JP2014055735A - Refrigerant radiator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerant radiator that can suppress temperature distribution of air blown out by exchanging heat with a refrigerant.SOLUTION: A refrigerant radiator includes two heat radiation parts 10, 20 disposed in series with respect to a flowing direction of blast air. In the downwind side heat radiation part 10 out of the two heat radiation parts 10, 20, a refrigerant inflow port 12b is installed in a tank part 12 disposed on the upper side, and all of a plurality of tubes 111 are configured so that a refrigerant flows from the upper side toward the lower side. A plurality of tubes 211 in the upwind side heat radiation part 20 includes: a first tube group 21a in which the refrigerant flows from the lower side toward the upper side; and a second tube group 21b in which the refrigerant flows from the upper side toward the lower side.

Description

  The present invention relates to a refrigerant radiator that dissipates heat in a vapor compression refrigeration cycle.

  2. Description of the Related Art Conventionally, there is known a refrigerant radiator that radiates heat by exchanging heat with high-temperature and high-pressure refrigerant discharged from a compressor in a vapor compression refrigeration cycle. For example, the refrigerant radiator of Patent Document 1 is applied to a vehicle air conditioner, and exchanges heat between a compressor discharge refrigerant and vehicle interior blown air that is blown into a vehicle interior that is an air conditioning target space. It functions as a heating means for heating the blown air.

  Further, this refrigerant radiator has a heat exchange region disposed on the windward side in the flow direction of the blown air and a heat exchange region disposed on the leeward side. In the heat exchange region on the leeward side, the refrigerant discharged from the compressor Is circulated from one end side to the other end side, and the leeward heat exchange region outflow refrigerant is circulated from the other end side to the one end side in the heat exchange region on the windward side.

JP 2011-230655 A

  Here, when the refrigerant radiator disclosed in Patent Document 1 is a cross-flow type heat exchanger in which the refrigerant discharged from the compressor flows in the horizontal direction, the state of the refrigerant at one end side of each of the two heat exchange regions is super. While heat or subcooling occurs, the refrigerant on the other end side of each of the two heat exchange regions is in a gas-liquid two-phase state. For this reason, when the refrigerant radiator is viewed from the flow direction of the blown air, a temperature distribution is generated in the left-right direction of the heat exchange core portion (heat exchange region).

  Further, when the refrigerant radiator described in Patent Document 1 is a downflow type heat exchanger in which the refrigerant discharged from the compressor flows in the vertical direction, one of the heat exchange area on the leeward side and the heat exchange area on the leeward side. The refrigerant flow in the heat exchange region becomes an upward flow that flows upward while the refrigerant is condensed. Liquid phase refrigerants are greatly affected by gravity due to their high density.

  Therefore, in the region where the refrigerant flow is an upward flow, the liquid-phase refrigerant must be pushed upward against gravity, and the refrigerant flow concentrates on some of the tubes constituting the heat exchange region. It becomes difficult for the refrigerant to flow through the other tubes. For this reason, when the said one heat exchange area | region is seen from the flow direction of blowing air, temperature distribution arises in the left-right direction (tube lamination direction) of a heat exchange core part.

  As described above, even if the refrigerant radiator described in Patent Document 1 is a crossflow type or a downflow type heat exchanger, a temperature distribution is generated in the left-right direction of the heat exchange core portion. . Thereby, there exists a problem that temperature distribution generate | occur | produces in the ventilation air which blows off from a refrigerant | coolant heat radiator.

  An object of this invention is to provide the refrigerant | coolant heat radiator which can suppress the temperature distribution of the air which heat-exchanges with a refrigerant | coolant and blows off in view of the said point.

  In order to achieve the above-described object, the invention according to claim 1 includes at least two heat radiating portions (10, 20) arranged in series with respect to the flow direction of the blown air, and includes at least two heat radiating portions (10, 20) Each is connected to the core part (11, 21) formed by laminating a plurality of tubes (111, 211) through which the refrigerant flows, and to both ends of the plurality of tubes (111, 211). And a pair of tank parts (12, 13, 22, 23) for collecting or distributing the refrigerant flowing through the tubes (111, 211), and the tank parts (12, 13, 22, 23) are the core parts (11). 21) are arranged at both ends in the vertical direction, and are configured such that the refrigerant flows in the vertical direction, and any one of the pair of tank portions (12, 13, 22, 23). ( 2, 23) are provided with refrigerant inlets (12b, 24) for allowing the refrigerant to flow in, and among the at least two heat radiating parts (10, 20), a heat radiating part (at the most downstream side of the blown air flow ( 10), the refrigerant inlet (12b) is provided in the tank part (12) arranged on the upper side of the pair of tank parts (12, 13), and at least two heat radiating parts (10, 20) are provided. Among these, in the heat radiation part (10) in which the refrigerant inlet (12b) is provided in the tank part (12) arranged on the upper side of the pair of tank parts (12, 13, 22, 23), a plurality of All of the tubes (111) are configured such that the refrigerant flows from the upper side toward the lower side, and the pair of tank parts (12, 13, 22) of at least two heat radiating parts (10, 20). 23) on the lower side The first tube group in which the refrigerant flows from the lower side to the upper side in the plurality of tubes (211) in the heat radiating unit (20) in which the refrigerant inlet (24) is provided in the placed tank unit (23). (21a) and a second tube group (21b) in which the refrigerant flows from the upper side to the lower side are provided.

  According to this, in the heat radiating part (10) in which the refrigerant inlet (12b) is provided in the tank part (12) arranged on the upper side of the pair of tank parts (12, 13), a plurality of tubes (111) is configured so that the refrigerant flows from the upper side toward the lower side, so that in the heat dissipating part (10), the direction of gravity applied to the liquid phase refrigerant flowing through the tube (111), and the liquid Since the flow direction of the phase refrigerant matches, the refrigerant is well distributed to all the tubes (111).

  On the other hand, a plurality of tubes (20) in the heat dissipating part (20) in which the refrigerant inlet (24) is provided in the tank part (23) disposed on the lower side of the pair of tank parts (12, 13, 22, 23). 211) includes a first tube group (21a) in which the refrigerant flows from the lower side to the upper side, and a second tube group (21b) in which the refrigerant flows from the upper side to the lower side. In the tube group (21a), since the direction of gravity applied to the liquid refrigerant flowing through the tube (211) is opposite to the flow direction of the liquid refrigerant, refrigerant distribution of the tubes (211) belonging to the first tube group (21a) is reversed. Sex worsens.

  However, the heat radiating section (20) is provided with both the first tube group (21a) and the second tube group (21b), and the refrigerant flow is configured to turn at least once. The flow path cross-sectional area decreases and the flow rate of the refrigerant increases. For this reason, it is possible to minimize the influence of deterioration in refrigerant distribution due to the provision of the first tube group (21a) in which the refrigerant flows from the lower side toward the upper side.

  By the way, in at least two heat radiating portions (10, 20) arranged in series with respect to the flow direction of the blast air, even if an air temperature distribution is generated in the heat radiating portion (20) arranged on the upstream side of the blast air flow. The temperature difference is alleviated by the heat dissipating part (10) arranged on the downstream side of the blown air flow. However, if an air temperature difference occurs in the heat dissipating part (10) arranged on the most downstream side of the blown air flow, the air is directly blown into the vehicle interior without being reduced. Further, the amount of heat exchange between the blown air and the refrigerant in the core part (11) of the heat dissipating part (10) arranged on the most downstream side of the blown air flow is the air blowing in the core part (21) of the other heat dissipating part (20). It becomes larger than the amount of heat exchange between the air and the refrigerant. Therefore, the core part (11) of the heat radiating part (10) arranged on the most downstream side of the blown air flow has the greatest influence on the temperature distribution of the blown air as the whole refrigerant radiator.

  For this reason, while arrange | positioning two types of thermal radiation parts (10, 20) mentioned above in series with respect to the flow direction of blowing air, a refrigerant | coolant flows toward the downward side from the upper side in all the some tubes (111). By disposing the heat dissipating part (10) configured as described above on the most downstream side of the blown air flow, the temperature distribution can be relaxed in the heat dissipating part (10) with good refrigerant distribution. For this reason, the temperature distribution of the air blown out by exchanging heat with the refrigerant can be suppressed as the whole refrigerant radiator.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the heating operation of the heat pump cycle of 1st Embodiment. It is a whole block diagram which shows the refrigerant | coolant flow path etc. at the time of the cooling operation of the heat pump cycle of 1st Embodiment. It is a front view of the refrigerant radiator concerning a 1st embodiment. FIG. 4 is an exploded perspective view of the refrigerant radiator shown in FIG. 3. It is a perspective view which shows the communication part in 1st Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the refrigerant radiator which concerns on 1st Embodiment. It is a graph which shows the investigation result of the temperature distribution of a refrigerant radiator. It is an expansion perspective view which shows the communicating part vicinity of the refrigerant | coolant heat radiator which concerns on 2nd Embodiment. It is an expansion perspective view which shows the communicating part vicinity of the refrigerant | coolant heat radiator which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the refrigerant radiator which concerns on 4th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the refrigerant radiator which concerns on 5th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the refrigerant radiator which concerns on 6th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the refrigerant radiator which concerns on 7th Embodiment. It is the top view which looked at the refrigerant radiator concerning 8th Embodiment from the upper side. It is the top view which looked at the refrigerant radiator which concerns on 8th Embodiment from the downward side.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, a heat pump cycle 100 (vapor compression refrigeration cycle) including the refrigerant radiator 1 of the present invention is applied to a vehicle air conditioner. The vehicle air conditioner can be applied not only to a normal engine vehicle that obtains a driving force for driving from an engine (internal combustion engine) but also to various vehicles such as a hybrid vehicle and an electric vehicle.

  The heat pump cycle 100 fulfills the function of heating or cooling the vehicle interior air blown into the vehicle interior that is the air conditioning target space in the vehicle air conditioner. Therefore, the heat pump cycle 100 switches the refrigerant flow path, heats the vehicle interior blown air that is the 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.

  In the entire configuration diagram shown in the heat pump cycle 100 of FIGS. 1 and 2, the refrigerant flow during the heating operation and the refrigerant flow during the cooling operation are indicated by solid arrows.

  First, the compressor 110 is disposed in the engine room, sucks the refrigerant in the heat pump cycle 100, compresses and discharges the refrigerant, and a fixed displacement compressor 110a having a fixed discharge capacity is replaced by an electric motor 110b. It is an electric compressor to drive. Specifically, various types of compression mechanisms such as a scroll type compression mechanism and a vane type compression mechanism can be adopted as the fixed capacity type compressor 110a.

  The electric motor 110b 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 | coolant discharge capability of the compressor 110 is changed by this rotation speed control. Therefore, in the present embodiment, the electric motor 110b constitutes a discharge capacity changing unit of the compressor 110.

  A refrigerant inlet side of the refrigerant radiator 1 is connected to the refrigerant discharge port of the compressor 110. The refrigerant radiator 1 is disposed in a casing 31 of an indoor air conditioning unit 30 of the vehicle air conditioner 1 described later, and is blown into the vehicle interior after passing through a high-temperature and high-pressure refrigerant discharged from the compressor 110 and a refrigerant evaporator 40 described later. It is a heat exchanger for heating that exchanges heat with air. The detailed configurations of the refrigerant radiator 1 and the indoor air conditioning unit 30 will be described later.

  On the refrigerant outlet side of the refrigerant radiator 1, a heating fixed throttle 130 is connected as a decompression means for heating operation that decompresses and expands the refrigerant that has flowed out of the refrigerant radiator 1 during the heating operation. As the heating fixed throttle 130, an orifice, a capillary tube or the like can be adopted. The refrigerant inlet side of the outdoor heat exchanger 160 is connected to the outlet side of the heating fixed throttle 130.

  Further, a fixed throttle bypass passage 140 is connected to the refrigerant outlet side of the refrigerant radiator 1 to guide the refrigerant flowing out of the refrigerant radiator 1 to the outdoor heat exchanger 160 side by bypassing the heating fixed throttle 130. Yes. The fixed throttle bypass passage 140 is provided with an on-off valve 15a for opening and closing the fixed throttle bypass passage 140. 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.

  Further, the pressure loss that occurs when the refrigerant passes through the on-off valve 15a is extremely small with respect to the pressure loss that occurs when the refrigerant passes through the heating fixed throttle 130. Accordingly, the refrigerant that has flowed out of the refrigerant radiator 1 flows into the outdoor heat exchanger 160 via the fixed throttle bypass passage 140 when the on-off valve 15a is open, and when the on-off valve 15a is closed. Flows into the outdoor heat exchanger 160 through the heating fixed throttle 130.

  Thereby, the on-off valve 15 a can switch the refrigerant flow path of the heat pump cycle 100. 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 refrigerant radiator 1 outlet side and the heating fixed throttle 130 inlet side, the refrigerant radiator 1 outlet side, and the fixed throttle bypass passage 140 inlet side. An electric three-way valve or the like that switches the refrigerant circuit that connects the two may be employed.

  The outdoor heat exchanger 160 exchanges heat between the low-pressure refrigerant circulating inside and the outside air blown from the blower fan 170. This outdoor heat exchanger 160 is disposed in the engine room and functions as an evaporator that evaporates the low-pressure refrigerant and exerts an endothermic action during heating operation, and functions as a radiator that radiates the high-pressure refrigerant during cooling operation. Heat exchanger.

  The blower fan 170 is an electric blower in which the operation rate, that is, the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device. An electrical three-way valve 15 b is connected to the outlet side of the outdoor heat exchanger 160. 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.

  More specifically, the three-way valve 15b switches to a refrigerant flow path that connects an outlet side of the outdoor heat exchanger 160 and an inlet side of an accumulator 180 described later during heating operation, and the outdoor heat exchanger 160 during cooling operation. Is switched to the refrigerant flow path connecting the outlet side of the cooling and the inlet side of the cooling fixed throttle 190.

  The cooling fixed throttle 190 is a pressure reducing means for cooling operation that decompresses and expands the refrigerant that flows out of the outdoor heat exchanger 160 during the cooling operation, and the basic configuration thereof is the same as that of the heating fixed throttle 130. The outlet side of the cooling fixed throttle 190 is connected to the refrigerant inlet side of the refrigerant evaporator 40 as an indoor evaporator.

  The refrigerant evaporator 40 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 refrigerant radiator 1, 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 180 is connected to the refrigerant outlet side of the refrigerant evaporator 40.

  The accumulator 180 is a gas-liquid separator for a low-pressure side refrigerant that separates the gas-liquid of the refrigerant that has flowed into the accumulator 180 and stores excess refrigerant in the cycle. The suction side of the compressor 110 is connected to the gas-phase refrigerant outlet of the accumulator 180. Therefore, the accumulator 180 functions to prevent liquid compression of the compressor 110 by suppressing the liquid phase refrigerant from being sucked into the compressor 110.

  Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is disposed inside the instrument panel (instrument panel) at the foremost part of the vehicle interior, and the blower 32, the above-described refrigerant radiator 1, the refrigerant evaporator 40, 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) that has a certain degree of elasticity and is excellent in 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.

  On the downstream side of the air flow of the inside / outside air switching device 33, a blower 32 that blows air sucked through the inside / outside air switching device 33 toward the vehicle interior is arranged. 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.

  On the downstream side of the air flow of the blower 32, the refrigerant evaporator 40 and the refrigerant radiator 1 are arranged in this order with respect to the flow of the air blown into the vehicle interior. In other words, the refrigerant evaporator 40 is disposed upstream of the refrigerant radiator 1 in the flow direction of the air blown into the vehicle interior.

  Further, on the downstream side of the air flow of the refrigerant evaporator 40 and on the upstream side of the air flow of the refrigerant radiator 1, the ratio of the air volume passing through the refrigerant radiator 1 in the blown air after passing through the refrigerant evaporator 40. An air mix door 34 for adjusting the air pressure is disposed. In addition, on the downstream side of the air flow of the refrigerant radiator 1, the blown air heated by exchanging heat with the refrigerant in the refrigerant radiator 1 and the blown air not heated by bypassing the refrigerant radiator 1 are mixed. A mixing space 35 is provided.

  An opening hole for blowing the conditioned air mixed in the mixing space 35 into the vehicle interior, which is the space to be cooled, is disposed in the most downstream portion of the air flow of the casing 31. Specifically, the opening hole includes a face opening hole that blows conditioned air toward the upper body of an occupant in the vehicle interior, a foot opening hole that blows conditioned air toward the feet of the occupant, and the inner surface of the front window glass of the vehicle A defroster opening hole (both not shown) for blowing air-conditioning air toward is provided.

  Therefore, 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 refrigerant radiator 1, and the temperature of the conditioned air blown out from each opening hole. 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.

  In other words, 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 110 and the air blown into the passenger compartment in the refrigerant radiator 1. 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.

  Furthermore, on the upstream side of the air flow of the face opening hole, foot opening hole, and defroster opening hole, a face door that adjusts the opening area of the face opening hole, a foot door that adjusts the opening area of the foot opening hole, and a defroster opening hole, 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 opening hole mode switching means for switching the opening hole 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).

  On the other hand, the air flow downstream side of the face opening hole, the foot opening hole, and the defroster opening hole is respectively connected to the face air outlet, the foot air outlet, and the defroster air outlet provided in the vehicle interior via ducts that form air passages. It is connected. For example, the face opening hole is connected to a front face air outlet provided at the center in the left-right direction of the instrument panel, and a side face air outlet provided at the end in the left-right direction (both not shown). .

Moreover, these front face outlets and side face outlets are provided at a plurality of locations for the driver seat and the passenger seat, respectively. For example, the heat exchanger area on the driver seat side of the refrigerant radiator 1 during the heating operation. The blown air heated in the step is mainly blown out to the driver's seat side, and the blown air heated in the heat exchange area on the passenger seat side is mainly blown out to the passenger seat side.

  Next, the electric control unit of this embodiment will be described. 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 110, 15a, 15b, 170, 32, etc. is controlled.

  Further, on the input side of the air conditioning control device, 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, and the temperature of the air blown from the refrigerant evaporator 40 (evaporator) Sensor group for various air conditioning control, such as an evaporator temperature sensor for detecting the temperature), a discharge refrigerant temperature sensor for detecting the refrigerant discharge refrigerant temperature of the compressor 110, and an outlet refrigerant temperature sensor for detecting the refrigerant temperature on the outlet side of the outdoor heat exchanger 160. Is connected.

  Further, 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. . As 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.

  The air-conditioning control apparatus is configured integrally with control means for controlling the electric motor 110b, the on-off valve 15a, the three-way valve 15b, etc. of the compressor 110, and controls these operations. In this embodiment, Of the air conditioning control device, the configuration (hardware and software) for controlling the operation of the compressor 110 constitutes the refrigerant discharge capacity control means, and the construction for controlling the operations of the various devices 15a and 15b constituting the refrigerant flow path switching means. Constitutes a refrigerant flow path control means.

  Next, the detailed configuration of the refrigerant radiator 1 will be described with reference to FIGS. 3 and 4. In addition, the up and down arrows in FIGS. 3 and 4 indicate the up and down directions in a state where the refrigerant radiator 1 is mounted in the casing 31 of the indoor air conditioning unit 30. The same applies to the following drawings.

  The refrigerant radiator 1 includes two heat radiating portions 10 and 20 arranged in series with respect to the flow direction of the blown air (flow direction of the fluid to be cooled). Here, in this embodiment, the heat radiation part arrange | positioned in the leeward side (downstream side) of the air flow direction of blowing air among the two heat radiation parts 10 and 20 is called the leeward side heat radiation part 10, and the flow of blowing air The heat dissipating part disposed on the windward side (upstream side) in the direction is referred to as the windward heat dissipating part 20. In addition, the leeward side heat radiating part 10 in the present embodiment constitutes the “first heat radiating part” in the claims, and the windward side heat radiating part 20 constitutes the “second heat radiating part” in the claims. Yes.

  The basic configuration of the leeward side heat radiating part 10 and the windward side heat radiating part 20 is the same, and a pair of tank parts 12, 13, 22 disposed on the upper and lower sides of the core parts 11, 21 and the core parts 11, 21, respectively. 23.

  In the present embodiment, the core portion in the leeward side heat radiating portion 10 is referred to as the leeward side core portion 11, and the core portion in the leeward side heat radiating portion 20 is referred to as the leeward side core portion 21. Of the pair of tank portions 12 and 13 in the leeward side heat radiating portion 10, the tank portion disposed on the upper side is referred to as the first leeward side tank portion 12, and the tank portion disposed on the lower side is referred to as the second leeward side. This is referred to as a tank portion 13. Similarly, of the pair of tank parts 22 and 23 in the windward side heat radiating part 20, the tank part disposed on the upper side is referred to as a first windward tank part 22, and the tank part disposed on the lower side is referred to as the second wind part. This is referred to as the upper tank portion 23.

  Each of the leeward core portion 11 and the leeward core portion 21 of the present embodiment includes a plurality of tubes 111 and 211 extending in the vertical direction (vertical direction) and fins 112 and 212 joined between the adjacent tubes 111 and 211. And a laminate in which layers are alternately arranged. Hereinafter, the stacking direction in the stacked body of the plurality of tubes 111 and 211 and the plurality of fins 112 and 212 is referred to as a tube stacking direction.

  The tube 111 of the leeward core portion 11 has one end side (upper end side) in the longitudinal direction connected to the first leeward side tank portion 12 and the other end side (lower end side) in the longitudinal direction is connected to the second leeward side tank portion. 13 is connected. The tube 211 of the windward core portion 21 has one end side (upper end side) in the longitudinal direction connected to the first windward tank portion 22 and the other end side (lower end side) in the longitudinal direction is connected to the second windward side. It is connected to the tank part 23.

  Here, in the leeward side heat radiating part 10, all of the plurality of tubes 111 constituting the leeward side core part 11 are configured such that the refrigerant flows from the upper side toward the lower side. Further, in the windward heat radiating section 20, the plurality of tubes 211 constituting the windward core section 21 includes the first tube group 21a in which the refrigerant flows from the lower side to the upper side, and the refrigerant from the upper side to the lower side. The 2nd tube group 21b which flows toward is provided.

  In this embodiment, when the windward core portion 21 is viewed from the upstream side of the blown air flow, the first tube group 21a is disposed on the right side in the tube stacking direction, and the second tube group 21b is positioned on the left side in the tube stacking direction. Is arranged. Each of the tubes 111 and 211 includes a flat tube in which a refrigerant passage through which a refrigerant flows is formed and a cross-sectional shape thereof is a flat shape extending along the flow direction of the blown air.

  Each of the fins 112 and 212 is a corrugated fin formed by bending a thin plate material into a wave shape, joined to the flat outer surface side of the tubes 111 and 211, and heat exchange for expanding the heat transfer area between the blown air and the refrigerant. Configure the facilitating means.

  In the laminated body of the tubes 111 and 211 and the fins 112 and 212, side plates 113 and 213 that reinforce the core portions 11 and 12 are disposed at both ends in the tube laminating direction. The side plates 113 and 213 are joined to the fins 112 and 212 arranged on the outermost side in the tube stacking direction.

  The first leeward tank unit 12 is closed at one end (left end when viewed from the upstream side of the blown air flow) and is closed at the other end (right end when viewed from the upstream side of the blown air flow). It is comprised with the cylindrical member to which the refrigerant | coolant introduction part 12a for introducing the refrigerant | coolant discharged from the compressor 110 was connected to. The first leeward tank section 12 has a through hole (not shown) in which one end side (upper end side) of each tube 111 is inserted and joined at the bottom. That is, the first leeward tank unit 12 is configured such that the internal space thereof communicates with each tube 111 of the leeward core unit 11, and refrigerant distribution that distributes the refrigerant to each tube 111 of the leeward core unit 11. It functions as a part.

  The 2nd leeward side tank part 13 is comprised with the cylindrical member by which the both end sides were obstruct | occluded. The second leeward tank portion 13 has a through hole (not shown) in which the other end side (lower end side) of each tube 111 is inserted and joined to the ceiling portion. That is, the second leeward tank unit 13 is configured such that the internal space thereof communicates with each tube 111, and functions as a refrigerant collecting unit that collects the refrigerant from each tube 111 of the leeward core unit 11.

  The second windward tank portion 23 is closed at one end side, and connected to the other end side is a refrigerant derivation portion 23a for deriving the refrigerant from the inside of the tank to the on-off valve 15a or the heating fixed throttle 130 side. It is comprised with the cylindrical member. The second upwind tank portion 23 has a through hole (not shown) in which the other end side (lower end side) of each tube 211 is inserted and joined to the ceiling portion. That is, the second upwind tank unit 23 is configured such that its internal space communicates with each tube 211 of the upwind core unit 21.

  Inside the second upwind tank section 23, a partition section 231 is disposed at a central position in the longitudinal direction, and the tank 211 communicates with each tube 211 belonging to the first tube group 21a by the partition section 231. It is partitioned into a space and a space in which each tube 211 belonging to the second tube group 21b communicates.

  A communication portion 50 described later is connected to a space where the tubes 211 belonging to the first tube group 21a communicate. Moreover, the refrigerant | coolant derivation | leading-out part 23a is connected to the space which each tube 211 which belongs to the 2nd tube group 21b connects.

  Here, the space where the tubes 211 belonging to the first tube group 21a communicate with each other in the second upwind tank portion 23 distributes the refrigerant to the tubes 211 belonging to the first tube group 21a. The space in which the tubes 211 belonging to the second tube group 21b communicate with each other functions as a refrigerant collecting portion 233 for collecting refrigerant from the tubes 211 belonging to the second tube group 21b.

  The first upwind tank unit 22 is configured by a cylindrical member whose both ends are closed. The first upwind tank section 22 has a through hole (not shown) in which one end side (upper end side) of each tube 211 is inserted and joined at the bottom. That is, the first upwind tank unit 22 is configured such that its internal space communicates with each tube 211 of the upwind core unit 21. The first upwind tank unit 22 collects refrigerant from the tubes 211 belonging to the first tube group 21a of the upwind core unit 21 and distributes the refrigerant to the tubes 211 belonging to the second tube group 21b. It functions as a part.

  The space in the tank of the second leeward tank unit 13 and the refrigerant distribution unit 232 of the second leeward tank unit 23 are connected via the communication unit 50. The communication part 50 is configured as a separate body from the second leeward tank part 13 and the second leeward tank part 23.

  In this embodiment, as shown in FIG. 5, the communication part 50 is comprised with the multi-hole tube which has a some refrigerant path. The communicating portion 50 has through-holes 14 and 24 formed in the second leeward tank portion 13 and the second windward tank portion 23, respectively, at both ends of the refrigerant flow direction (flowing air flow direction) (see FIG. 4). Is fixed to the second leeward tank unit 13 and the second leeward tank unit 23.

  Cutouts 51 are formed at both ends of the communication portion 50 in the refrigerant flow direction. The lengths of the through holes 14 and 24 in the second leeward tank portion 13 and the second leeward tank portion 23 in the width direction are both ends of the communication portion 50 in the refrigerant flow direction (notches 51 are formed. Slightly longer than the length in the width direction of the portion) and shorter than the length in the width direction of the central portion of the communication portion 50 in the refrigerant flow direction (the portion where the notch 51 is not formed). The “width direction” in the through holes 14 and 24 and the communication portion 50 means a direction parallel to the longitudinal direction (tube stacking direction) of the second leeward tank portion 13 and the second leeward tank portion 23. To do.

  Therefore, when the communication portion 50 is inserted into the through holes 14 and 24 of the second leeward tank portion 13 and the second leeward tank portion 23, only the both ends in the refrigerant flow direction of the communication portion 50 are the through holes 14 and 24. The inside of the communicating portion 50 in the refrigerant flow direction does not enter the through holes 14 and 24. Thereby, positioning of the communication part 50 with respect to the 2nd leeward side tank part 13 and the 2nd leeward side tank part 23 can be performed easily.

  Here, the refrigerant flow in the refrigerant radiator of the first embodiment will be described. As shown by the solid line arrows in FIGS. 4 and 6, the refrigerant that has flowed into the first leeward tank portion 12 of the leeward heat radiating portion 10 from the refrigerant introduction portion 12 a moves upward in the tube 111 constituting the leeward core portion 11. Flows from the side toward the lower side and gathers in the second leeward tank unit 13. Thereafter, the refrigerant gathered in the second leeward tank unit 13 flows into the refrigerant distribution unit 232 of the second leeward tank unit 23 of the windward heat radiating unit 20 through the communication unit 50.

  The refrigerant that has flowed into the refrigerant distributor 232 of the second upwind tank unit 23 flows through the tubes 211 belonging to the first tube group 21 a of the upwind core unit 21 and flows into the first upwind tank unit 22. The refrigerant flowing into the first upwind tank unit 22 flows through the tubes 211 belonging to the second tube group 21b of the upwind core unit 21 and collects in the refrigerant collecting unit 233 of the second upwind tank unit 23. Then, the refrigerant flows out from the refrigerant outlet 23a.

  As described above, the refrigerant discharged from the compressor 110 flows into the first leeward tank unit 12 of the leeward heat radiating unit 10 through the refrigerant introduction unit 12a. In addition, the refrigerant that has flowed out of the communication part 50 flows into the second windward tank part 23 of the windward heat dissipation part 20 through the through hole 24. Accordingly, the portion 12b of the first leeward tank portion 12 to which the refrigerant introduction portion 12a is connected and the through hole 24 of the second leeward tank portion 23 constitute the “refrigerant inlet” in the claims. Yes.

  Moreover, the refrigerant | coolant which distribute | circulated the refrigerant | coolant heat radiator 1 flows out from the refrigerant | coolant derivation | leading-out part 23a connected to the 2nd windward side tank part 23 outside. Accordingly, the portion 23b of the second upwind tank portion 23 to which the refrigerant outlet portion 23a is connected constitutes the “refrigerant outlet” in the claims.

  Next, the operation of the vehicle air conditioner of the present embodiment having the above configuration will be described. In the vehicle air conditioner of the present embodiment, as described above, the heating operation for heating the vehicle interior and the cooling operation for cooling the vehicle interior can be executed. The operation in each operation will be described below.

(A) Heating operation 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. During the heating operation, the air conditioning control device 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 160 and the inlet side of the accumulator 180. As a result, the heat pump cycle 100 is switched to the refrigerant flow path through which the refrigerant flows as shown by the solid line arrows in FIG.

  With this refrigerant flow path configuration, the air conditioning control device reads the detection signal of the above-described air conditioning control sensor group and the operation signal of the operation panel. 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. Furthermore, based on the calculated target blowing temperature TAO and the detection signal of the sensor group, the operating states of various air conditioning control devices connected to the output side of the air conditioning control device are determined.

  For example, the refrigerant discharge capacity of the compressor 110, that is, the control signal output to the electric motor of the compressor 110 is determined as follows. First, the target evaporator outlet temperature TEO of the refrigerant evaporator 40 is determined based on the target outlet temperature TAO with reference to a control map stored in advance in the air conditioning controller.

  And based on the deviation of this target evaporator blowing temperature TEO and the blowing air temperature from the refrigerant evaporator 40 detected by the evaporator temperature sensor, the blowing air temperature from the refrigerant evaporator 40 is calculated using a feedback control method. A control signal output to the electric motor of the compressor 110 is determined so as to approach the target evaporator outlet temperature TEO.

  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 refrigerant evaporator 40, the compressor 110 discharge refrigerant temperature detected by the discharge refrigerant temperature sensor, and the like are used. Thus, 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.

  During heating operation, as shown in FIG. 1, even if the opening degree of the air mix door 34 is controlled so that the total air volume of the vehicle interior air blown from the blower 32 passes through the refrigerant radiator 1. Good.

  Then, the control signal determined as described above is 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. Such a control routine is basically repeated in the same manner during the cooling operation.

  Further, in the heat pump cycle 100 during the heating operation, the high-pressure refrigerant discharged from the compressor 110 flows into the refrigerant radiator 1. The refrigerant that has flowed into the refrigerant radiator 1 exchanges heat with the vehicle interior blown air that has been blown from the blower 32 and passed through the refrigerant evaporator 40 to radiate heat. Thereby, vehicle interior blowing air is heated.

  Since the on-off valve 15a is closed, the high-pressure refrigerant that has flowed out of the refrigerant radiator 1 flows into the heating fixed throttle 130 and is decompressed and expanded. The low-pressure refrigerant decompressed and expanded by the heating fixed throttle 130 flows into the outdoor heat exchanger 160. The low-pressure refrigerant that has flowed into the outdoor heat exchanger 160 absorbs heat from the outside air blown by the blower fan 170 and evaporates.

  The refrigerant flowing out of the outdoor heat exchanger 160 flows into the accumulator 180 because the three-way valve 15b is switched to the refrigerant flow path connecting the outlet side of the outdoor heat exchanger 160 and the inlet side of the accumulator 180. Gas-liquid separation. The gas-phase refrigerant separated by the accumulator 180 is sucked into the compressor 110 and compressed again.

  As described above, during the heating operation, the air blown into the vehicle interior is heated by the amount of heat of the refrigerant discharged from the compressor 110 by the refrigerant radiator 1, and the vehicle interior, which is the air conditioning target space, can be heated.

(B) Air-cooling operation Air-cooling operation is started when the operation switch of the operation panel is turned on (ON) and the air-cooling operation mode is selected by the selection switch. During this cooling operation, the air conditioning control device opens the on-off valve 15 a and switches the three-way valve 15 b to a refrigerant flow path that connects the outlet side of the outdoor heat exchanger 160 and the inlet side of the cooling fixed throttle 190. As a result, the heat pump cycle 100 is switched to the refrigerant flow path through which the refrigerant flows as shown by the solid line arrows in FIG.

  In the heat pump cycle 100 during the cooling operation, the high-pressure refrigerant discharged from the compressor 110 flows into the refrigerant radiator 1, exchanges heat with the vehicle interior blowing air that is blown from the blower 32 and passes through the refrigerant evaporator 40. When heat is radiated or when air does not pass through the refrigerant radiator 1, it passes through with little heat dissipation. The high-pressure refrigerant that has flowed out of the refrigerant radiator 1 flows into the outdoor heat exchanger 160 through the fixed throttle bypass passage 140 because the on-off valve 15a is open.

  The high-pressure refrigerant that has flowed into the outdoor heat exchanger 160 further radiates heat to the outside air blown by the blower fan 170. Since the refrigerant flowing out of the outdoor heat exchanger 160 is switched to the refrigerant flow path in which the three-way valve 15b connects the outlet side of the outdoor heat exchanger 160 and the inlet side of the cooling fixed throttle 190, it is fixed for cooling. The diaphragm 190 is decompressed and expanded.

  The refrigerant that has flowed out from the cooling fixed throttle 190 flows into the refrigerant evaporator 40, absorbs heat from the vehicle interior blown air blown by the blower 32, and evaporates. Thereby, vehicle interior blowing air is cooled. The refrigerant flowing out from the refrigerant evaporator 40 flows into the accumulator 180 and is separated into gas and liquid.

  The gas-phase refrigerant separated by the accumulator 180 is sucked into the compressor 110 and compressed again. As described above, during the cooling operation, the refrigerant evaporator 40 absorbs heat from the air blown into the vehicle interior and evaporates, whereby the air blown into the vehicle interior is cooled and the vehicle interior can be cooled.

  When the occupant sets a temperature higher than the vehicle interior temperature by the vehicle interior temperature setting switch during the cooling operation, the opening degree of the air mix door 34 is set so that the temperature of the air blown into the vehicle interior becomes higher than the vehicle interior temperature. Is adjusted. Even in such a case, in the refrigerant evaporator 40, the air blown into the passenger compartment is cooled and its absolute humidity is reduced, so that dehumidifying heating in the passenger compartment can be realized.

  As described above, in the vehicle air conditioner of the present embodiment, the heating operation, the cooling operation, and the dehumidifying heating operation can be executed by switching the refrigerant flow path of the heat pump cycle 100.

  Next, the examination result of the temperature distribution of the refrigerant radiator will be described with reference to FIG. 7A and 7C show the results of the refrigerant radiator of the comparative example, and FIGS. 7B and 7D show the results of the refrigerant radiator of the present embodiment. In FIG. 7, (a) and (b) show the case where the refrigerant flow rate is high (80 kg / h), and (c) and (d) show the case where the refrigerant flow rate is low (30 kg / h). Shows the case.

  In addition, the refrigerant heat radiator of the comparative example has two downflow type heat radiating portions in which the refrigerant flows in the vertical direction and is arranged in series with respect to the flow direction of the blown air. In the refrigerant radiator of the comparative example, the refrigerant flows in from the lower tank part of one of the two heat radiating parts, and the refrigerant flows from the lower part to the upper part through the core part to the upper tank part. Gather. Then, the refrigerant gathered in the upper tank part of one heat radiating part flows into the tank part above the other heat radiating part, flows from the upper part to the lower side, and gathers in the lower tank part. And flow out to the outside.

  As shown in FIGS. 7A and 7C, in the refrigerant radiator of the comparative example, particularly when the refrigerant flow rate is low (see FIG. 7C), the refrigerant flow is concentrated near the refrigerant inlet side. However, the refrigerant does not reach the tube far from the refrigerant inlet, and the right and left temperature distribution of the air blown out from the refrigerant radiator increases.

  The reason is as follows. Since the refrigerant radiator functions as a condenser in which the refrigerant is condensed inside, the gas-phase refrigerant is liquefied while condensing and dissipates heat to the outside. That is, the dryness of the refrigerant gradually decreases from the refrigerant inlet side, and the ratio of the liquid phase refrigerant increases. Here, since the density of the liquid phase refrigerant is larger than that of the gas phase refrigerant, it is greatly affected by gravity.

  In the downflow type heat exchanger, in the downward flow in which the refrigerant flows from the upper side to the lower side, the gravity direction and the flow direction of the refrigerant coincide with each other, so that the refrigerant flows smoothly. On the other hand, in the upward flow in which the refrigerant flows from the lower side toward the upper side, the gravity direction and the flow direction of the refrigerant are reversed, and the refrigerant flows against the gravity. For this reason, the condensed liquid phase refrigerant receives a force in the direction opposite to the flow direction.

  Therefore, when the refrigerant flow rate is low, in the region where the refrigerant flow is an upward flow, the refrigerant flow is concentrated only in the cross-sectional integral that balances the flow velocity for pushing up the liquid-phase refrigerant. As a result, the left and right temperature distribution blown out from the refrigerant radiator is increased.

  On the other hand, the refrigerant radiator of the present embodiment, as is apparent from FIGS. 7B and 7D, radiates the refrigerant even when the refrigerant flow rate is low (see FIG. 7D). The left and right temperature distribution blown out of the vessel is reduced.

  The reason is as follows. In the leeward side heat radiating part 10 in which the refrigerant inlet 12b is provided in the tank part 12 disposed on the upper side of the pair of tank parts 12 and 13, all of the plurality of tubes 111 are moved downward from the upper side. It is configured to flow toward the side. For this reason, in the leeward side heat radiating unit 10, the direction of gravity applied to the liquid refrigerant flowing through the tubes 111 coincides with the flow direction of the liquid refrigerant, so that the refrigerant is well distributed to all the tubes 111.

  On the other hand, the refrigerant flows from the lower side to the upper side in the plurality of tubes 211 in the windward heat radiating unit 20 in which the refrigerant inlet 24 is provided in the tank unit 23 disposed on the lower side of the pair of tank units 22 and 23. The 1st tube group 21a which flows toward the 1st tube group, and the 2nd tube group 21b which a refrigerant | coolant flows toward the downward side from the upper side are provided. For this reason, in the first tube group 21a, the direction of gravity applied to the liquid-phase refrigerant flowing through the tube 211 is opposite to the flow direction of the liquid-phase refrigerant. Therefore, the refrigerant distribution property of the tubes 211 belonging to the first tube group 21a. Gets worse.

  However, since both the first tube group 21a and the second tube group 21b are provided in the windward heat radiating portion 20 and the refrigerant flow is turned, the flow as the entire windward heat radiating portion 20 is provided. The road cross-sectional area decreases and the flow rate of the refrigerant increases. For this reason, the influence of the deterioration of the refrigerant | coolant distribution property by providing the 1st tube group 21a from which a refrigerant | coolant flows toward the upper side from the downward side can be suppressed to the minimum. In addition, even if some refrigerant distribution occurs in the first tube group 21a from which the refrigerant flows from the lower side to the upper side and the air temperature distribution deteriorates, the temperature distribution when the blown air passes through the leeward side heat radiating unit 10. Therefore, the influence on the temperature distribution of the blown air as the refrigerant radiator 1 as a whole can be reduced.

  By the way, in the two thermal radiation parts 10 and 20 arrange | positioned in series with respect to the flow direction of blowing air, the ventilation air and refrigerant | coolant in the core part 11 of the leeward side thermal radiation part 10 arrange | positioned in the blowing air flow most downstream side The heat exchange amount is larger than the heat exchange amount between the blown air and the refrigerant in the core portion 21 of the windward heat radiating portion 20. That is, the core part 11 of the leeward side heat radiating part 10 disposed on the most downstream side of the blown air flow has the largest influence on the temperature distribution of the blown air as the refrigerant radiator 1 as a whole.

  Accordingly, the above-described two heat dissipating units 10 and 20 are arranged in series with respect to the flow direction of the blown air, and the leeward is configured such that the refrigerant flows from the upper side toward the lower side in all of the plurality of tubes 111. By disposing the side heat radiating part 10 on the most downstream side of the blown air flow, the temperature distribution is relaxed in the leeward side heat radiating part 10 having good refrigerant distribution. For this reason, the temperature distribution of the air blown out by exchanging heat with the refrigerant can be suppressed as the refrigerant radiator 1 as a whole.

  By the way, when the second leeward tank unit 13 and the second leeward tank unit 23 are in thermal contact with each other, the second leeward tank unit 13 moves from the second leeward tank unit 23 to the vicinity of the refrigerant outlet 23b. Heat is transmitted. As a result, reboiling occurs in the refrigerant in the refrigerant collecting portion 233 of the second upwind tank 23, and the refrigerant flows in the direction opposite to the flow direction in the tubes 211 constituting the second tube group 21b (from the lower side to the upper side). Will be pushed back. As a result, in the windward heat radiating section 20, the left and right temperature distribution is deteriorated and the heat radiating performance is lowered.

  On the other hand, in the present embodiment, the second leeward tank unit 13 and the second leeward tank unit 23 are configured separately and the communication unit 50 guides the refrigerant of the first refrigerant assembly unit 13 to the refrigerant distribution unit 232. It is connected through. According to this, the tank parts 22 and 23 arrange | positioned under the core parts 11 and 21 can be thermally interrupted | blocked in parts other than the communication part 50. FIG. Therefore, it is possible to prevent heat from being transmitted from the second leeward tank unit 13 to the vicinity of the refrigerant outlet 23b of the second leeward tank unit 23.

  Furthermore, in this embodiment, the 2nd leeward side tank part 13 and the 2nd leeward side tank part 23 are comprised as a different body. Thereby, since the tank parts 12 and 22 arrange | positioned in the upper part of the core parts 11 and 21 in the two heat radiating parts 10 and 20 can be thermally interrupted, it is the 1st leeward tank part 12 from 1st. 1 It is possible to suppress heat from being transmitted to the upwind tank unit 22.

  Furthermore, in this embodiment, the refrigerant | coolant outflow port 23b is provided in the edge part by the side of the 2nd windward side tank part 23 in the windward side heat sink 20 near the refrigerant | coolant inflow port 12b in a tube lamination direction. For this reason, in the leeward side core part 11, the temperature near the refrigerant introduction part 12a (left side in FIG. 6) is higher than the side far from the refrigerant introduction part 12a (right side in FIG. 6). On the other hand, in the windward core portion 21, the side closer to the refrigerant introduction portion 12a is in the subcooled state, and therefore the temperature is lower than that on the side far from the refrigerant introduction portion 12a.

  And since the temperature of blowing air is canceled in the two core parts 11 and 21 when the two heat radiating parts 10 and 20 are arrange | positioned in series with respect to a ventilation air flow, it becomes difficult to produce temperature distribution on either side. Furthermore, since the refrigerant pipes (not shown) connected to the refrigerant introduction part 12a and the refrigerant outlet part 23a can be collected on the same side surface of the refrigerant radiator 1, the handling of the refrigerant pipes can be improved. . Thereby, the mounting property to the indoor air conditioning unit 30 of the refrigerant | coolant heat radiator 1 can be improved.

  By the way, when the refrigerant radiator 1 of the present invention is applied to the heat pump cycle 100 as in this embodiment, during the cooling operation, the refrigerant radiator 1 functions as a refrigerant pipe constituting the cycle and does not radiate the refrigerant. For this reason, it is necessary to reduce the pressure loss of the refrigerant in the refrigerant radiator 1. Specifically, the refrigerant flow path cross-sectional areas before and after the refrigerant flow turns are made equal, that is, the number of tubes 211 belonging to the first tube group 21a and the number of tubes 211 belonging to the second tube group 21b are made equal. Thus, the pressure loss of the refrigerant can be reduced most.

  Here, in the tube 211 belonging to the first tube group 21a of the windward radiating unit 20, the refrigerant flow becomes an upward flow, so that the pressure loss of the refrigerant becomes larger than that of the tube 211 belonging to the second tube group 21b. . Therefore, if the total number of tubes 211 belonging to the first tube group 21a is too large among the tubes 211 constituting the windward radiator 20, the refrigerant flow rate of the tubes 211 belonging to the first tube group 21a decreases during the heating operation. However, when the refrigerant distribution property is deteriorated, the right and left temperature distribution is increased.

  On the other hand, in the present embodiment, in the windward heat radiating portion 20, the total number of the tubes 211 constituting the windward core portion 21 is n, the number of the first tube groups 21a included in the windward core portion 21 and the number of the first tubes 21a. When the total number of tube groups, which is the total number of the two tube groups 21b, is x (x = 2 in this example), the total number m of the tubes 211 constituting the first tube group 21a is m ≦ n / x ( However, the windward core portion 21 is configured so as to satisfy the relationship m is a natural number). According to this, it is possible to improve both the refrigerant distribution of the windward core portion 21 and to reduce the pressure loss during the cooling operation.

  Furthermore, in this embodiment, the communicating part 50 is a multi-hole tube having a plurality of refrigerant passages. According to this, the difference of the distance from the refrigerant | coolant exit part of the communication part 50 to the tube 211 inlet part of the windward core part 21 can be made small. For this reason, the refrigerant | coolant redistribution property in the refrigerant | coolant distribution part 232 of the windward thermal radiation part 20 can be improved.

  In addition, by forming the communication portion 50 as a multi-hole tube, a plurality of inner pillar portions can be easily provided inside the communication portion 50. Thereby, the pressure | voltage resistance of the communication part 50 can be improved.

  Further, in the present embodiment, a positioning notch 51 is formed in the communication portion 50. According to this, since the positioning can be satisfactorily performed by the notch 51, when the communication portion 50 is inserted into the through holes 14 and 24 of the tank portions 13 and 23, the portion of the portion entering the tank portions 13 and 23 is inserted. The length (projection amount) can be shortened. For this reason, while reducing the pressure loss of the refrigerant | coolant in the communication part 50, the distribution property of a refrigerant | coolant can be improved.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. In the second embodiment, the configuration of the communication unit 50 is different from that in the first embodiment. 8 coincides with the vertical direction at the time of manufacture, and FIG. 8 is shown upside down with respect to FIG.

  As shown in FIG. 8, in the present embodiment, through holes (not shown) are formed in the bottom portions (portions farthest from the core portions 11 and 21) of the second leeward tank portion 13 and the second leeward tank portion 23. ) Is formed. And the refrigerant | coolant assembly part of the 2nd leeward side tank part 13 and the refrigerant | coolant of the 2nd leeward side tank part 23 are arrange | positioned so that both of these two through-holes may be covered, and the communication part 50 formed in the cup shape is arrange | positioned. The distribution unit 232 is configured to communicate with each other.

  According to this embodiment, since the communication part 50 can be assembled | attached from the upper side of the 2nd leeward side tank part 13 and the 2nd leeward side tank part 23 at the time of manufacture, an assembly property can be improved.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. In the third embodiment, the configuration of the communication unit 50 is different from that in the first embodiment.

  As shown in FIG. 9, in the present embodiment, through holes (see FIG. 9) are provided at the ends of the second leeward tank portion 13 and the second leeward tank portion 23 on the side far from the refrigerant inlet 12 b in the tube stacking direction. (Not shown) is formed. And the refrigerant | coolant assembly part of the 2nd leeward side tank part 13 and the refrigerant | coolant of the 2nd leeward side tank part 23 are arrange | positioned so that both of these two through-holes may be covered, and the communication part 50 formed in the cup shape is arrange | positioned. The distribution unit 232 is configured to communicate with each other.

  According to this embodiment, since the communication part 50 can be assembled | attached from the side of the 2nd leeward side tank part 13 and the 2nd leeward side tank part 23 at the time of manufacture, an assemblability can be improved.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG. Compared to the first embodiment, the fourth embodiment employs an N-turn flow path configuration in which the refrigerant flow makes a U-turn twice as the flow path configuration of the windward heat radiation unit 20. Is different.

  As shown in FIG. 10, the windward heat radiating portion 20 of the present embodiment has two first tube groups 21 a and one second tube group 21 b. The second tube group 21b is disposed between the two first tube groups 21a. Here, of the two first tube groups 21a, the one arranged on the upstream side of the refrigerant flow is referred to as the upstream first tube group 211a, and the one arranged on the downstream side of the refrigerant flow is the downstream first tube group 212a. That's it.

  Inside the second upwind tank section 23, a partition section 231 is disposed near the end on the side far from the refrigerant introduction section 12a in the tube stacking direction. And by this partition part 231, the tank internal space of the 2nd windward side tank part 23, each tube 211 which belongs to the space where each tube 211 which belongs to the upstream 1st tube group 211a communicates, and each tube 211 which belongs to the 2nd tube group 21b, and The downstream first tube group 212a is partitioned into a space communicating with each other. The communication part 50 is connected to the space which each tube 211 which belongs to the upstream 1st tube group 211a communicates.

  Here, the space where the tubes 211 belonging to the upstream first tube group 211a communicate with each other in the second upwind tank unit 23 distributes the refrigerant to the tubes 211 belonging to the upstream first tube group 211a. A space that functions as the refrigerant distributor 232 and communicates with both the tubes 211 belonging to the second tube group 21b and the downstream first tube group 212a collects refrigerant from the tubes 211 belonging to the second tube group 21b. At the same time, it functions as a refrigerant assembly / distribution unit 234 that distributes the refrigerant to the tubes 211 belonging to the downstream first tube group 212a.

  Inside the first upwind tank portion 22, a partition portion 221 is disposed near the end portion on the side close to the refrigerant introduction portion 12a in the tube stacking direction. And by this partition part 221, the tank internal space of the 1st wind side tank part 22 is the space where both each tube 211 which belongs to the upstream 1st tube group 211a, and each tube 211 which belongs to the 2nd tube group 21b communicates. And a space where the downstream first tube group 212a communicates. The refrigerant outlet 23a is connected to the space where the downstream first tube group 212a communicates.

  Here, the space where both the tubes 211 belonging to the upstream first tube group 211a and the tubes 211 belonging to the second tube group 21b communicate with each other in the first upwind tank section 22 is the upstream first. The refrigerant from the tubes 211 belonging to the tube group 211a is gathered and functions as a refrigerant collecting / distributing portion 222 that distributes the refrigerant to the tubes 211 belonging to the second tube group 21b, and the downstream first tube group 21a communicates. The space functions as a refrigerant collecting portion 223 that collects refrigerant from each tube 211 belonging to the downstream first tube group 212a.

  According to this embodiment, since the refrigerant | coolant derivation | leading-out part 23a is connected to the 1st leeward side tank part 22, the refrigerant | coolant introduction part 12a and the refrigerant | coolant derivation | leading-out part 23a can be concentrated on the upper side of a refrigerant radiator. Therefore, the manageability of the refrigerant pipe (not shown) connected to the refrigerant introduction part 12a and the refrigerant outlet part 23a can be improved.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIG. In the fifth embodiment, as compared with the first embodiment, the flow path configuration of the leeward side heat radiating portion 10 and the windward side heat radiating portion 20 is an all-pass flow path configuration in which the refrigerant flow does not make a U-turn. The point of adoption is different.

  As shown in FIG. 11, in the windward heat radiation part 20 of this embodiment, all the several tubes 211 which comprise the windward core part 21 are comprised so that a refrigerant | coolant may flow toward the downward side from the upper side. ing.

  A refrigerant outlet 15 for allowing the refrigerant gathered in the second leeward tank unit 13 to flow out to the end of the second leeward tank unit 13 of the leeward heat radiating unit 10 on the side close to the refrigerant introduction part 12a in the tube stacking direction. Is formed. A refrigerant inlet 25 for allowing the refrigerant to flow into the first windward tank section 22 is formed at the end of the first windward tank section 22 of the windward heat radiating section 20 on the side close to the refrigerant introduction section 12a in the tube stacking direction. Has been.

  The refrigerant outlet 15 and the refrigerant inlet 25 are connected by a tubular communication portion 50. That is, the communication unit 50 is configured such that the refrigerant gathered in the second leeward tank unit 13 flows into the first leeward tank unit 22 via the communication unit 50.

  According to the present embodiment, all of the plurality of tubes 111 and 211 are configured such that the refrigerant flows from the upper side toward the lower side in both the leeward side heat radiating unit 10 and the upwind side heat radiating unit 20. Thus, since the direction of gravity applied to the liquid refrigerant flowing through the tubes 111 and 211 coincides with the flow direction of the liquid refrigerant, the refrigerant is transferred to all the tubes 111 and 211 in both the leeward side heat radiating unit 10 and the windward side heat radiating unit 20. Is well distributed. Therefore, the temperature distribution of the air blown out by exchanging heat with the refrigerant can be more reliably suppressed as the whole refrigerant radiator.

  In the present embodiment, the refrigerant outlet 15 and the refrigerant inlet 25 may be arranged on the side of the refrigerant radiator 1 opposite to the refrigerant introduction part 12a and the refrigerant outlet part 23a.

(Sixth embodiment)
Next, a sixth embodiment of the present invention will be described with reference to FIG. The sixth embodiment is different from the first embodiment in that three heat radiating portions 10, 20, and 60 are arranged in series with respect to the flow direction of the blown air.

  As shown in FIG. 12, an intermediate heat radiating portion 60 is provided between the leeward side heat radiating portion 10 and the windward side heat radiating portion 20. Since the basic configuration of the intermediate heat radiating unit 60 is the same as that of the windward heat radiating unit 20 described in the first embodiment, detailed description thereof is omitted.

  The plurality of tubes (not shown) of the intermediate heat radiating unit 60 include a first tube group 61a in which the refrigerant flows from the lower side to the upper side, and a second tube group 61b in which the refrigerant flows from the upper side to the lower side. Is provided. When the intermediate heat radiating unit 60 is viewed from the downstream side of the blown air flow, the first tube group 61a is disposed on the left side in the tube stacking direction, and the second tube group 61b is disposed on the right side in the tube stacking direction.

  A partition portion 631 is disposed at a central position in the longitudinal direction inside the second intermediate tank portion 63 disposed on the lower side of the tank portions 62 and 63 of the intermediate heat radiating portion 60. The second intermediate tank section 63 is partitioned by the partition section 631 into a space in which the tank internal space communicates with each tube belonging to the first tube group 61a and a space in which each tube belonging to the second tube group 61b communicates. ing.

  A first communication portion 50a, which will be described later, is connected to a space where the tubes belonging to the first tube group 61a communicate. Moreover, the 2nd communication part 50b mentioned later is connected to the space which each tube which belongs to the 2nd tube group 61b communicates.

  Here, in the inside of the second intermediate tank 63, the space in which the tubes belonging to the first tube group 61a communicate with each other functions as the refrigerant distributor 632 that distributes the refrigerant to the tubes belonging to the first tube group 61a. The space in which the tubes belonging to the second tube group 61b communicate with each other functions as a refrigerant collecting portion 633 that collects refrigerant from the tubes belonging to the second tube group 61b.

  The first intermediate tank unit 62 disposed on the upper side of the tank units 62 and 63 of the intermediate heat radiating unit 60 collects the refrigerant from the tubes belonging to the first tube group 61a and also belongs to the second tube group 61b. It functions as a refrigerant assembly / distribution unit that distributes the refrigerant to the tubes.

  By the way, in this embodiment, when the windward heat radiation part 20 is seen from the blast air flow downstream side, the first tube group 21a is arranged on the right side in the tube stacking direction, and the second tube on the left side in the tube stacking direction. Group 21b is arranged.

  The in-tank space of the second leeward tank unit 13 and the refrigerant distribution unit 632 of the second intermediate tank unit 63 are connected via the first communication unit 50a. The refrigerant collecting part 633 of the second intermediate tank part 63 and the refrigerant distribution part 232 of the second upwind tank part 23 are connected via the second communication part 50b. The structure of the 1st communication part 50a and the 2nd communication part 50b is the same as that of the communication part 50 demonstrated in 1st Embodiment. The first communication part 50a is arranged on the side close to the refrigerant introduction part 12a in the tube stacking direction, and the second communication part 50b is arranged on the side far from the refrigerant introduction part 12a in the tube lamination direction.

  According to the present embodiment, the three radiating units 10, 20, 60 are arranged in series with respect to the blast air flow, and further the refrigerant flow of the leeward side radiating unit 10 arranged on the most downstream side of the blast air flow is from the upper side. It is possible to obtain the same effect as in the first embodiment by adopting an all-pass type that flows downward and a U-turn type refrigerant flow in the other heat radiating units 10 and 20.

(Seventh embodiment)
Next, a seventh embodiment of the present invention will be described with reference to FIG. The seventh embodiment is different from the fifth embodiment in that the refrigerant flows in the leeward side heat radiating portion 10 and the windward side heat radiating portion 20 are independent.

  As shown in FIG. 13, in this embodiment, the leeward side heat radiating part 10 and the windward side heat radiating part 20 are each configured as an independent heat exchanger. Specifically, the refrigerant introduction parts 12a and 22a are connected to the first leeward tank part 12 of the leeward heat radiation part 10 and the first windward tank part 22 of the windward heat radiation part 20, respectively. Refrigerant derivation units 13a and 23a are connected to the second leeward tank unit 13 of the leeward radiating unit 10 and the second leeward tank unit 23 of the upwind radiating unit 20, respectively.

  The refrigerant introduction parts 12 a and 22 a and the refrigerant outlet parts 13 a and 23 a are arranged on the same side surface of the refrigerant radiator 1. According to this, the manageability of the refrigerant piping (not shown) connected to the refrigerant introduction parts 12a and 22a and the refrigerant outlet parts 13a and 23a can be improved.

  According to the present embodiment, the two heat dissipating units 10 and 20 are arranged in series with respect to the blown air flow, and the all-pass type in which the refrigerant flow of these two heat dissipating units 10 and 20 flows from the upper side to the lower side. By doing so, it is possible to obtain the same effects as those of the fifth embodiment.

(Eighth embodiment)
Next, an eighth embodiment of the present invention will be described with reference to FIGS. In the eighth embodiment, the structures of the tank portions 12, 13, 22, 23 are different from those of the first embodiment.

  As shown in FIG. 14, in this embodiment, the 1st leeward side tank part 12 and the 1st leeward side tank part 22 are integrally formed. Here, the tank part in which the first leeward tank part 12 and the first leeward tank part 22 are integrally formed is referred to as an upper tank part 120.

  A slit 120a extending in parallel with the tube stacking direction is formed in a portion between the first leeward tank portion 12 and the first leeward tank portion 22 in the upper tank portion 120. The slit 120a is formed by notching the upper tank portion 120 from an end portion closer to the refrigerant introduction portion 12a in the tube stacking direction toward an end portion farther from the refrigerant introduction portion 12b.

  Similarly, as shown in FIG. 15, the second leeward tank unit 13 and the second leeward tank unit 23 are integrally formed. Here, the tank part in which the second leeward tank part 13 and the second leeward tank part 23 are integrally formed is referred to as a lower tank part 130.

  A slit 130 a extending in parallel with the tube stacking direction is formed at a portion other than the communication portion 50 between the second leeward tank portion 13 and the second leeward tank portion 23 in the lower tank portion 130. The slits 130 a are formed by notching the lower tank portion 130 from the both ends in the tube stacking direction toward the communication portion 50.

  According to the present embodiment, the slit 120a is provided in the upper tank portion 120 between the first leeward tank portion 12 and the first leeward tank portion 22, so that the first leeward tank portion 12 and the first leeward tank portion 12 The heat transfer between the one wind side tank unit 22 can be blocked. Similarly, the second leeward tank unit 13 and the second leeward tank are provided by providing a slit 130a in a portion between the second leeward tank unit 13 and the second leeward tank unit 23 in the lower tank unit 130. The heat transfer between the parts 23 can be blocked.

  Further, in the present embodiment, the first leeward tank unit 12 and the first leeward tank unit 22 are integrally formed, and the second leeward tank unit 13 and the second leeward tank unit 23 are integrally formed. Therefore, the two core parts 11, 21, the upper tank part 120 and the lower tank part 130 can be assembled at a time. Therefore, the manufacturing time of the refrigerant radiator 1 can be shortened.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment (excluding the fourth embodiment), the example in which the first tube group 21a and the second tube group 21b are provided one by one in the windward heat radiation unit 20 has been described. Not limited to this, a plurality of at least one of the first tube group 21a and the second tube group 21b may be provided, and the first tube group 21a and the second tube group 21b may be alternately arranged.

  (2) In the refrigerant radiator 1 of the above-described embodiment, the example in which the refrigerant and the air blown into the passenger compartment are heat-exchanged has been described, but the configuration of the refrigerant radiator 1 of the present invention is as follows. It is not limited. For example, it may be configured to allow heat exchange of a plurality of types of fluids such as a refrigerant, air blown into the vehicle interior, and other heat medium.

  As a heat exchanger configured such that heat exchange of a plurality of types of fluids can be realized, a refrigerant tube that circulates a refrigerant and a heat medium tube that circulates a heat medium are sequentially stacked and arranged adjacent to each other. An air passage through which the blown air is circulated is formed between the tube for heating and the heat medium tube, and the refrigerant, the air and the heat medium are joined to both the refrigerant tube and the heat medium tube in the air passage. The structure which arrange | positioned the fin which enables heat transfer with a refrigerant | coolant and a heat medium while accelerating | stimulating heat exchange with blast air can be employ | adopted.

  (3) In the above-mentioned embodiment, although the example which applied the heat pump cycle 100 provided with the refrigerant | coolant heat radiator 1 of this invention to a vehicle air conditioner was applied, application of the heat pump cycle 100 provided with the refrigerant | coolant heat radiator 1 of this invention is applied. It is not limited to this. For example, the present invention may be applied to a stationary air conditioner, a cold / hot storage, a cooling / heating device for a vending machine, and the like.

10 Downward side heat radiation part (first heat radiation part)
20 Windward side heat radiation part (second heat radiation part)
11, 21 Core part 12, 13, 22, 23 Tank part 21a 1st tube group 21b 2nd tube group 50 Communication part 111, 211 tube

Claims (6)

A refrigerant radiator that is applied to a vapor compression refrigeration cycle (100) and heat-exchanges the refrigerant compressed by the compressor (110) and the blown air blown into the air-conditioning target space to dissipate the refrigerant. There,
Comprising at least two heat dissipating parts (10, 20) arranged in series with respect to the flow direction of the blown air;
Each of the at least two heat radiating portions (10, 20) includes a core portion (11, 21) configured by stacking a plurality of tubes (111, 211) through which the refrigerant flows, and the plurality of tubes (111, 211). ) And a pair of tank parts (12, 13, 22, 23) for collecting or distributing the refrigerant flowing through the plurality of tubes (111, 211). (12, 13, 22, 23) are arranged at both ends of the core portion (11, 21) in the vertical direction, and the refrigerant flows in the vertical direction, and the pair of tank portions (12, 13, 22, 23) are provided with refrigerant inlets (12b, 24) for allowing the refrigerant to flow into one of the tank portions (12, 23),
Of the at least two heat dissipating parts (10, 20), the heat dissipating part (10) disposed on the most downstream side of the blown air flow is disposed on the upper side of the pair of tank parts (12, 13). The refrigerant inlet (12b) is provided in the tank part (12) that is made,
Of the at least two heat radiating portions (10, 20), the refrigerant inlet (12b) is provided in the tank portion (12) disposed on the upper side of the pair of tank portions (12, 13, 22, 23). In the heat dissipating part (10) provided, all of the plurality of tubes (111) are configured such that the refrigerant flows from the upper side toward the lower side,
Of the at least two heat radiating portions (10, 20), the refrigerant inlet (24) is provided in the tank portion (23) disposed on the lower side of the pair of tank portions (12, 13, 22, 23). In the plurality of tubes (211) in the heat radiating section (20) provided, the first tube group (21a) in which the refrigerant flows from the lower side to the upper side, and the refrigerant from the upper side to the lower side. The refrigerant | coolant heat radiator characterized by providing the 2nd tube group (21b) which flows toward. As the at least two heat dissipating parts, a first heat dissipating part (10) and a second heat dissipating part (20) arranged on the upstream side of the blown air flow of the first heat dissipating part (10) are provided,
In the first heat radiating part (10), the tank part (12) disposed on the upper side of the pair of tank parts (12, 13) is provided with the refrigerant inlet (12b), and All of the plurality of tubes (111) are configured such that the refrigerant flows from the upper side toward the lower side,
The plurality of tubes (211) in the second heat radiating section (20) are provided with the first tube group (21a) and the second tube group (21b),
The tank part (13) disposed on the lower side of the pair of tank parts (12, 13) in the first heat radiating part (10) is the plurality of tubes (111) of the first heat radiating part (10). Comprising a first refrigerant assembly part (13) for collecting the refrigerant from
The tank part (23) disposed on the lower side of the pair of tank parts (22, 23) in the second heat radiating part (20) distributes the refrigerant to the first tube group (21a). Part (232), and a second refrigerant assembly part (233) that collects the refrigerant from the second tube group (21b),
The first heat radiating part (10) and the second heat radiating part (20) are connected via a communication part (50) that guides the refrigerant of the first refrigerant assembly part (13) to the refrigerant distribution part (232). The refrigerant radiator according to claim 1, wherein the refrigerant radiator is provided. The tank part (12) arranged on the upper side of the pair of tank parts (12, 13) in the first heat radiation part (10), on one end side in the stacking direction of the tubes (111), A refrigerant inlet (12b) is provided;
Close to the refrigerant inlet (12b) in the stacking direction of the tube (211) of any one of the pair of tank parts (22, 23) in the second heat radiating part (20). The refrigerant radiator according to claim 2, wherein a refrigerant outlet (23b) through which the refrigerant flows out is provided at an end portion on the side.   The tank parts (12, 22) disposed above the core parts (11, 21) in the first heat radiating part (10) and the second heat radiating part (20), and the core part (11 21) The tank parts (22, 23) arranged on the lower side of the communication part (50) are thermally blocked at a part other than the communication part (50). Refrigerant radiator. Among the at least two heat radiating portions (10, 20), in the heat radiating portion (20), the plurality of tubes (211) are provided with the first tube group (21a) and the second tube group (21b). Is
The first tube group (21a) and the second tube group (21b) are alternately arranged,
The total number of the plurality of tubes (211) constituting the core portion (21) is n, the number of the first tube groups (21a) included in the core portion (21), and the number of the second tube groups (21b). When the total number of tube groups, which is the total number, is x,
5. The total number m of the tubes (211) constituting the first tube group (21 a) satisfies a relationship of m ≦ n / x (where m is a natural number). The refrigerant radiator as described in any one of these.   The refrigerant radiator according to claim 2, wherein the communication part (50) is a multi-hole tube having a plurality of refrigerant passages.

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