the first downstream tank section 740a via the refrigerant communication paths 752b and 752d formed in the intermediate plate member 752. To do.
- the refrigerant that has flowed out of the refrigerant tube 16a of the upstream heat exchange section 71 enters the refrigerant space 77 of the first downstream tank section 740a via the upstream refrigerant communication path 752a formed in the intermediate plate member 752. Gather together.
- the refrigerant gathered in the refrigerant space 77 of the first downstream tank portion 740a flows from the right side to the left side in FIG. After that, a part of the refrigerant gathered in the refrigerant space 77 of the first downstream tank part 740a passes through the refrigerant communication passages 752b and 752d formed in the intermediate plate member 752, and the refrigerant in the downstream heat exchange part 72 It flows into the tube 16a and flows in the refrigerant tube 16a from the lower side to the upper side in the figure.
- the other part of the refrigerant gathered in the refrigerant space 77 of the first downstream tank portion 740a is passed through the upstream refrigerant communication passage 752a formed in the intermediate plate member 752, and the upstream heat exchange portion 72.
- the refrigerant flows in the refrigerant tube 16a and flows in the refrigerant tube 16a from the lower side to the upper side in FIG.
- the refrigerant that has flowed out of the refrigerant tube 16a of the downstream heat exchange section 72 enters the second refrigerant space 77b of the second downstream tank section 740b via the refrigerant communication paths 752b and 752d formed in the intermediate plate member 752. Gather together.
- the refrigerant flowing out of the refrigerant tube 16a of the upstream heat exchange section 71 passes through the upstream refrigerant communication path 752a formed in the intermediate plate member 752, and the second refrigerant space of the second downstream tank section 740b. Collect at 77b.
- the refrigerant gathered in the second refrigerant space 77b of the second downstream tank portion 740b flows from the right side to the left side in FIG. 26 and flows out from the refrigerant outflow pipe 165.
- the coolant flowing into the first coolant space 76a of the second upstream tank portion 730b via the coolant inflow pipe 434 is formed in the intermediate plate member 752. It flows in into the coolant tube 43a of the upstream heat exchange part 71 via the coolant communication path 752c, and flows in the coolant tube 43a from the upper side to the lower side in FIG.
- the coolant that has flowed out of the coolant tube 43a of the upstream heat exchange section 71 enters the coolant space 76 of the first upstream tank section 730a via the coolant communication path 752c formed in the intermediate plate member 752. Gather together. Then, the coolant gathered in the coolant space 76 of the first upstream tank portion 730a flows from the left side to the right side in FIG.
- the coolant gathered in the coolant space 76 of the first upstream tank portion 730a passes through the coolant communication passage 752c formed in the intermediate plate member 752, and serves as the coolant for the upstream heat exchange portion 71. It flows into the tube 43a and flows in the coolant tube 43a from the lower side to the upper side in the figure.
- the coolant that has flowed out of the coolant tube 43a of the upstream heat exchange section 71 passes through the coolant communication path 752c formed in the intermediate plate member 752, and the second coolant space in the second upstream tank section 730b. Collect at 76b.
- the coolant that has gathered in the second coolant space 76b of the second upstream tank section 730b flows from the left side to the right side in FIG. 26 and flows out from the coolant outlet pipe 435.
- FIG. 27 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- the refrigerant flow in the heat exchanger 70 is indicated by thick solid arrows, and the same applies to FIGS. 28 to 35 described later.
- the first upstream tank unit 730a and the first downstream tank unit 740a are located below the gravity direction with respect to the upstream heat exchange unit 71 and the downstream heat exchange unit 72 (see FIG. 9 and the like). Arranged on the side. This is the same in the 16th to 26th embodiments described later.
- the downstream partition member 742 that partitions the internal space into two in the longitudinal direction of the first downstream tank portion 740a is disposed. Therefore, the first downstream tank portion 740a is formed with a first refrigerant space 77a and a second refrigerant space 77b arranged in series from the other end in the longitudinal direction (the right side in FIG. 27). .
- the refrigerant inflow pipe 164 is connected to a first refrigerant space 77a formed in the first downstream tank portion 740a.
- the refrigerant outflow pipe 165 is connected to a second refrigerant space 77b formed in the first downstream tank portion 740a.
- the second downstream tank portion 740b is closed on both sides in the longitudinal direction by a closing member, and a refrigerant space 77 is formed inside.
- the refrigerant space 77 formed in the second downstream tank portion 740b collects the refrigerant from the refrigerant tube 16a and distributes the refrigerant to the refrigerant tube 16a.
- the portion where the refrigerant tube 16a interposed between the refrigerant space 77a and the first refrigerant space 77a is connected is on the refrigerant tube outlet side. It functions as a refrigerant space 772.
- a portion where the refrigerant tube 16a interposed between the second refrigerant space 77b is connected functions as the refrigerant space 771 on the refrigerant tube inlet side.
- the refrigerant space 771 on the refrigerant tube inlet side and the refrigerant space 772 on the refrigerant tube outlet side integrally form one refrigerant space 77.
- the first upstream tank portion 730a has one end side in the longitudinal direction (left side in FIG. 27) closed by a closing member, while the other end side in the longitudinal direction (right side in FIG. 27) has a coolant inlet pipe. 434 is connected.
- the second upstream tank portion 730b has one end in the longitudinal direction closed by a closing member, and a coolant outflow pipe 435 is connected to the other end in the longitudinal direction.
- a coolant space 76 is formed in each of the first upstream tank portion 730a and the second upstream tank portion 730b.
- the refrigerant that has flowed into the heat exchanger 70 from the refrigerant inflow pipe 164 flows from the first refrigerant space 77a formed in the first downstream tank portion 740a, as indicated by the thick solid line arrow in FIG. Then, the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the first refrigerant space 77a upward in the gravity direction. Then, the refrigerant flows from the refrigerant tube 16a to the refrigerant space 77 formed in the second downstream tank portion 740b, and the other end in the longitudinal direction of the second downstream tank portion 740b in the refrigerant space 77. Flows from the side to one end in the longitudinal direction.
- the refrigerant passes through a plurality of refrigerant tubes 16a communicating with the refrigerant space 77 and the second refrigerant space 77b from the refrigerant space 77 formed in the second downstream tank portion 740b. It flows downward in the direction of gravity and flows from the refrigerant tube 16a to the second refrigerant space 77b.
- FIG. 28 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is disposed in the first upstream tank portion 730a. Therefore, the first upstream tank portion 730a is formed with a first refrigerant space 77a and a second refrigerant space 77b arranged in series from the other end in the longitudinal direction (the right side in FIG. 28). .
- the refrigerant inflow pipe 164 is connected to a first refrigerant space 77a formed in the first upstream tank portion 730a.
- the refrigerant outflow pipe 165 is connected to a second refrigerant space 77b formed in the first upstream tank portion 730a.
- the second downstream tank portion 740b is closed on both sides in the longitudinal direction by a closing member, and a refrigerant space 77 is formed inside.
- first downstream tank portion 740a has one end side in the longitudinal direction (left side in FIG. 28) closed by a closing member, while the other end side in the longitudinal direction (right side in FIG. 28) has a coolant inlet pipe. 434 is connected.
- the second upstream tank portion 730b has one end in the longitudinal direction closed by a closing member, and a coolant outflow pipe 435 is connected to the other end in the longitudinal direction.
- a coolant space 76 is formed in each of the first downstream tank portion 740a and the second upstream tank portion 730b.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 flows from the first refrigerant space 77a formed in the first upstream tank portion 730a as shown by the thick solid line arrow in FIG. Then, the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the first refrigerant space 77a upward in the gravity direction. Then, the refrigerant flows from the refrigerant tube 16a to the refrigerant space 77 formed in the second downstream tank portion 740b, and the other end in the longitudinal direction of the second downstream tank portion 740b in the refrigerant space 77. Flows from the side to one end in the longitudinal direction.
- the refrigerant passes through a plurality of refrigerant tubes 16a communicating with the refrigerant space 77 and the second refrigerant space 77b from the refrigerant space 77 formed in the second downstream tank portion 740b. It flows downward in the direction of gravity and flows from the refrigerant tube 16a to the second refrigerant space 77b.
- FIG. 29 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- the first downstream tank section 740a is provided with a downstream partition member 742 that partitions the internal space into two in the longitudinal direction thereof. Therefore, a first refrigerant space 77a and a second refrigerant space 77b are formed in the first downstream tank portion 740a in series from the other longitudinal end side (the right side in FIG. 29). .
- the refrigerant inflow pipe 164 is connected to a first refrigerant space 77a formed in the first downstream tank portion 740a.
- the refrigerant outflow pipe 165 is connected to a second refrigerant space 77b formed in the first downstream tank portion 740a.
- the second upstream tank portion 730b is closed on both sides in the longitudinal direction by a closing member, and a refrigerant space 77 is formed inside.
- the first upstream tank portion 730a has one end side in the longitudinal direction (left side in FIG. 29) closed by a closing member, while the other end side in the longitudinal direction (right side in FIG. 29) has a coolant inlet pipe. 434 is connected.
- the second downstream tank portion 740b is closed at one end in the longitudinal direction by a closing member, and is connected to a coolant outflow pipe 435 at the other end in the longitudinal direction.
- a coolant space 76 is formed in each of the first upstream tank portion 730a and the second downstream tank portion 740b.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 flows from the first refrigerant space 77a formed in the first downstream tank portion 740a as shown by the thick solid arrow in FIG. Then, the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the first refrigerant space 77a upward in the gravity direction. Then, the refrigerant flows from the refrigerant tube 16 a to the refrigerant space 77 formed in the second upstream tank portion 730 b, and the other longitudinal end of the second upstream tank portion 730 b in the refrigerant space 77. Flows from the side to one end in the longitudinal direction.
- the refrigerant passes through a plurality of refrigerant tubes 16a communicating with the refrigerant space 77 and the second refrigerant space 77b from the refrigerant space 77 formed in the second upstream tank portion 730b. It flows downward in the direction of gravity and flows from the refrigerant tube 16a to the second refrigerant space 77b.
- FIG. 30 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- the first upstream tank portion 730a is provided with an upstream partition member 732 that divides the internal space into two in the longitudinal direction thereof. Therefore, the first upstream tank portion 730a is formed with a first refrigerant space 77a and a second refrigerant space 77b arranged in series from the other end in the longitudinal direction (the right side in FIG. 30). .
- the refrigerant inflow pipe 164 is connected to a first refrigerant space 77a formed in the first upstream tank portion 730a.
- the refrigerant outflow pipe 165 is connected to a second refrigerant space 77b formed in the first upstream tank portion 730a.
- the second upstream tank portion 730b is closed on both sides in the longitudinal direction by a closing member, and a refrigerant space 77 is formed inside.
- first downstream tank portion 740a has one end side in the longitudinal direction (left side in FIG. 30) closed by a closing member, while the other end side in the longitudinal direction (right side in FIG. 30) has a coolant inlet pipe. 434 is connected.
- the second downstream tank portion 740b is closed at one end in the longitudinal direction by a closing member, and is connected to a coolant outflow pipe 435 at the other end in the longitudinal direction.
- a coolant space 76 is formed in each of the first downstream tank portion 740a and the second downstream tank portion 740b.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 flows from the first refrigerant space 77a formed in the first upstream tank portion 730a as shown by the thick solid line arrow in FIG. Then, the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the first refrigerant space 77a upward in the gravity direction. Then, the refrigerant flows from the refrigerant tube 16 a to the refrigerant space 77 formed in the second upstream tank portion 730 b, and the other longitudinal end of the second upstream tank portion 730 b in the refrigerant space 77. Flows from the side to one end in the longitudinal direction.
- the refrigerant passes through a plurality of refrigerant tubes 16a communicating with the refrigerant space 77 and the second refrigerant space 77b from the refrigerant space 77 formed in the second upstream tank portion 730b. It flows downward in the direction of gravity and flows from the refrigerant tube 16a to the second refrigerant space 77b.
- FIG. 31 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- the first upstream tank section 730a is provided with an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof.
- the first upstream tank portion 730a is formed with a first refrigerant space 77a and a second coolant space 76b arranged in series from the other end in the longitudinal direction (the right side in FIG. 31). ing.
- first downstream tank portion 740a is provided with a downstream partition member 742 that partitions the internal space into two in the longitudinal direction thereof.
- first downstream tank portion 740a is formed with a first coolant space 76a and a second refrigerant space 77b arranged in series from the other end in the longitudinal direction thereof.
- the refrigerant inflow pipe 164 is connected to a first refrigerant space 77a formed in the first upstream tank portion 730a.
- the refrigerant outflow pipe 165 is connected to a second refrigerant space 77b formed in the first downstream tank portion 740a.
- the second upstream tank portion 730b is closed on both sides in the longitudinal direction by a closing member, and a refrigerant space 77 is formed inside.
- the coolant inflow pipe 434 is connected to a first coolant space 76a formed in the first downstream tank portion 740a.
- the coolant outflow pipe 435 is connected to the second coolant space 76b formed in the first upstream tank portion 730a.
- the second downstream tank portion 740b is closed on both sides in the longitudinal direction by a closing member, and a cooling liquid space 76 is formed inside.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 flows from the first refrigerant space 77a formed in the first upstream tank portion 730a as shown by the thick solid line arrow in FIG. Then, the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the first refrigerant space 77a upward in the gravity direction. Then, the refrigerant flows from the refrigerant tube 16 a to the refrigerant space 77 formed in the second upstream tank portion 730 b, and the other longitudinal end of the second upstream tank portion 730 b in the refrigerant space 77. Flows from the side to one end in the longitudinal direction.
- the refrigerant passes through a plurality of refrigerant tubes 16a communicating with the refrigerant space 77 and the second refrigerant space 77b from the refrigerant space 77 formed in the second upstream tank portion 730b. It flows downward in the direction of gravity and flows from the refrigerant tube 16a to the second refrigerant space 77b.
- the coolant flowing into the heat exchanger 70 from the coolant inflow pipe 434 communicates with the first coolant space 76a from the first coolant space 76a formed in the first downstream tank section 740a.
- the plurality of coolant tubes 43a flow upward in the direction of gravity.
- the cooling liquid flows from the cooling liquid tube 43a to the cooling liquid space 76 formed in the second downstream tank section 740b, and in the cooling liquid space 76, the second downstream tank section 740b It flows from the other end in the longitudinal direction to one end in the longitudinal direction.
- the cooling liquid is a plurality of cooling liquids communicating from the cooling liquid space 76 formed in the second downstream tank portion 740b to the cooling liquid space 76 and the second cooling liquid space 76b.
- FIG. 32 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is disposed in the first upstream tank portion 730a. Therefore, the first upstream tank portion 730a is formed with a first refrigerant space 77a and a third refrigerant space 77c arranged in series from the other end in the longitudinal direction (the right side in FIG. 32). .
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is also disposed in the second upstream tank portion 730b. Therefore, a fourth refrigerant space 77d and a second refrigerant space 77b are formed in the second upstream tank portion 730b in series from the other end in the longitudinal direction thereof.
- the upstream partition member 732 provided in the second upstream tank portion 730b is one end in the longitudinal direction of the second upstream tank portion 730b rather than the upstream partition member 732 provided in the first upstream tank portion 730a. It is arranged on the side (left side in FIG. 32). Therefore, in the longitudinal direction of the second upstream tank portion 730b, that is, in the stacking direction of the refrigerant tubes 16a, the upstream partition member 732 and the first upstream tank portion 730a provided in the second upstream tank portion 730b are provided.
- the refrigerant tube 16a disposed between the upstream partition member 732 communicates with both the third refrigerant space 77c and the fourth refrigerant space 77d.
- the refrigerant inflow pipe 164 is connected to a first refrigerant space 77a formed in the first upstream tank portion 730a.
- the refrigerant outflow pipe 165 is connected to a second refrigerant space 77b formed in the second upstream tank portion 730b.
- the first upstream tank portion 730a is closed at one end in the longitudinal direction by a closing member, and the second upstream tank portion 730b is closed at the other end in the longitudinal direction by a closing member.
- the first downstream tank portion 740a is closed at one end in the longitudinal direction by a closing member, and connected to the coolant inflow pipe 434 at the other end in the longitudinal direction.
- the second downstream tank portion 740b is closed at one end in the longitudinal direction by a closing member, and is connected to a coolant outflow pipe 435 at the other end in the longitudinal direction.
- a coolant space 76 is formed in each of the first downstream tank portion 740a and the second downstream tank portion 740b.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 flows from the first refrigerant space 77a formed in the first upstream tank portion 730a as shown by the thick solid line arrow in FIG. Then, the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the first refrigerant space 77a upward in the gravity direction. Next, the refrigerant flows from the refrigerant tube 16a to the fourth refrigerant space 77d formed in the second upstream tank portion 730b, and the second upstream tank portion 730b in the fourth refrigerant space 77d. From the other end in the longitudinal direction to the one end in the longitudinal direction.
- the refrigerant flows from the fourth refrigerant space 77d downward in the direction of gravity through the plurality of refrigerant tubes 16a communicating with the fourth refrigerant space 77d and the third refrigerant space 77c. Then, the refrigerant flows from the refrigerant tube 16a to the third refrigerant space 77c. Next, the refrigerant flows in the third refrigerant space 77c from the other end in the longitudinal direction of the first upstream tank portion 730a to one end in the longitudinal direction, and the third refrigerant space 77c and the second refrigerant space The refrigerant flows through the plurality of refrigerant tubes 16a communicating with the space 77b upward in the gravity direction. Further, the refrigerant flows from the refrigerant tube 16a to the second refrigerant space 77b.
- a plurality of cooling liquids flowing into the heat exchanger 70 from the cooling liquid inflow pipe 434 communicate with the cooling liquid space 76 from the cooling liquid space 76 formed in the first downstream tank portion 740a.
- the coolant flows from the coolant tube 43a to the coolant space 76 formed in the second downstream tank portion 740b.
- the heat exchanger 70 includes a plurality of refrigerant tubes 16a interposed between a pair of refrigerant spaces 77 (including 77a, 77b, 77c, and 77d) in the refrigerant flow path. And three refrigerant paths 161a, 161b, 161c (first fluid path). Specifically, for a plurality of refrigerants interposed between the first refrigerant space 77a and the fourth refrigerant space 77d and connected to both the first refrigerant space 77a and the fourth refrigerant space 77d.
- a first refrigerant path 161a is configured from the tube 16a.
- the second refrigerant path 161b is configured. Also, from the plurality of refrigerant tubes 16a interposed between the third refrigerant space 77c and the second refrigerant space 77b and connected to both the third refrigerant space 77c and the second refrigerant space 77b.
- the third refrigerant path 161c is configured.
- the first refrigerant path 161a, the second refrigerant path 161b, and the third refrigerant path 161c are connected in series via the refrigerant space 77 in the refrigerant flow path (refrigerant flow path) as shown by the solid line arrows in FIG. Are consolidated. Further, the refrigerant flows upward in the first refrigerant path 161a, flows downward in the second refrigerant path 161b, and flows upward in the third refrigerant path 161c.
- each of the first refrigerant path 161a, the second refrigerant path 161b, and the third refrigerant path 161c is such that the refrigerant flows in the opposite direction in the direction of gravity with respect to the other refrigerant paths adjacent in the refrigerant flow path.
- the other refrigerant paths adjacent in the refrigerant flow path mean other refrigerant paths adjacent in the stacking direction of the refrigerant tubes 16a as can be seen from FIG.
- the refrigerant flows in the gravity direction in the direction opposite to the other refrigerant path adjacent to the first refrigerant path 161a, that is, the second refrigerant path 161b.
- the refrigerant flows in a direction opposite to the gravity direction with respect to other refrigerant paths adjacent to the second refrigerant path 161b in the refrigerant distribution path, that is, the first refrigerant path 161a and the third refrigerant path 161c. Is.
- the third refrigerant path 161c is a refrigerant flowing in the direction opposite to the gravity direction with respect to another refrigerant path adjacent to the third refrigerant path 161c in the refrigerant flow path, that is, the second refrigerant path 161b.
- the first refrigerant path 161a and the third refrigerant path 161c are upflow refrigerant paths (upflow first fluid path) in which the refrigerant flows upward (upward) in the gravity direction.
- the tube stacking width L1 of the refrigerant tubes 16a constituting the first refrigerant path 161a is equal to that of the refrigerant tubes 16a constituting the second refrigerant paths 161b adjacent in the refrigerant flow path. It is smaller than the tube stacking width L2 (L2> L1).
- the tube stacking width L3 of the refrigerant tube 16a constituting the third coolant path 161c is also smaller than the tube stacking width L2 of the second coolant path 161b adjacent in the coolant circulation path (L3 ⁇ L2 ). That is, regardless of which of the first refrigerant path 161a and the third refrigerant path 161c, the tube stacking width of the refrigerant tube 16a is increased in the refrigerant flow path. It is smaller than any refrigerant path (second refrigerant path 161b) adjacent to the flowing refrigerant path.
- the tube stack width L1, L2, L3 increases as the number of tube stacks of the refrigerant tubes 16a constituting each coolant path 161a, 161b, 161c increases, and the tube stack number and the tube stack widths L1, L2, L3 Correspond to each other in a one-to-one relationship.
- the first refrigerant path 161a and the third refrigerant path 161c have a refrigerant flow according to the small tube stacking widths L1 and L3.
- the path is narrowed compared to the second refrigerant path 161b. Therefore, the flow rate of the upward flow in which the refrigerant flows upward in the gravity direction in the refrigerant tube 16a is increased, and for example, the refrigerant can be vigorously raised against the weight of the liquid component contained in the refrigerant. As a result, the refrigerant can easily flow through the refrigerant tubes 16a evenly.
- FIG. 33 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is disposed in the first upstream tank portion 730a. Therefore, the first upstream tank portion 730a is formed with a first refrigerant space 77a and a third refrigerant space 77c arranged in series from the other end in the longitudinal direction (the right side in FIG. 33). .
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is also disposed in the second upstream tank portion 730b. Therefore, a fourth refrigerant space 77d and a second coolant space 76b are formed in the second upstream tank portion 730b in series from the other end in the longitudinal direction thereof.
- a downstream partition member 742 that partitions the internal space into two in the longitudinal direction thereof is disposed in the second downstream tank portion 740b. Therefore, a first coolant space 76a and a second refrigerant space 77b are formed in the second downstream tank portion 740b in series from the other end in the longitudinal direction. In addition, a cooling liquid space 76 is formed in the first downstream tank portion 740a.
- upstream partition members 732 provided in the first upstream tank portion 730a and the second upstream tank portion 730b shown in FIG. 33 are arranged at the same positions as in FIG. 32 described above.
- the downstream partition member 742 provided in the second downstream tank portion 740b is disposed at the same position as the upstream partition member 732 provided in the second upstream tank portion 730b in the stacking direction of the refrigerant tubes 16a. Has been.
- the refrigerant inflow pipe 164 is connected to the first refrigerant space 77a, and the refrigerant outflow pipe 165 is connected to the second refrigerant space 77b.
- the coolant inflow pipe 434 is connected to the first coolant space 76a, and the coolant outflow pipe 435 is connected to the second coolant space 76b.
- one end side in the longitudinal direction of the first upstream tank portion 730a, the other end side in the longitudinal direction of the second upstream tank portion 730b, and both ends in the longitudinal direction of the first downstream tank portion 740a are respectively closed by blocking members. ing.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 communicates with the first refrigerant space 77a from the first refrigerant space 77a as shown by the thick solid arrow in FIG.
- the refrigerant flows through the plurality of refrigerant tubes 16a upward in the direction of gravity.
- the refrigerant flows from the refrigerant tube 16a to the fourth refrigerant space 77d, and in the fourth refrigerant space 77d, from the other longitudinal end side of the second upstream tank portion 730b to one longitudinal end side. And flow.
- the refrigerant flows from the fourth refrigerant space 77d downward in the direction of gravity through the plurality of refrigerant tubes 16a communicating with the fourth refrigerant space 77d and the third refrigerant space 77c. Then, the refrigerant flows from the refrigerant tube 16a to the third refrigerant space 77c. Next, the refrigerant flows in the third refrigerant space 77c from the other end in the longitudinal direction of the first upstream tank portion 730a to one end in the longitudinal direction, and the third refrigerant space 77c and the second refrigerant space The refrigerant flows through the plurality of refrigerant tubes 16a communicating with the space 77b upward in the gravity direction. Further, the refrigerant flows from the refrigerant tube 16a to the second refrigerant space 77b.
- the coolant flowing into the heat exchanger 70 from the coolant inflow pipe 434 is transferred from the first coolant space 76a into the plurality of coolant tubes 43a communicating with the first coolant space 76a. Flows downward in the direction of gravity.
- the coolant flows from the coolant tube 43 a to the coolant space 76 formed in the first downstream tank portion 740 a, and the first downstream tank portion 740 a in the coolant space 76. From the other end in the longitudinal direction to the one end in the longitudinal direction.
- the cooling liquid is supplied from the cooling liquid space 76 formed in the first downstream tank portion 740a to a plurality of cooling liquids communicating with the cooling liquid space 76 and the second cooling liquid space 76b. The liquid flows through the liquid tube 43a upward in the gravity direction, and flows from the cooling liquid tube 43a to the second cooling liquid space 76b.
- the heat exchanger 70 in FIG. 33 includes a first refrigerant path 161a, a second refrigerant path 161b, and a third refrigerant path 161c similar to those in FIG. 32 described above.
- the first refrigerant path 161a and the third refrigerant path 161c are upward flow refrigerant paths.
- the tube stacking width L1 of the first refrigerant path 161a is smaller than the tube stacking width L2 of the second refrigerant path 161b (L2> L1), and the tube stacking width L3 of the third refrigerant path 161c is also the second. It is smaller than the tube stacking width L2 of the refrigerant path 161b (L3 ⁇ L2).
- FIG. 34 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is disposed in the second upstream tank portion 730b. Therefore, the second upstream tank portion 730b is formed with a first refrigerant space 77a and a third refrigerant space 77c arranged in series from the other longitudinal end side (the right side in FIG. 34) thereof. .
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is also disposed in the first upstream tank portion 730a. Therefore, a fourth refrigerant space 77d and a second coolant space 76b are formed in the first upstream tank portion 730a in series from the other end in the longitudinal direction thereof.
- a coolant space 76 is formed in each of the first downstream tank portion 740a and the second downstream tank portion 740b.
- the upstream partition member 732 provided in the second upstream tank portion 730b is longer than the upstream partition member 732 provided in the first upstream tank portion 730a in the longitudinal direction of the second upstream tank portion 730b. It is arrange
- the refrigerant inflow pipe 164 is connected to the first refrigerant space 77a, and the refrigerant outflow pipe 165 is connected to the second refrigerant space 77b.
- the coolant inflow pipe 434 is connected to a coolant space 76 formed in the first downstream tank portion 740a.
- the coolant outlet pipe 435 is connected to a coolant space 76 formed in the second downstream tank portion 740b. Further, the other end in the longitudinal direction of the first upstream tank portion 730a, one end in the longitudinal direction of the second upstream tank portion 730b, one end in the longitudinal direction of the first downstream tank portion 740a, and the second downstream tank portion. One end side in the longitudinal direction of 740b is closed by a closing member.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 communicates from the first refrigerant space 77a to the first refrigerant space 77a as shown by the thick solid line arrow in FIG.
- the refrigerant flows through the plurality of refrigerant tubes 16a downward in the direction of gravity.
- the refrigerant flows from the refrigerant tube 16a to the fourth refrigerant space 77d, and in the fourth refrigerant space 77d, from the other longitudinal end of the first upstream tank portion 730a to one longitudinal end. And flow.
- the refrigerant flows from the fourth refrigerant space 77d to the upper side in the gravity direction in the plurality of refrigerant tubes 16a communicating with the fourth refrigerant space 77d and the third refrigerant space 77c.
- the refrigerant flows from the refrigerant tube 16a to the third refrigerant space 77c.
- the refrigerant flows in the third refrigerant space 77c from the other end in the longitudinal direction of the second upstream tank portion 730b to one end in the longitudinal direction, and the third refrigerant space 77c and the second refrigerant space
- the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the space 77b downward in the gravity direction. Further, the refrigerant flows from the refrigerant tube 16a to the second refrigerant space 77b.
- a plurality of cooling liquids flowing into the heat exchanger 70 from the cooling liquid inflow pipe 434 communicate with the cooling liquid space 76 from the cooling liquid space 76 formed in the first downstream tank portion 740a.
- the coolant flows from the coolant tube 43a to the coolant space 76 formed in the second downstream tank portion 740b.
- the heat exchanger 70 in FIG. 34 has a first refrigerant path 161a, a second refrigerant path 161b, and a third refrigerant path 161c, as in FIG. 32 described above, and these refrigerant paths 161a, 161b, 161c.
- the refrigerant flow direction in FIG. 3 differs from the tube stacking widths L1, L2, and L3.
- the second refrigerant path 161b is an upflow refrigerant path, while the first refrigerant path 161a and the third refrigerant path 161c do not correspond to the upflow refrigerant path.
- the tube stacking width L2 of the second refrigerant path 161b is smaller than both the tube stacking width L1 of the first refrigerant path 161a and the tube stacking width L3 of the third refrigerant path 161c (L1>). L2, L3> L2).
- the tube stacking width of the refrigerant tube 16a is such that the second refrigerant path 161b, which is an upflow refrigerant path, is adjacent to the second refrigerant path 161b in the refrigerant flow path (first refrigerant path). 161a and the third refrigerant path 161c). Therefore, the present embodiment can provide the same effects as those of the twentieth embodiment described above.
- the twenty-third embodiment is obtained by changing the flow path configuration of the heat exchanger 70 with respect to the first and fourteenth to twenty-second embodiments described above.
- FIG. 35 is a schematic perspective view for explaining the refrigerant flow in the heat exchanger 70 of the present embodiment.
- the second upstream tank portion 730b is provided with an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof. Therefore, the second upstream tank portion 730b is formed with a first refrigerant space 77a and a third refrigerant space 77c arranged in series from the other longitudinal end (the right side in FIG. 35). .
- an upstream partition member 732 that partitions the internal space into two in the longitudinal direction thereof is also disposed in the first upstream tank portion 730a. Therefore, a fourth refrigerant space 77d and a second coolant space 76b are formed in the first upstream tank portion 730a in series from the other end in the longitudinal direction thereof.
- first downstream tank portion 740a is provided with a downstream partition member 742 that partitions the internal space into two in the longitudinal direction thereof. Therefore, the first downstream tank portion 740a is formed with a first coolant space 76a and a second refrigerant space 77b arranged in series from the other longitudinal end of the tank portion 740a. A cooling liquid space 76 is formed in the second downstream tank portion 740b.
- upstream partition members 732 provided in the first upstream tank portion 730a and the second upstream tank portion 730b shown in FIG. 35 are arranged at the same positions as in FIG. 34 described above.
- the downstream partition member 742 provided in the first downstream tank portion 740a is disposed at the same position as the upstream partition member 732 provided in the first upstream tank portion 730a in the stacking direction of the refrigerant tubes 16a. Has been.
- the refrigerant inflow pipe 164 is connected to the first refrigerant space 77a, and the refrigerant outflow pipe 165 is connected to the second refrigerant space 77b.
- the coolant inflow pipe 434 is connected to the first coolant space 76a, and the coolant outflow pipe 435 is connected to the second coolant space 76b. Further, the other end in the longitudinal direction of the first upstream tank portion 730a, the one end in the longitudinal direction of the second upstream tank portion 730b, and the both ends in the longitudinal direction of the second downstream tank portion 740b are respectively closed by a closing member. ing.
- the refrigerant flowing into the heat exchanger 70 from the refrigerant inflow pipe 164 communicates from the first refrigerant space 77a to the first refrigerant space 77a, as indicated by the thick solid line arrow in FIG.
- the refrigerant flows through the plurality of refrigerant tubes 16a downward in the direction of gravity.
- the refrigerant flows from the refrigerant tube 16a to the fourth refrigerant space 77d, and in the fourth refrigerant space 77d, from the other longitudinal end of the first upstream tank portion 730a to one longitudinal end. And flow.
- the refrigerant flows from the fourth refrigerant space 77d to the upper side in the gravity direction in the plurality of refrigerant tubes 16a communicating with the fourth refrigerant space 77d and the third refrigerant space 77c.
- the refrigerant flows from the refrigerant tube 16a to the third refrigerant space 77c.
- the refrigerant flows in the third refrigerant space 77c from the other end in the longitudinal direction of the second upstream tank portion 730b to one end in the longitudinal direction, and the third refrigerant space 77c and the second refrigerant space
- the refrigerant flows through the plurality of refrigerant tubes 16a communicating with the space 77b downward in the gravity direction. Further, the refrigerant flows from the refrigerant tube 16a to the second refrigerant space 77b.
- the coolant flowing into the heat exchanger 70 from the coolant inflow pipe 434 is transferred from the first coolant space 76a into the plurality of coolant tubes 43a communicating with the first coolant space 76a. Flows upward in the direction of gravity.
- the coolant flows from the coolant tube 43 a to the coolant space 76 formed in the second downstream tank portion 740 b, and the second downstream tank portion 740 b in the coolant space 76. From the other end in the longitudinal direction to the one end in the longitudinal direction.
- the cooling liquid is supplied from a cooling liquid space 76 formed in the second downstream tank portion 740b to a plurality of cooling liquids communicating with the cooling liquid space 76 and the second cooling liquid space 76b. The liquid flows in the liquid tube 43a downward in the gravity direction, and flows from the cooling liquid tube 43a to the second cooling liquid space 76b.
- the heat exchanger 70 in FIG. 35 includes a first refrigerant path 161a, a second refrigerant path 161b, and a third refrigerant path 161c similar to those in FIG. 34 described above.
- the second refrigerant path 161b is an upflow refrigerant path.
- the tube stacking width L2 of the second refrigerant path 161b is smaller than the tube stacking width L1 of the first refrigerant path 161a (L1> L2), and the tube stacking width L3 of the third refrigerant path 161c is the same. It is smaller than that (L3> L2). Therefore, the present embodiment can provide the same effects as those of the twentieth embodiment described above.
- FIG. 36 shows a tank cross-sectional view of portion G in FIG. 36 (a) is a cross-sectional view corresponding to FIG. 13 (a)
- FIG. 36 (b) is a cross-sectional view corresponding to FIG. 13 (b)
- FIGS. 36 (a) and 36 (b) are respectively diagrams. 13 (a) and 13 (b) are upside down.
- the intermediate plate member 752 includes a first plate member 911 and a second plate member 912 in order from the side closer to the upstream heat exchange unit 71 and the downstream heat exchange unit 72 (the lower side in FIG. 36). And the third plate member 913 are stacked in the thickness direction and joined together.
- the first plate member 911 includes a second plate member 912 from the second plate member 912 side so as to straddle both the refrigerant tubes 16a of the upstream heat exchange unit 71 and the downstream heat exchange unit 72.
- a coolant circulation part 911a that is a recessed hole recessed in the plate thickness direction is formed.
- two through holes 911b and 911c are formed side by side in the outside air flow direction X on the bottom surface of the refrigerant circulation part 911a.
- the refrigerant tube 16a of the upstream heat exchange section 71 passes through one of the through holes 911b, and the tip of the refrigerant tube 16a protrudes into the refrigerant circulation section 911a.
- coolant tube 16a of the downstream heat exchange part 72 penetrates the other through-hole 911c, and the front-end
- a through hole 912a is formed in the second plate member 912, and the through hole 912a communicates with the coolant circulation part 911a.
- the third plate member 913 is formed with a through hole 913a.
- the through hole 913a communicates with the through hole 912a of the second plate member 912 and also communicates with the refrigerant space 77.
- a refrigerant space 77 shown in FIG. 36 is a refrigerant space 771 on the refrigerant tube inlet side that is connected to the inlet side of the refrigerant tube 16a and distributes the refrigerant.
- the upstream side refrigerant communication path 752a is configured by the through hole 912a of the second plate member 912 and the through hole 913a of the third plate member 913.
- the refrigerant circulation portion 911a of the first plate member 911, the through hole 912a of the second plate member 912, and the through hole 913a of the third plate member 913 constitute a downstream refrigerant communication passage 752b.
- the first plate member 911 has a coolant circulation portion 911d and a coolant circulation portion 911a that are recessed holes recessed in the plate thickness direction from the second plate member 912 side. They are formed side by side from the upstream side of X. And the through-hole 911e is formed in the bottom face of the coolant circulation part 911d, and the through-hole 911f is formed in the bottom face of the coolant circulation part 911a.
- the coolant tube 43a of the upstream heat exchange section 71 passes through one through hole 911e, and the tip of the coolant tube 43a protrudes into the coolant circulation section 911d.
- the coolant circulation part 911 d communicates with the coolant tube 43 a of the upstream heat exchange part 71.
- coolant tube 16a of the downstream heat exchange part 72 penetrates the other through-hole 911f, and the front-end
- circulation part 911a is connected with the tube 16a for refrigerant
- a through hole 912c is formed in the second plate member 912, and the through hole 912c communicates with the coolant circulation part 911d without communicating with the refrigerant circulation part 911a.
- the third plate member 913 is formed with a through hole 913c, and the through hole 913c communicates with the through hole 912c of the second plate member 912. Further, the through hole 913 c of the third plate member 913 communicates with the coolant space 76 without communicating with the coolant space 77.
- the refrigerant circulation part 911a shown in FIG. 36 (b) is the same as the refrigerant circulation part 911a shown in FIG. 36 (a) described above, and the downstream part of the outside air flow direction X is a tube as shown in FIG. It extends in the stacking direction.
- the upstream side coolant communication path 752c is configured by the through hole 912c of the second plate member 912 and the through hole 913c of the third plate member 913.
- the refrigerant circulation portion 911a of the first plate member 911, the through hole 912a of the second plate member 912, and the through hole 913a of the third plate member 913 constitute a downstream refrigerant communication passage 752d. That is, the refrigerant flow path (upstream refrigerant communication path 752a) between the refrigerant space 771 on the refrigerant tube inlet side and the upstream refrigerant tube group 16b, and the refrigerant space 771 on the refrigerant tube inlet side and the downstream side.
- a refrigerant flow path (downstream refrigerant communication passages 752b and 752d) between the side refrigerant tube group 16c is provided in parallel.
- the refrigerant space 771 on the refrigerant tube inlet side in the outside air flow direction X is more upstream than the downstream refrigerant tube group 16c (low pressure loss side refrigerant tube group). It is arranged on the tube group 16b (high pressure loss side refrigerant tube group) side. In short, the refrigerant space 771 on the refrigerant tube inlet side is formed in the upstream tank portion 73.
- the flow path resistance between the refrigerant space 771 on the refrigerant tube inlet side and the upstream refrigerant tube group 16b is mainly due to the difference in the length of the refrigerant flow channel, and the refrigerant space 771 on the refrigerant tube inlet side. And the flow path resistance between the downstream refrigerant tube group 16c. This is because the flow path resistance of the refrigerant flow path increases as the flow path length of the refrigerant flow path increases.
- 752e is opened toward the refrigerant tube 16a included in the upstream refrigerant tube group 16b.
- the opening 752e of the upstream refrigerant communication passage 752a is provided so as to overlap the opening end surface 16d in a direction perpendicular to the opening end surface 16d of the refrigerant tube 16a.
- the upstream side refrigerant communication path 752a is opened so as to face the opening end face 16d of the refrigerant tube 16a.
- the refrigerant can be vigorously flowed into the upstream refrigerant tube group 16b on the high-pressure loss side using the dynamic pressure of the refrigerant flowing through the refrigerant space 771 on the refrigerant tube inlet side. Therefore, for example, it is possible to suppress a large amount of refrigerant from flowing toward the downstream refrigerant tube group 16c.
- the through hole 912a of the second plate member 912 and the through hole 913a of the third plate member 913 are formed as shown in FIG. 38, for example, as shown by a broken line L02 in FIG.
- the opening 752e of the refrigerant communication path 752a is not provided so as to overlap the opening end face 16d in a direction perpendicular to the opening end face 16d of the refrigerant tube 16a.
- the refrigerant flowing through the refrigerant tube 16a is gravity. It has a flow component in the direction.
- the refrigerant space 771 on the refrigerant tube inlet side shown in FIG. 36 is interposed between the refrigerant space 771 and the first refrigerant space 77a formed in the first upstream tank portion 730a. Since the refrigerant that has circulated through the refrigerant tube 16a flows in, the refrigerant that has exchanged heat with the outside air (third fluid) at least once in the upstream and downstream heat exchange units 71 and 72 is introduced.
- the refrigerant can exchange heat with the outside air once in the upstream and downstream heat exchange sections 71 and 72. For example, it is in a state composed of two phases of gas and liquid.
- the liquid component contained in the refrigerant is more susceptible to gravity than the gas, most of the refrigerant is contained in the refrigerant space 771 on the refrigerant tube inlet side. It is easy to flow into the refrigerant tube 16a connected to the upstream side in the refrigerant flow direction.
- the refrigerant space 771 on the refrigerant tube inlet side shown in FIG. 36 is arranged not on the downstream refrigerant tube group 16c but on the upstream refrigerant tube group 16b. Therefore, the refrigerant flow in the refrigerant space 771 is compared to the case where it is assumed that the refrigerant space 771 on the refrigerant tube inlet side is above the downstream refrigerant tube group 16c in which the refrigerant flows relatively easily. It is suppressed that the refrigerant is biased and flows into the refrigerant tube 16a on the upstream side.
- the refrigerant can be uniformly supplied to the plurality of refrigerant tubes 16a connected to the refrigerant space 771 on the refrigerant tube inlet side.
- the configurations of the second upstream tank portion 730b and the second downstream tank portion 740b in the twenty-fourth embodiment described above are as shown in FIG. 39 instead of FIG.
- the cross-sectional view corresponding to FIG. 36B is the same as that in the twenty-fourth embodiment, so that the illustration is omitted.
- the refrigerant circulation part 911a shown in FIG. 36 (b) is replaced with the refrigerant circulation part 911g, and FIG. 36 (b) is used.
- the intermediate plate member 752 includes a first plate member 911 and a second plate member 912 in order from the side closer to the upstream heat exchange unit 71 and the downstream heat exchange unit 72 (the lower side in FIG. 39). And the third plate member 913 are stacked in the thickness direction and joined together.
- refrigerant circulation portions 911a and 911g that are recessed holes recessed in the thickness direction from the second plate member 912 side are formed side by side in the outside air flow direction X.
- a through hole 911b is formed on the bottom surface of one refrigerant circulation portion 911a, and a through hole 911c is formed on the bottom surface of the other refrigerant circulation portion 911g.
- coolant tube 16a of the upstream heat exchange part 71 penetrates the through-hole 911b connected to the one refrigerant
- coolant tube 16a of the downstream heat exchange part 72 penetrates the through-hole 911c connected to the other refrigerant
- one refrigerant circulation part 911 a communicates with the refrigerant tube 16 a of the upstream heat exchange part 71, and the other refrigerant circulation part 911 g communicates with the refrigerant tube 16 a of the downstream heat exchange part 72.
- the third plate member 913 is formed with two through holes 913a and 913d.
- One of the through holes 913a communicates with one of the through holes 912a of the second plate member 912, and the refrigerant space. 77.
- the other through hole 913 d of the third plate member 913 communicates with the other through hole 912 d of the second plate member 912 and also communicates with the refrigerant space 77. Note that neither of the two through holes 913 a and 913 d of the third plate member 913 communicates with the coolant space 76.
- the upstream side refrigerant communication path 752a is configured by the through hole 912a of the second plate member 912 and the through hole 913a of the third plate member 913.
- the refrigerant circulation portion 911d of the first plate member 911, the through hole 912d of the second plate member 912, and the through hole 913d of the third plate member 913 constitute a downstream refrigerant communication passage 752b.
- the refrigerant circulation part 911g in FIG. 36 (b) is the same as the above-described refrigerant circulation part 911g shown in FIG. 39, and the refrigerant circulation part 911g extends in the tube stacking direction as in the above-described twenty-fourth embodiment. Is formed. Accordingly, the downstream side refrigerant communication passage 752d in FIG. 36B is configured by the refrigerant flow portion 911g of the first plate member 911, the through hole 912d of the second plate member 912, and the through hole 913d of the third plate member 913. ing.
- the flow path resistance between the refrigerant space 771 on the refrigerant tube inlet side and the upstream refrigerant tube group 16b is mainly the length of the refrigerant flow path. Due to the difference, the flow path resistance between the refrigerant space 771 on the refrigerant tube inlet side and the downstream refrigerant tube group 16c is smaller.
- the flow path resistance of the refrigerant flow path increases as the flow path length increases, but decreases as the flow path opening area increases. For example, in FIG. 39, the flow path length and the open area are adjusted.
- the flow path resistance of the upstream side refrigerant communication passage 752a and the downstream side refrigerant communication passages 752b and 752d are adjusted.
- the flow path resistance between the refrigerant space 771 on the refrigerant tube inlet side and the upstream refrigerant tube group 16b is also determined by the difference in the opening area (flow channel cross-sectional area) of the refrigerant flow channel.
- the configuration of the header tank 75 disposed on one end side in the longitudinal direction of the refrigerant tube 16a is the same as that in the first embodiment. That is, as shown in FIG. However, the header tank 75 arranged on the other end side in the longitudinal direction of the refrigerant tube 16a (upper side in FIG. 5) is configured as shown in FIG. In FIG. 40, the flow of the refrigerant is indicated by thick solid arrows, and the flow of the coolant is indicated by thick broken arrows.
- the intermediate plate member 752 includes a first plate member 931 and a second plate member 932 in order from the side closer to the upstream heat exchange unit 71 and the downstream heat exchange unit 72 (the lower side in FIG. 40). Are stacked in the plate thickness direction and joined together.
- a through hole 931a is formed in the first plate member 931 at a portion in the header tank 75 where the refrigerant tubes 16a overlap each other when viewed from the outside air flow direction X in the upstream heat exchange unit 71 and the downstream heat exchange unit 72. Is formed. And the through-hole 931a is formed in the 1st plate member 931 so that the site
- a through hole 932a is formed in the second plate member 932, and the through hole 912a communicates with the through hole 931a of the first plate member 931. Further, the through hole 932 a of the second plate member 932 communicates with the coolant space 77 without communicating with the coolant space 76.
- the upstream side refrigerant communication passage 752a and the downstream side refrigerant communication passage 752b are configured by the through hole 931a of the first plate member 931 and the through hole 932a of the second plate member 932.
- two through holes 931b, 931 c is formed in the first plate member 931 side by side from the upstream side in the outside air flow direction X.
- One through hole 931 b communicates with the coolant tube 43 a of the upstream heat exchange section 71
- the other through hole 931 c communicates with the refrigerant tube 16 a of the downstream heat exchange section 72.
- the second plate member 932 has two through holes 932b and 932c formed side by side from the upstream side in the outside air flow direction X.
- One through hole 932 b communicates with one through hole 931 b of the first plate member 931 and also communicates with the cooling liquid space 76, but does not communicate with the refrigerant space 77.
- the other through hole 932 c communicates with the other through hole 931 c of the first plate member 931 and communicates with the refrigerant space 77, but does not communicate with the coolant space 76.
- the upstream side coolant communication path 752c is configured by the through hole 931b of the first plate member 931 and the through hole 932b of the second plate member 932.
- the downstream side refrigerant communication path 752d is configured by the through hole 931c of the first plate member 931 and the through hole 932c of the second plate member 932.
- the refrigerant space 77 shown in FIG. 40 is a refrigerant space 772 on the refrigerant tube outlet side connected to the outlet side of the refrigerant tube 16a and collecting refrigerant.
- the refrigerant space 772 on the refrigerant tube outlet side is arranged on the downstream refrigerant tube group 16c side in the outside air flow direction X with respect to the upstream refrigerant tube group 16b.
- the refrigerant space 772 on the refrigerant tube outlet side is formed in the second downstream tank portion 740b.
- the refrigerant can easily flow into the refrigerant space 772 on the refrigerant tube outlet side. It is easy to configure the header tank 75.
- the header tank 75 can be comprised so that a refrigerant
- FIG. 41 is an overall configuration diagram showing the refrigerant flow path and the like during the waste heat recovery operation in the present embodiment.
- the refrigerant flow in the heat pump cycle 10 is shown by a solid line, and the coolant flow in the coolant circulation circuit 40 is shown. Is indicated by a dashed arrow.
- the indoor condenser 12 of the first embodiment is abolished, and the composite heat exchanger 70 of the first embodiment is arranged in the casing 31 of the indoor air conditioning unit 30. Yes. And among this heat exchanger 70, the outdoor heat exchange part 16 of 1st Embodiment is functioned as the indoor condenser 12.
- FIG. hereinafter, a part of the heat exchanger 70 that functions as the indoor condenser 12 is referred to as an indoor condenser.
- the outdoor heat exchange unit 16 is configured as a single heat exchanger that exchanges heat between the refrigerant circulating inside and the outside air blown from the blower fan 17.
- Other configurations are the same as those of the first embodiment.
- the defrosting operation is not executed, but the other operations are the same as those in the first embodiment.
- the air blown into the vehicle interior is heated by exchanging heat with the refrigerant discharged from the compressor 11 in the indoor condensing part of the heat exchanger 70 and further heated in the indoor condensing part.
- the air blown into the passenger compartment can be heated by exchanging heat with the coolant in the radiator 43 of the heat exchanger 70.
- the heat exchange between the coolant and the air blown into the vehicle interior can be performed, so that the operation of the heat pump cycle 10 (specifically, the compressor 11) is stopped. Even in such a case, heating of the passenger compartment can be realized. Moreover, even when the temperature of the refrigerant discharged from the compressor 11 is low and the heating capacity of the heat pump cycle 10 is low, heating of the passenger compartment can be realized.
- the refrigerant condensing (liquefaction) in the refrigerant tube 16a in the indoor condensing part is impaired and the refrigerant flows in a gas phase state.
- the pressure loss increases, and as a result, the refrigerant distribution 16a of the upstream heat exchanging portion 71 and the refrigerant tube 16a of the downstream heat exchanging portion 72 are likely to be biased in the distribution of the refrigerant.
- the refrigerant tube 16a of the upstream heat exchange unit 71 and the refrigerant of the downstream heat exchange unit 72 are used. It is possible to appropriately adjust the refrigerant distribution by eliminating the influence of the difference in pressure loss with the tube 16a.
- heat exchanger 70 described in the second to twenty-sixth embodiments may be applied to the heat pump cycle 10 of the present embodiment.
- the upstream number ratio and the downstream number ratio may be the same. That is, the upstream heat exchanging portion 71 and the downstream heat exchanging portion 72 are configured such that the refrigerant tubes 16a overlap with each other in the outside air flow direction X, and the refrigerant tube 16a and the coolant tube in the outside air flow direction X. What is necessary is just to be comprised so that both of the site
- the coolant tubes 43a may be arranged every two refrigerant tubes 16a. That is, in the upstream heat exchange section 71, two refrigerant tubes 16a may be disposed between the adjacent coolant tubes 43a.
- the upstream number ratio can be increased. Therefore, in the upstream heat exchange section 71, the amount of heat exchange between the refrigerant and the outside air can be ensured more reliably.
- the refrigerant of the heat pump cycle 10 is employed as the first fluid
- the coolant of the coolant circulation circuit 40 is employed as the second fluid
- the blower fan 17 serves as the third fluid.
- the 1st-3rd fluid is not limited to this.
- vehicle interior air may be employed as the third fluid.
- the first fluid may be a high-pressure side refrigerant of the heat pump cycle 10 or a low-pressure side refrigerant.
- the second fluid may employ a coolant that cools an electric device such as an inverter that supplies electric power to the engine and the traveling electric motor MG.
- the oil for cooling may be employ
- a 2nd heat exchange part may be functioned as an oil cooler, and a heat storage agent, a cool storage agent, etc. may be employ
- the heat pump cycle 10 to which the heat exchanger 70 of the present disclosure is applied is applied to a stationary air conditioner, a cold storage, a vending machine cooling heating device, etc.
- the heat pump cycle 10 is compressed as the second fluid.
- the example in which the heat exchanger 70 of the present disclosure is applied to the heat pump cycle (refrigeration cycle) has been described, but the application of the heat exchanger 70 of the present disclosure is not limited to this. That is, the present invention can be widely applied to devices that exchange heat between three types of fluids.
- the first fluid is a heat medium that absorbs the heat amount of the first in-vehicle device that generates heat during operation
- the second fluid is a heat medium that absorbs the heat amount of the second in-vehicle device that generates heat during operation
- the third fluid may be outdoor air.
- the first in-vehicle device is an engine EG
- the first fluid is a coolant for the engine EG
- the second in-vehicle device is a traveling electric motor
- the second fluid is It is good also as a cooling fluid of the electric motor for driving
- the temperature of the coolant of the engine EG and the temperature of the coolant of the running electric motor also change depending on the running state of the vehicle. Therefore, according to this example, it is possible to dissipate the heat generated in the in-vehicle device having a large calorific value not only to the air but also to the in-vehicle device side having a small calorific value.
- the three types of fluids not only mean fluids having different physical properties and components, but also fluids having the same physical properties and components but having different fluid states such as temperature, gas phase, and liquid phase. Meaning included. Therefore, the first to third fluids in the present disclosure are not limited to fluids having different physical properties and components.
- the circuit switching unit is not limited thereto.
- a thermostat valve may be employed.
- the thermostat valve is a cooling medium temperature responsive valve configured by a mechanical mechanism that opens and closes a cooling medium passage by displacing a valve body by a thermo wax (temperature-sensitive member) whose volume changes with temperature. Therefore, the coolant temperature sensor 52 can be abolished by adopting a thermostat valve.
- the type of refrigerant is not limited to this.
- Natural refrigerants such as carbon dioxide, hydrocarbon refrigerants, and the like may be employed.
- the heat pump cycle 10 may constitute a supercritical refrigeration cycle in which the refrigerant discharged from the compressor 11 is equal to or higher than the critical pressure of the refrigerant.
- the flow path configuration of the heat exchanger 70 is not limited to the configuration shown in FIG. 6 and FIGS. 26 to 35, and the flow path configuration of the heat exchanger 70 can be variously changed.
- a U-turn type in which the refrigerant flow makes a U-turn between the tube group on one side and the tube group on the other side an S-turn type in which the refrigerant flow makes a U-turn twice
- an all-pass type in which the refrigerant flow does not make a U-turn The flow path configuration can be adopted.
- a flow path configuration such as a U-turn type, an S-turn type, or an all-pass type can be adopted for the coolant flow.
- a flow path configuration such as a parallel flow type in which the refrigerant flow direction and the coolant flow direction are the same, and a counter flow type in which the refrigerant flow direction and the coolant flow direction are opposite.
- the refrigerant flow in the refrigerant tube 16a is U-turned from the downstream side in the external air flow direction X to the upstream side in the external air flow direction X, and the flow of the cooling liquid in the cooling liquid tube 43a is changed to the external air flow direction.
- the refrigerant flowing through the adjacent refrigerant tubes 16a and the flow of the cooling liquid flowing through the cooling liquid tubes 43a are viewed macroscopically from the upstream side of X to the downstream side in the flow direction X of the outside air.
- the flow may be in the direction opposite to the flow direction X of the outside air (counter flow).
- the reason for the difference in pressure loss between the refrigerant tube 16a of the upstream heat exchange unit 71 and the refrigerant tube 16a of the downstream heat exchange unit 72 is that of the upstream heat exchange unit 71.
- the state of the refrigerant flowing through the refrigerant tube 16a is different from the state of the refrigerant flowing through the refrigerant tube 16a of the downstream heat exchange unit 72
- the difference in the pressure loss is related to the upstream heat exchange unit 71.
- the refrigerant tube 16a and the refrigerant tube 16a of the downstream heat exchanging portion 72 may have different structures (shape, overall length, flow path area, etc., in other words, flow path resistance).
- FIG. 40 of the above-described twenty-sixth embodiment two through holes 932a and 932c communicating with the refrigerant space 77 are independently formed in the second plate member 932, but the through holes 932a, 932c may be replaced with a large through-hole in which a plurality of through-holes 932a and 932c are connected.
- the through holes 932a and 932c of the second plate member 932 in FIG. 40 may be replaced with through holes 932d and 932e including a plurality of the through holes 932a and 932c.
- the entire opening 752e of the upstream refrigerant communication passage 752a is provided so as to overlap the opening end face 16d in a direction perpendicular to the opening end face 16d of the refrigerant tube 16a.
- the heat exchanger 70 has three refrigerant paths 161a, 161b, and 161c, but there may be four or more refrigerant paths.
- the first relationship that the flow resistance of the upstream refrigerant communication passage 752a is smaller than the flow resistance of the downstream refrigerant communication passage 752b, and the upstream refrigerant tube group 16b.
- the second relationship that the flow path resistance between the refrigerant space 77 and the refrigerant space 77 is smaller than the flow path resistance between the downstream refrigerant tube group 16c and the one refrigerant space 77. Both are established, but regarding the flow path resistance, one of the first and second relationships may be established, and the other may not be established. Note that the present disclosure is not limited to the above-described embodiment, and can be modified as appropriate.
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Abstract
Description
(第1実施形態)
第1実施形態を図1~図9に基づいて説明する。本実施形態では、熱交換器70を、車両用空調装置1において車室内送風空気の温調を行うヒートポンプサイクル10に適用している。図1~図3は、本第1実施形態の車両用空調装置1の全体構成図である。
暖房運転は、操作パネルの作動スイッチが投入(ON)された状態で、選択スイッチによって暖房運転モードが選択されると開始される。そして、暖房運転時に、着霜判定手段によって室外熱交換部16の着霜が生じていると判定された際には除霜運転が実行される。
次に、除霜運転について説明する。ここで、本実施形態のヒートポンプサイクル10のように、室外熱交換部16にて冷媒と外気とを熱交換させて冷媒を蒸発させる冷凍サイクル装置では、室外熱交換部16における冷媒蒸発温度が着霜温度(具体的には、0℃)以下になってしまうと室外熱交換部16に着霜が生じるおそれがある。
冷房運転は、操作パネルの作動スイッチが投入(ON)された状態で、選択スイッチによって冷房運転モードが選択されると開始される。この冷房運転時には、空調制御装置が、開閉弁15aを開くとともに、三方弁15bを室外熱交換部16の出口側と冷房用固定絞り19の入口側とを接続する冷媒流路に切り替える。これにより、ヒートポンプサイクル10は、図3の実線矢印に示すように冷媒が流れる冷媒流路に切り替えられる。
(第2実施形態)
上記第1実施形態では、上流側冷媒連通路752aが下流側冷媒連通路752bに比べて直線的に形成されていることによって、上流側冷媒連通路752aの流路抵抗を下流側冷媒連通路752bの流路抵抗よりも小さくしているが、本第2実施形態では、図10に示すように、上流側冷媒連通路752aの流路面積が下流側冷媒連通路752bの流路面積よりも大きくなっていることによって、上流側冷媒連通路752aの流路抵抗を下流側冷媒連通路752bの流路抵抗よりも小さくしている。
(第3実施形態)
上記第1、第2実施形態では、上流側冷媒連通路752aの流路抵抗を下流側冷媒連通路752bの流路抵抗よりも小さくすることによって、上流側熱交換部71の第1チューブ16aと冷媒用空間77との間の流路抵抗を下流側熱交換部72の第1チューブ16aと冷媒用空間77との間の流路抵抗よりも小さくしているが、本第3実施形態では、図11に示すように、上記第1、第2実施形態に対して冷却液用空間76と冷媒用空間77の配置を逆にすることによって、上流側熱交換部71の第1チューブ16aと冷媒用空間77との間の流路抵抗を下流側熱交換部72の第1チューブ16aと冷媒用空間77との間の流路抵抗よりも小さくしている。
(第4実施形態)
上記第3実施形態では、中間プレート部材752を4枚のプレート部材821~824の積層によって構成しているが、本第4実施形態では、図13に示すように、中間プレート部材752を2枚のプレート部材831、832の積層によって構成している。
(第5実施形態)
上記第4実施形態では、中間プレート部材752を2枚のプレート部材831、832の積層によって構成しているが、本第5実施形態では、図15に示すように、中間プレート部材752を3枚のプレート部材841、842、843の積層によって構成している。
(第6実施形態)
本第6実施形態では、図16に示すように、冷媒用チューブ16aおよび冷却液用チューブ43aの長手方向一端側(図16の下側)では冷媒用空間77を冷却液用空間76よりも外気の流れ方向Xの上流側に配置し、冷媒用チューブ16aおよび冷却液用チューブ43aの長手方向他端側(図16の上側)では冷媒用空間77を冷却液用空間76よりも外気の流れ方向Xの下流側に配置している。換言すれば、2つの冷媒用空間77を対角配置している。
(第7実施形態)
本第7実施形態では、図17に示すように、冷媒用空間77を、上流側熱交換部71の冷媒用チューブ16aと下流側熱交換部72の冷媒用チューブ16aとから等距離にある仮想直線CLと重なり合う位置に配置することによって、上流側熱交換部71の冷媒用チューブ16aと下流側熱交換部72の冷媒用チューブ16aとに対する冷媒の分配性を適切化している。
(第8実施形態)
上記第7実施形態では、冷媒用空間77は、外気の流れ方向Xにおける幅寸法が冷却液用空間76よりも大きく形成されているが、本第8実施形態では、図18に示すように、冷媒用空間77は、外気の流れ方向Xにおける幅寸法が冷却液用空間76と同等に形成されている。
(第9実施形態)
上記第8実施形態では、冷媒用空間77は、冷却液用空間76よりも外気の流れ方向Xの下流側かつ仮想直線CLと重なり合う位置に配置されているが、本第9実施形態では、図19に示すように、冷媒用空間77は、冷却液用空間76よりも外気の流れ方向Xの上流側に配置され、冷却液用空間76が仮想直線CLと重なり合う位置に配置されている。
(第10実施形態)
本第10実施形態では、図20に示すように、上記第9実施形態において空間Sが形成されている領域に第2の冷媒用空間78(第3タンク空間)を形成している。
(第11実施形態)
本第11実施形態では、図21に示すように、上記第10実施形態に対して、第1の冷媒用空間77と冷却液用空間76の配置を逆にしている。
(第12実施形態)
本第12実施形態では、図22に示すように、上記第11実施形態に対して、タンク内連通路91が廃止され、コネクタ92には、その内部空間921を第2の冷媒用空間78と連通させる第2のコネクタ連通路923が形成されている。
(第13実施形態)
本第13実施形態は、上記第12実施形態とは異なり、図23~25に示すように、第1の冷媒用空間77が、冷却液用空間76及び第2の冷媒用空間78を形成するタンク形成部材753とは別のタンク形成部材753d、753eにより形成されている。本実施形態では、便宜上、タンク形成部材753を第1タンク形成部材753と呼び、タンク形成部材753dを第2タンク形成部材753dと呼び、タンク形成部材753eを第3タンク形成部材753eと呼ぶものとする。本実施形態の熱交換器70において、図23はヘッダタンク75の分解斜視図であり、図24は図22(a)に相当する断面図であり、図25は図22(b)に相当する断面図である。
(第14実施形態)
本第14実施形態は、上記第1実施形態に対して、熱交換器70の流路構成を変更したものである。図26は、本実施形態の熱交換器70における冷媒流れおよび冷却液流れを説明するための模式的な斜視図である。
(第15実施形態)
本第15実施形態は、上述した第1、第14実施形態に対して、熱交換器70の流路構成を変更したものである。図27は、本実施形態の熱交換器70における冷媒流れを説明するための模式的な斜視図である。図27では熱交換器70内の冷媒流れが太い実線矢印で示されており、後述する図28~35でも同様である。
(第16実施形態)
本第16実施形態は、上述した第1、第14、第15実施形態に対して、熱交換器70の流路構成を変更したものである。図28は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第17実施形態)
本第17実施形態は、上述した第1、第14~16実施形態に対して、熱交換器70の流路構成を変更したものである。図29は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第18実施形態)
本第18実施形態は、上述した第1、第14~17実施形態に対して、熱交換器70の流路構成を変更したものである。図30は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第19実施形態)
本第19実施形態は、上述した第1、第14~18実施形態に対して、熱交換器70の流路構成を変更したものである。図31は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第20実施形態)
本第20実施形態は、上述した第1、第14~19実施形態に対して、熱交換器70の流路構成を変更したものである。図32は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第21実施形態)
本第21実施形態は、上述した第1、第14~20実施形態に対して、熱交換器70の流路構成を変更したものである。図33は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第22実施形態)
本第22実施形態は、上述した第1、第14~21実施形態に対して、熱交換器70の流路構成を変更したものである。図34は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第23実施形態)
本第23実施形態は、上述した第1、第14~22実施形態に対して、熱交換器70の流路構成を変更したものである。図35は、本実施形態の熱交換器70における冷媒流れ説明するための模式的な斜視図である。
(第24実施形態)
本実施形態では、前述した第18実施形態の図30において、第2上流側タンク部730bおよび第2下流側タンク部740bの構成が図36のようになっている。例えば、図36は図30のG部分のタンク断面図を表している。図36(a)は図13(a)に対応する断面図であり、図36(b)は図13(b)に対応する断面図であるが、図36(a)(b)はそれぞれ図13(a)(b)に対して上下方向が逆になっている。
空間771と上流側冷媒用チューブ群16bとを互いに連通させる上流側冷媒連通路752aの開口部752eは、上流側冷媒用チューブ群16bに含まれる冷媒用チューブ16aに向けて開口している。更に、その上流側冷媒連通路752aの開口部752eは、冷媒用チューブ16aの開口端面16dに垂直な方向にその開口端面16dと重ねて設けられている。すなわち、その上流側冷媒連通路752aは、その冷媒用チューブ16aの開口端面16dに対向するように開口している。これにより、冷媒用チューブ入口側の冷媒用空間771を流れる冷媒の動圧を利用して、高圧損側である上流側冷媒用チューブ群16bへ冷媒を勢いよく流入させることができる。そのため、例えば、冷媒が下流側冷媒用チューブ群16cへ偏って多く流れることを抑制することが可能である。
すように、上流側冷媒連通路752aの開口部752eは、冷媒用チューブ16aの開口端面16dに垂直な方向にその開口端面16dと重ねて設けられていないことになる。
(第25実施形態)
本実施形態では、前述した第24実施形態における第2上流側タンク部730bおよび第2下流側タンク部740bの構成が、図36(a)に替えて図39のようになっている。本実施形態において、図36(b)に相当する断面図は第24実施形態と同じであるので、その図示を省略する。但し、図36(b)に示される冷媒流通部911aは冷媒流通部911gに読み替えて、図36(b)が用いられる。
(第26実施形態)
本実施形態において、冷媒用チューブ16aの長手方向一端側(図5の下側)に配置されているヘッダタンク75の構成は前述の第1実施形態と同じである。すなわち、図9の通りである。しかし、冷媒用チューブ16aの長手方向他端側(図5の上側)に配置されているヘッダタンク75は、図40のように構成されている。なお、図40では、冷媒の流れは太い実線矢印で示されており、冷却液の流れは太い破線矢印で示されている。
(第27実施形態)
本実施形態では、図41の全体構成図に示すように、第1実施形態に対して、ヒートポンプサイクル10の構成を変更した例を説明する。なお、図41は、本実施形態における廃熱回収運転時の冷媒流路等を示す全体構成図であり、ヒートポンプサイクル10における冷媒の流れを実線で示し、冷却液循環回路40における冷却液の流れを破線矢印で示している。
なお、本開示は上記した実施形態に限定されるものではなく、適宜変更が可能である。また、上記各実施形態は、互いに無関係なものではなく、組み合わせが明らかに不可な場合を除き、適宜組み合わせが可能である。また、上記各実施形態において、実施形態を構成する要素は、特に必須であると明示した場合および原理的に明らかに必須であると考えられる場合等を除き、必ずしも必須のものではないことは言うまでもない。また、上記各実施形態において、実施形態の構成要素の個数、数値、量、範囲等の数値が言及されている場合、特に必須であると明示した場合および原理的に明らかに特定の数に限定される場合等を除き、その特定の数に限定されるものではない。また、上記各実施形態において、構成要素等の形状、位置関係等に言及するときは、特に明示した場合および原理的に特定の形状、位置関係等に限定される場合等を除き、その形状、位置関係等に限定されるものではない。
Claims (22)
- 第1流体が流通する複数本の第1チューブ(16a)、および第2流体が流通する複数本の第2チューブ(43a)が積層配置され、前記第1流体および前記第2流体と第3流体とを熱交換させる熱交換部(71、72)と、
前記第1チューブ(16a)と連通して前記第1流体の前記第1チューブ(16a)からの集合あるいは前記第1チューブ(16a)への分配を行う第1タンク空間(77)、および前記第2チューブ(43a)と連通して前記第2流体の前記第2チューブ(43a)からの集合あるいは前記第2チューブ(43a)への分配を行う第2タンク空間(76)を有するタンク部(75)と、
前記第1チューブ(16a)および前記第2チューブ(43a)のうち隣り合うチューブ(16a、43a)間に形成され、前記第3流体が流通する第3流体用通路(70a)と、
前記第3流体用通路(70a)に配置され、前記第1流体と前記第3流体との熱交換および前記第2流体と前記第3流体との熱交換を促進するとともに、前記第1チューブ(16a)を流通する前記第1流体と前記第2チューブ(43a)を流通する前記第2流体との間の熱移動を可能とするアウターフィン(50)とを備え、
前記熱交換部(71、72)は、上流側熱交換部(71)と、前記上流側熱交換部(71)に対して前記第3流体の流れ方向(X)の下流側に配置される下流側熱交換部(72)とを有し、
前記第1チューブ(16a)は、前記上流側熱交換部(71)および前記下流側熱交換部(72)の双方に配置され、
前記第2チューブ(43a)は、前記上流側熱交換部(71)および前記下流側熱交換部(72)のうち少なくとも一方に配置され、
前記上流側熱交換部(71)および前記下流側熱交換部(72)は、前記第3流体の流れ方向(X)において前記第1チューブ(16a)同士が重なっている部位、および前記第3流体の流れ方向(X)において前記第1チューブ(16a)と前記第2チューブ(43a)とが重なっている部位の両方が存在するように配置され、
前記タンク部(75)は、前記第1タンク空間(77)および前記第2タンク空間(76)を前記第1、第2チューブ(16a、43a)側から閉塞するように配置されたプレート部材(752)を有し、
前記プレート部材(752)には、前記第1タンク空間(77)と前記第1チューブ(16a)とを連通させる第1流体用連通路(752a、752b、752d)、および前記第2タンク空間(76)と前記第2チューブ(43a)とを連通させる第2流体用連通路(752c)が貫通孔によって形成され、
前記上流側熱交換部(71)の複数本の前記第1チューブ(16a)は上流側第1チューブ群(16b)であり、前記下流側熱交換部(72)の複数本の前記第1チューブ(16a)は下流側第1チューブ群(16c)であり、
前記上流側第1チューブ群(16b)と前記下流側第1チューブ群(16c)のうち前記第1流体の圧力損失が大きくなる方を高圧損側第1チューブ群とし、
前記上流側第1チューブ群(16b)と前記下流側第1チューブ群(16c)のうち前記第1流体の圧力損失が小さくなる方を低圧損側第1チューブ群とし、
前記高圧損側第1チューブ群と前記第1タンク空間(77)との間の流路抵抗が、前記低圧損側第1チューブ群と前記第1タンク空間(77)との間の流路抵抗よりも小さくなっている熱交換器。 - 前記第1タンク空間(77)は、前記第1チューブ(16a)の入口側に接続され前記第1流体の分配を行う入口側第1タンク空間(771)と、前記第1チューブ(16a)の出口側に接続され前記第1流体の集合を行う出口側第1タンク空間(772)とから構成され、
前記高圧損側第1チューブ群と前記入口側第1タンク空間(771)との間の流路抵抗は、前記低圧損側第1チューブ群と前記入口側第1タンク空間(771)との間の流路抵抗よりも小さくなっており、
前記入口側第1タンク空間(771)は、前記第3流体の流れ方向(X)において、前記低圧損側第1チューブ群よりも前記高圧損側第1チューブ群に近くなるように配置され、
前記第1流体用連通路(752a、752b、752d)のうち前記入口側第1タンク空間(771)と前記高圧損側第1チューブ群とを連通させる連通路の前記第1チューブ(16a)に向けて開口する開口部(752e)は、その少なくとも一部が前記第1チューブ(16a)の開口端面(16d)に垂直な方向に該開口端面(16d)と重ねて設けられている請求項1に記載の熱交換器。 - 前記第1チューブ(16a)は、該第1チューブ(16a)内を流通する前記第1流体が重力方向の流速成分を有するように配置されるものであり、
前記第1流体は冷媒であり、
前記入口側第1タンク空間(771)へは、前記熱交換部(71、72)にて前記第3流体と少なくとも1回は熱交換した前記第1流体が導入され、
前記入口側第1タンク空間(771)は、前記高圧損側第1チューブ群(16b)の上に配置される請求項2に記載の熱交換器。 - 第1流体が流通する複数本の第1チューブ(16a)、および第2流体が流通する複数本の第2チューブ(43a)が積層配置され、前記第1流体および前記第2流体と第3流体とを熱交換させる熱交換部(71、72)と、
前記第1チューブ(16a)と連通して前記第1流体の前記第1チューブ(16a)からの集合あるいは前記第1チューブ(16a)への分配を行う第1タンク空間(77)、および前記第2チューブ(43a)と連通して前記第2流体の前記第2チューブ(43a)からの集合あるいは前記第2チューブ(43a)への分配を行う第2タンク空間(76)を有するタンク部(75)と、
前記第1チューブ(16a)および前記第2チューブ(43a)のうち隣り合うチューブ(16a、43a)間に形成され、前記第3流体が流通する第3流体用通路(70a)と、
前記第3流体用通路(70a)に配置され、前記第1流体と前記第3流体との熱交換および前記第2流体と前記第3流体との熱交換を促進するとともに、前記第1チューブ(16a)を流通する前記第1流体と前記第2チューブ(43a)を流通する前記第2流体との間の熱移動を可能とするアウターフィン(50)とを備え、
前記熱交換部(71、72)は、上流側熱交換部(71)と、前記上流側熱交換部(71)に対して前記第3流体の流れ方向(X)の下流側に配置される下流側熱交換部(72)とを有し、
前記第1チューブ(16a)は、前記上流側熱交換部(71)および前記下流側熱交換部(72)の双方に配置され、
前記第2チューブ(43a)は、前記上流側熱交換部(71)および前記下流側熱交換部(72)のうち少なくとも一方に配置され、
前記上流側熱交換部(71)および前記下流側熱交換部(72)は、前記第3流体の流れ方向(X)において前記第1チューブ(16a)同士が重なっている部位、および前記第3流体の流れ方向(X)において前記第1チューブ(16a)と前記第2チューブ(43a)とが重なっている部位の両方が存在するように配置され、
前記タンク部(75)は、前記第1タンク空間(77)および前記第2タンク空間(76)を前記第1、第2チューブ(16a、43a)側から閉塞するように配置されたプレート部材(752)を有し、
前記プレート部材(752)には、前記第1タンク空間(77)と前記第1チューブ(16a)とを連通させる第1流体用連通路(752a、752b、752d)、および前記第2タンク空間(76)と前記第2チューブ(43a)とを連通させる第2流体用連通路(752c)が貫通孔によって形成され、
前記上流側熱交換部(71)の前記第1チューブ(16a)および前記下流側熱交換部(72)の前記第1チューブ(16a)のうち、前記第1流体の圧力損失が大きくなる方の第1チューブ(16a)を高圧損側第1チューブとし、前記第1流体の圧力損失が小さくなる方の第1チューブ(16a)を低圧損側第1チューブとし、
前記高圧損側第1チューブと前記第1タンク空間(77)との間の流路抵抗が、前記低圧損側第1チューブと前記第1タンク空間(77)との間の流路抵抗よりも小さくなっている熱交換器。 - 前記上流側熱交換部(71)を構成する前記第1チューブ(16a)および前記第2チューブ(43a)の総チューブ本数に対する前記第1チューブ(16a)の本数割合と、前記下流側熱交換部(72)を構成する前記第1チューブ(16a)および前記第2チューブ(43a)の総チューブ本数に対する前記第1チューブ(16a)の本数割合とが異なっている請求項4に記載の熱交換器。
- 前記第1タンク空間(77)および前記第2タンク空間(76)は、前記第1チューブ(16a)および前記第2チューブ(43a)の積層方向に延びて形成され、前記第3流体の流れ方向(X)に互いに並んで配置され、
前記第1タンク空間(77)は、前記第3流体の流れ方向(X)において、前記高圧損側第1チューブよりも前記低圧損側第1チューブに近い側に配置され、
前記第2タンク空間(76)は、前記第3流体の流れ方向(X)において、前記低圧損側第1チューブよりも前記高圧損側第1チューブに近い側に配置され、
前記プレート部材(752)には、前記第1流体用連通路(752a、752b、752d)として、前記高圧損側第1チューブと前記第1タンク空間(77)とを連通させる高圧損側連通路、および前記低圧損側第1チューブと前記第1タンク空間(77)とを連通させる低圧損側連通路が形成され、
前記高圧損側連通路の流路抵抗が前記低圧損側連通路の流路抵抗よりも小さくなっていることによって、前記高圧損側第1チューブと前記第1タンク空間(77)との間の流路抵抗が、前記低圧損側第1チューブと前記第1タンク空間(77)との間の流路抵抗よりも小さくなっている請求項4または5に記載の熱交換器。 - 前記プレート部材(752)には、前記高圧損側連通路を構成する貫通孔(812a)と、前記低圧損側連通路を構成する貫通孔(812b)とが形成され、
前記高圧損側連通路を構成する貫通孔(812a)の孔面積が前記低圧損側連通路を構成する貫通孔(812b)の孔面積よりも大きくなっていることによって、前記高圧損側連通路の流路抵抗が前記低圧損側連通路の流路抵抗よりも小さくなっている請求項6に記載の熱交換器。 - 前記第1タンク空間(77)および前記第2タンク空間(76)は、前記第1チューブ(16a)および前記第2チューブ(43a)の積層方向に延びて形成され、前記第3流体の流れ方向(X)に互いに並んで配置され、
前記第1タンク空間(77)が前記第3流体の流れ方向(X)において前記低圧損側第1チューブよりも前記高圧損側第1チューブに近い側に配置され、且つ前記第2タンク空間(76)が前記第3流体の流れ方向(X)において前記高圧損側第1チューブよりも前記低圧損側第1チューブに近い側に配置されていることによって、前記高圧損側第1チューブと前記第1タンク空間(77)との間の流路抵抗が、前記低圧損側第1チューブと前記第1タンク空間(77)との間の流路抵抗よりも小さくなっている請求項4または5に記載の熱交換器。 - 第1流体が流通する複数本の第1チューブ(16a)、および第2流体が流通する複数本の第2チューブ(43a)が積層配置され、前記第1流体および前記第2流体と第3流体とを熱交換させる熱交換部(71、72)と、
前記第1チューブ(16a)と連通して前記第1流体の前記第1チューブ(16a)からの集合あるいは前記第1チューブ(16a)への分配を行う第1タンク空間(77)、および前記第2チューブ(43a)と連通して前記第2流体の前記第2チューブ(43a)からの集合あるいは前記第2チューブ(43a)への分配を行う第2タンク空間(76)を有するタンク部(75)と、
前記第1チューブ(16a)および前記第2チューブ(43a)のうち隣り合うチューブ(16a、43a)間に形成され、前記第3流体が流通する第3流体用通路(70a)と、
前記第3流体用通路(70a)に配置され、前記第1流体と前記第3流体との熱交換および前記第2流体と前記第3流体との熱交換を促進するとともに、前記第1チューブ(16a)を流通する前記第1流体と前記第2チューブ(43a)を流通する前記第2流体との間の熱移動を可能とするアウターフィン(50)とを備え、
前記熱交換部(71、72)は、上流側熱交換部(71)と、前記上流側熱交換部(71)に対して前記第3流体の流れ方向(X)の下流側に配置される下流側熱交換部(72)とを有し、
前記第1チューブ(16a)は、前記上流側熱交換部(71)および前記下流側熱交換部(72)の双方に配置され、
前記第2チューブ(43a)は、前記上流側熱交換部(71)および前記下流側熱交換部(72)のうち少なくとも一方に配置され、
前記上流側熱交換部(71)および前記下流側熱交換部(72)は、前記第3流体の流れ方向(X)において前記第1チューブ(16a)同士が重なっている部位、および前記第3流体の流れ方向(X)において前記第1チューブ(16a)と前記第2チューブ(43a)とが重なっている部位の両方が存在するように配置され、
前記第1タンク空間(77)および前記第2タンク空間(76)は、前記第1チューブ(16a)および前記第2チューブ(43a)の積層方向に延びて形成され、前記第3流体の流れ方向(X)に互いに並んで配置され、
前記第1タンク空間(77)は、前記第3流体の流れ方向(X)における位置が、前記上流側熱交換部(71)の前記第1チューブ(16a)と前記下流側熱交換部(72)の前記第1チューブ(16a)とから等距離にある仮想直線(CL)と重なり合う位置となるように配置されており、
前記上流側熱交換部(71)を構成する前記第1チューブ(16a)および前記第2チューブ(43a)の総チューブ本数に対して該上流側熱交換部(71)の第1チューブ(16a)が占めるチューブ本数割合と、前記下流側熱交換部(72)を構成する前記第1チューブ(16a)および前記第2チューブ(43a)の総チューブ本数に対して該下流側熱交換部(72)の第1チューブ(16a)が占めるチューブ本数割合とが異なっている熱交換器。 - 前記第1タンク空間(77)は、前記第1チューブ(16a)の入口側に接続され前記第1流体の分配を行う入口側第1タンク空間(771)と、前記第1チューブ(16a)の出口側に接続され前記第1流体の集合を行う出口側第1タンク空間(772)とから構成され、
前記入口側第1タンク空間(771)は、前記第3流体の流れ方向(X)における位置が、前記上流側熱交換部(71)の前記第1チューブ(16a)と前記下流側熱交換部(72)の前記第1チューブ(16a)とから等距離にある仮想直線(CL)と重なり合う位置となるように配置されており、
前記上流側熱交換部(71)の複数本の前記第1チューブ(16a)は上流側第1チューブ群(16b)であり、前記下流側熱交換部(72)の複数本の前記第1チューブ(16a)は下流側第1チューブ群(16c)であり、
前記上流側第1チューブ群(16b)と前記下流側第1チューブ群(16c)のうち前記第1流体の圧力損失が大きくなる方を高圧損側第1チューブ群とし、
前記上流側第1チューブ群(16b)と前記下流側第1チューブ群(16c)のうち前記第1流体の圧力損失が小さくなる方を低圧損側第1チューブ群とし、
前記第3流体の流れ方向(X)において、前記入口側第1タンク空間(771)は、前記低圧損側第1チューブ群よりも、前記高圧損側第1チューブ群に近くなるように配置され、
前記入口側第1タンク空間(771)と前記高圧損側第1チューブ群とを連通させる連通路(752a)の前記第1チューブ(16a)に向けて開口する開口部(752e)は、その少なくとも一部が前記第1チューブ(16a)の開口端面(16d)に垂直な方向に該開口端面(16d)と重ねて設けられており、
前記第1チューブ(16a)は、該第1チューブ(16a)内を流通する前記第1流体が重力方向の流速成分を有するように配置されるものであり、
前記第1流体は冷媒であり、
前記入口側第1タンク空間(771)へは、前記第3流体用通路(70a)にて前記第3流体と少なくとも1回は熱交換した前記第1流体が導入され、
前記入口側第1タンク空間(771)は、前記高圧損側第1チューブ群の上に配置される請求項9に記載の熱交換器。 - 前記第1流体を蒸発させる蒸発器として用いられる熱交換器であって、
前記出口側第1タンク空間(772)は、前記第3流体の流れ方向(X)において、前記高圧損側第1チューブ群よりも前記低圧損側第1チューブ群側に配置されている請求項2、3、10のいずれか1つに記載の熱交換器。 - 前記高圧損側第1チューブ群に含まれる前記第1チューブ(16a)の本数は、前記低圧損側第1チューブ群と比較して少ない請求項1、2、3、10、11のいずれか1つに記載の熱交換器。
- 前記高圧損側第1チューブ群は前記上流側第1チューブ群(16b)であり、前記低圧損側第1チューブ群は前記下流側第1チューブ群(16c)である請求項1、2、3、10、11、12のいずれか1つに記載の熱交換器。
- 前記第1タンク空間(77)は、一対をなして構成されており、
前記熱交換部(71、72)は第1流体パス(161a、161b、161c)を3つ以上有し、各第1流体パス(161a、161b、161c)は一対をなす前記第1タンク空間(77)の間に介装された1本又は2本以上の前記第1チューブ(16a)を有し、
前記第1流体パス(161a、161b、161c)は、前記第1流体の流通経路において直列的に連結にされ、各第1流体パス(161a、161b、161c)は該流通経路にて隣り合う他の第1流体パスに対し前記第1流体が重力方向において逆向きに流れるものであり、
前記第1流体パス(161a、161b、161c)は、前記第1流体が重力方向上側へ流れる上昇流第1流体パスを含み、
前記第1チューブ(16a)の積層方向における前記第1流体パス(161a、161b、161c)を構成する前記第1チューブ(16a)の積層幅について、前記上昇流第1流体パスは前記第1流体の流通経路にて隣り合う何れの第1流体パスよりも小さい請求項1ないし13のいずれか1つに記載の熱交換器。 - 前記タンク部(75)は、前記第2チューブ(43a)の積層方向に延びる第3タンク空間(78)をさらに有し、
前記第1タンク空間(77)、前記第2タンク空間(76)および前記第3タンク空間(78)は、前記第3流体の流れ方向(X)に互いに並んで配置され、
前記タンク部(75)の内部には、前記第1タンク空間(77)と前記第3タンク空間(78)とを連通するタンク内連通路(91)が形成されている請求項9または10に記載の熱交換器。 - 前記タンク部(75)の外部であって該タンク部(75)に対して前記第1チューブ(16a)および前記第2チューブ(43a)の反対側の部位には、冷媒配管接続用のコネクタ(92)をさらに備え、
前記コネクタ(92)には、該コネクタ(92)の内部空間(921)を前記第1タンク空間(77)と連通させるコネクタ連通路(922)が形成されている請求項15に記載の熱交換器。 - 前記タンク部(75)は、前記第2チューブ(43a)の積層方向に延びる第3タンク空間(78)をさらに有し、
前記第1タンク空間(77)、前記第2タンク空間(76)および前記第3タンク空間(78)は、前記第3流体の流れ方向(X)に互いに並んで配置され、
前記タンク部(75)の外部であって該タンク部(75)に対して前記第1チューブ(16a)および前記第2チューブ(43a)の反対側の部位には、冷媒配管接続用のコネクタ(92)をさらに備え、
前記コネクタ(92)には、該コネクタ(92)の内部空間(921)を前記第1タンク空間(77)と連通させる第1のコネクタ連通路(922)と、前記内部空間(921)を前記第3タンク空間(78)と連通させる第2のコネクタ連通路(923)とが形成されている請求項9または10に記載の熱交換器。 - 前記第1流体および前記第2流体は互いに異なる流体循環回路に流通する熱媒体である請求項1ないし17のいずれか1つに記載の熱交換器。
- 蒸気圧縮式の冷凍サイクルにおいて冷媒を蒸発させる蒸発器として用いられる熱交換器であって、
前記第1流体は、前記冷凍サイクルの冷媒であり、
前記第2流体は、外部熱源の有する熱量を吸熱した熱媒体であり、
前記第3流体は、空気である請求項1ないし18のいずれか1つに記載の熱交換器。 - 蒸気圧縮式の冷凍サイクルにおいて冷媒を凝縮させる凝縮器として用いられる熱交換器であって、
前記第1流体は、前記冷凍サイクルの冷媒であり、
前記第2流体は、外部熱源の有する熱量を吸熱した熱媒体であり、
前記第3流体は、空気である請求項1ないし18のいずれか1つに記載の熱交換器。 - 車両用冷却システムに適用される熱交換器であって、
前記第1流体は、作動時に発熱を伴う第1車載機器の有する熱量を吸熱した熱媒体であり、
前記第2流体は、作動時に発熱を伴う第2車載機器の有する熱量を吸熱した熱媒体であり、
前記第3流体は、空気である請求項1ないし18のいずれか1つに記載の熱交換器。 - 前記第1流体を蒸発させる蒸発器として用いられる熱交換器であって、
前記上流側熱交換部(71)に含まれる前記第2チューブ(43a)の本数は前記下流側熱交換部(72)に比して多く、
前記第1流体よりも高温である前記第2流体を前記第2チューブ(43a)及び前記第2タンク空間(76)内に流通させることにより除霜が行われる請求項1ないし19、21のいずれか1つに記載の熱交換器。
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US9410745B2 (en) | 2011-11-30 | 2016-08-09 | Denso Corporation | Heat exchanger |
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JP2014149131A (ja) * | 2013-02-01 | 2014-08-21 | Mitsubishi Electric Corp | 室外機及び冷凍サイクル装置 |
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US10414244B2 (en) * | 2015-07-08 | 2019-09-17 | Denso Corporation | Refrigeration system, and in-vehicle refrigeration system |
KR101837046B1 (ko) * | 2015-07-31 | 2018-04-19 | 엘지전자 주식회사 | 열교환기 |
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US20170241308A1 (en) * | 2016-02-24 | 2017-08-24 | Ford Global Technologies, Llc | Oil maintenance strategy for electrified vehicles |
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JP6746234B2 (ja) * | 2017-01-25 | 2020-08-26 | 日立ジョンソンコントロールズ空調株式会社 | 熱交換器、及び、空気調和機 |
JP6717256B2 (ja) * | 2017-05-10 | 2020-07-01 | 株式会社デンソー | 冷媒蒸発器およびその製造方法 |
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JP7225666B2 (ja) * | 2018-10-18 | 2023-02-21 | 日本電産株式会社 | 冷却ユニット |
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Also Published As
Publication number | Publication date |
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JP2013137184A (ja) | 2013-07-11 |
CN103959004B (zh) | 2016-03-16 |
DE112012004988T5 (de) | 2014-09-11 |
JP5796564B2 (ja) | 2015-10-21 |
US9625214B2 (en) | 2017-04-18 |
US20150241131A1 (en) | 2015-08-27 |
CN103959004A (zh) | 2014-07-30 |
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