CN104781627A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN104781627A CN104781627A CN201380059310.4A CN201380059310A CN104781627A CN 104781627 A CN104781627 A CN 104781627A CN 201380059310 A CN201380059310 A CN 201380059310A CN 104781627 A CN104781627 A CN 104781627A
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- Prior art keywords
- refrigerant
- downstream
- pipe
- heat exchange
- cooling water
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- 239000012530 fluid Substances 0.000 claims abstract description 91
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0246—Arrangements for connecting header boxes with flow lines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00321—Heat exchangers for air-conditioning devices
- B60H1/00328—Heat exchangers for air-conditioning devices of the liquid-air type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00321—Heat exchangers for air-conditioning devices
- B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
- F28F9/0224—Header boxes formed by sealing end plates into covers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
- F28F2009/004—Common frame elements for multiple cores
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2270/00—Thermal insulation; Thermal decoupling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0246—Arrangements for connecting header boxes with flow lines
- F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
A composite heat exchanger configured to be capable of exchanging heat between three types of fluids, wherein an air passage (70a) through which external air circulates is formed on the perimeter of a refrigerant tube (12a) and a coolant tube (43a), there being arranged on the air passage (70a), an outer fin (70b) expediting heat exchange between a refrigerant and external air and between coolant and external air. The outer fin (70b) has a refrigerant-side thermal connection portion (71b) for thermally connecting refrigerant tubes (12a) to one another and a coolant-side thermal connection portion (72b) for thermally connecting a refrigerant tube (12a) to a coolant tube water (43a). In a first core section (701) configured from a downstream-most-refrigerant tube (121a) for forming a final path that is the downstream-most path of the refrigerant flow, the number of refrigerant-side thermal connection portions (71b) is greater than the number of coolant-side thermal connection portions (72b). Any decline in the heat exchanging performance of the heat exchanger as a whole is thereby minimized.
Description
Related application cross-referenced
The application based on by reference to and its disclosure is introduced the application, on November 13rd, 2012 application Japanese patent application 2012-249441.
Technical field
The present invention relates to the compound heat exchanger being configured to carry out heat exchange between three kinds of fluids.
Background technology
Conventionally, there is known be configured to the compound heat exchanger that can carry out heat exchange between three kinds of fluids.Such as, in patent document 1, disclose a kind of compound heat exchanger, the discharge refrigerant (first fluid) making to discharge from the compressor of cooling cycle system and wind pushing air (the 3rd fluid) are carried out heat exchange and integrally form discharging heat that refrigerant has as a heat exchanger to the radiator of wind pushing air heat release to the refrigerant radiator of wind pushing air heat release and the heat that makes the cooling water of cooled engine (second fluid) and wind pushing air carry out heat exchange and had by cooling water by it.
Specifically, Patent Document 1 discloses following heat exchanger, its cooling water pipe laminated configuration that will flow for refrigerant pipe and Cooling Water of discharging refrigerant flowing, and to manage between cooling water pipe in for the extraneous gas path of outside air passes to be configured with and can realize the outside fin that refrigerant manages the heat movement between cooling water pipe being formed at adjacent refrigerant.Thus, the heat exchange between refrigerant and wind pushing air, heat exchange between cooling water and wind pushing air can not only be realized, the heat exchange between refrigerant and cooling water can also be realized.
At first technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2012-144245 publication
Summary of the invention
But, usually, in cooling cycle system, the degree of subcooling of the refrigerant flowed out from refrigerant radiator is controlled, and makes the coefficient of refrigerating performance of the circulatory system (COP) reach maximum.
At this, according to the research of present inventor, in the compound heat exchanger described in above-mentioned patent document 1, carry out in overcooled supercooling portion to condensed refrigerant in refrigerant radiator, be configured in the outside fin formed between the refrigerant pipe in supercooling portion and the cooling water pipe adjacent with this refrigerant pipe, for the heat that makes cooling water have, externally the region that releases of gas is excessive, the region of the heat had for making discharge refrigerant externally gas releasing diminishes.Therefore, in order to make the refrigerant of refrigerant radiator outlet side have desired degree of subcooling, the length of the refrigerant pipe forming supercooling portion must be lengthened, increasing the gross area of the outside fin be connected with this refrigerant pipe.
But the supercooling portion in refrigerant radiator is compared with condensation part (heat unit beyond the supercooling portion in refrigerant radiator), and the coefficient of overall heat transmission in tube wall face is extremely low.On the other hand, the coefficient of overall heat transmission forming the tube wall face place of the refrigerant pipe of condensation part is high, and heat exchange performance is high.Therefore, if lengthen the length of the refrigerant pipe forming supercooling portion, then the length forming the refrigerant pipe of condensation part shortens, as the heat exchange performance possible deviation of refrigerant radiator entirety.
The present invention is made in view of above-mentioned point, its object is in the reduction being configured to carry out suppressing the heat exchange performance as heat exchanger entirety in the compound heat exchanger of heat exchange between three kinds of fluids.
According to a scheme of the present invention, heat exchanger has: inner multiple first pipes for first fluid circulation; Inner multiple second pipes for second fluid circulation; By the heat exchange department that multiple first pipe and multiple second pipe laminated configuration the heat making first fluid and second fluid have are released to the 3rd fluid; The surrounding being located at multiple first pipes and multiple second pipe, the 3rd fluid path circulated for the 3rd fluid; And be configured at the 3rd fluid path, promote the outside fin of first fluid and the heat exchange of the 3rd fluid and the heat exchange of second fluid and the 3rd fluid.Outside fin has multiple first pipe hot linked first thermally coupled portion and will multiple first pipe and multiple second manage hot linked second thermally coupled portion each other.Multiple first pipe is divided into multiple groups, the multiple groups of passages being the first fluid making to distribute from the same space respectively and flowing to same direction of multiple first pipe.Multiple first pipe has and forms the passage of most downstream side on first fluid flow direction and the most downstream side first of final passage is managed, and heat exchange department has the first core, and this first core comprises most downstream side first and manages.In the first core, the number in the first thermally coupled portion is more than the number in the second thermally coupled portion.
According to the program, in the heat exchange department comprising most downstream side first pipe, the number in the first thermally coupled portion is more than the number in the second thermally coupled portion, thus, in the outside fin being configured at the heat exchange department be made up of most downstream side first pipe, the heat had for making first fluid is greater than the region that the heat for making second fluid have is released to the 3rd fluid to the region that the 3rd fluid is released.Therefore, it is possible to the heat making the first fluid of managing interior circulation in most downstream side first have is released to the 3rd fluid fully.
Thus, temperature without the need to the first fluid in order to make heat exchanger outlet side becomes desired temperature and lengthens most downstream side first manages, namely without the need to shortening the first pipe not forming final passage, therefore, it is possible to suppress the reduction as the heat exchange performance of heat exchanger entirety.
It should be noted that, " first pipe and the second pipe laminated configuration " refers to that laminated configuration in any order managed by the first pipe and second, does not limit the configuration sequence of the first pipe and the second pipe.In addition, " number in the first thermally coupled portion is more than the number in the second thermally coupled portion " refer to that the number comprising the second thermally coupled portion is the situation of 0.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the air conditioner for vehicles of the first embodiment of the present invention.
Fig. 2 is the stereogram of the compound heat exchanger of the first embodiment.
Fig. 3 is the exploded perspective view of the compound heat exchanger of the first embodiment.
Fig. 4 is the IV-IV sectional view of Fig. 2.
Fig. 5 is the V-V sectional view of Fig. 2.
Fig. 6 is the schematic stereogram for illustration of the refrigerant flowing in the compound heat exchanger of the first embodiment and flow of cooling water.
Fig. 7 is the performance plot of the relation of the exothermicity representing degree of subcooling and medium side.
Fig. 8 is the schematic sectional view of the heat exchange department long side direction in the first core of compound heat exchanger involved by the second embodiment of the present invention.
Fig. 9 is the schematic stereogram for illustration of the refrigerant flowing in the compound heat exchanger of the 3rd embodiment of the present invention and flow of cooling water.
Figure 10 is the schematic stereogram for illustration of the refrigerant flowing in the compound heat exchanger of the 4th embodiment of the present invention and flow of cooling water.
The schematic diagram of stream when Figure 11 is the warming operation representing the heat pump circulating system of the 5th embodiment of the present invention and chilled(cooling) water return (CWR) etc.
The schematic diagram of stream when Figure 12 is the defrosting running representing the heat pump circulating system of the 5th embodiment and chilled(cooling) water return (CWR) etc.
The schematic diagram of stream when Figure 13 is the cooling operation representing the heat pump circulating system of the 5th embodiment and chilled(cooling) water return (CWR) etc.
The schematic diagram of stream when Figure 14 is the warming operation representing the heat pump circulating system of the 6th embodiment of the present invention and chilled(cooling) water return (CWR) etc.
The schematic diagram of stream when Figure 15 is the warm-operation representing the heat pump circulating system of the 6th embodiment and chilled(cooling) water return (CWR) etc.
The schematic diagram of stream when Figure 16 is the cooling operation representing the heat pump circulating system of the 6th embodiment and chilled(cooling) water return (CWR) etc.
Figure 17 is the schematic stereogram for illustration of the refrigerant flowing in the compound heat exchanger of variation of the present invention and flow of cooling water.
Detailed description of the invention
Hereinafter, with reference to the accompanying drawings of for implementing multiple mode of the present invention.In each mode, mark identical reference marks to the part corresponding with the item illustrated in mode formerly, the repetitive description thereof will be omitted sometimes.When being only described a part for structure in each mode, other parts for structure can be applied in other modes first illustrated.Not only the part combination with one another that can combine can be specifically expressed in each embodiment, as long as do not produce special obstacle during combination, also can by embodiment local combination each other even without expressing.
(the first embodiment)
According to Fig. 1 ~ Fig. 7, the first embodiment of the present invention is described.In the present embodiment, heat-exchange system of the present invention is applied to from internal combustion engine (engine) and traveling electro-motor MG obtain the driving force that vehicle travels, the air conditioner for vehicles 1 of so-called motor vehicle driven by mixed power.
Motor vehicle driven by mixed power can make engine action or stopping in the travel load according to vehicle etc. and the transport condition obtaining driving force to travel from engine and these both sides of traveling electro-motor MG, make engine stop and switch between transport condition only obtaining driving force to travel from traveling electro-motor MG etc.Thus, motor vehicle driven by mixed power relative to only can from engine obtain vehicle travel driving force common vehicle for, motor vehicle fuel utilization rate can be improved.
The heat-exchange system being applied to the air conditioner for vehicles 1 of present embodiment comprises: as the heat pump circulating system 10 of the cooling cycle system of steam compression type; And the cooling water circulation loop 40 etc. of cooling water circulation for cooling traveling electro-motor MG.
First, heat pump circulating system 10 plays the function of cooling to the wind pushing air of the indoor air-supply of car as air-conditioning object space in air conditioner for vehicles 1.In this heat pump circulating system 10, adopt common freon system refrigerant as refrigerant, form the subcritical refrigeration cycle system that high-pressure side refrigerant pressure is no more than the critical pressure of refrigerant.It should be noted that, in refrigerant, be mixed into the refrigerator oil for lubricating compressor 11, a part for refrigerator oil circulates together with refrigerant in the circulatory system.
Compressor 11 is configured in engine room, sucks refrigerant in heat pump circulating system 10, is compressed and the component of discharging, and is the motor compressor utilizing electro-motor 11b to drive the fixed capacity type compressor 11a that discharge capacity is fixed.As fixed capacity type compressor 11a, specifically, the various compressing mechanism such as Scrawl compressor structure, blade-tape compressor structure can be adopted.
Electro-motor 11b is the component being controlled its action (revolution) by the control signal exported from control device described later, can adopt the arbitrary form in alternating current motor, d.c. motor.Further, control by this revolution the refrigerant discharge ability changing compressor 11.Therefore, in the present embodiment, electro-motor 11b forms the discharge ability change mechanism of compressor 11.
The refrigerant inlet side of refrigerant radiator 12 is connected with the coolant outlet port of compressor 11.Refrigerant radiator 12 is configured in engine room, makes the discharge refrigerant (first fluid) of discharging from compressor carry out heat exchange with the extraneous gas as heat exchange subject fluid (the 3rd fluid) transported from Air Blast fan 13 and the heat externally gas heat release heat exchanger of releasing that discharge refrigerant is had.
In addition, Air Blast fan 13 is the electrodynamic type pressure fan being controlled running rate, i.e. revolution (wind pushing air amount) by the control voltage exported from control device.Further, the refrigerant radiator 12 of present embodiment is integrally formed with making the radiator described later (thermal medium radiator) 43 carrying out heat exchange as cooling water (second fluid) and the extraneous gas transported from Air Blast fan 13 of thermal medium cool traveling electro-motor MG.
Therefore, the Air Blast fan 13 of present embodiment forms the outdoor draft fan structure blowing extraneous gas towards refrigerant radiator 12 and these both sides of radiator 43.It should be noted that, the refrigerant radiator 12 of integration and the detailed construction of radiator 43 (heat exchanger 70 hereinafter referred to as compound) are in rear explanation.
Be configured with in the refrigerant exit side of refrigerant radiator 12 and make the refrigerant gas-liquid separation from refrigerant radiator 12 outflow and the holder 14 storing unnecessary liquid phase refrigerant.Further, be connected with the entrance side of temperature-type expansion valve 15 at the liquid phase refrigerant exit of holder 14, be connected with the refrigerant inlet side of refrigerant evaporator 16 at the outlet side of temperature-type expansion valve 15.
Temperature-type expansion valve 15 is following mechanisms of decompressor: have the not shown temperature-sensitive portion in the coolant path being configured in refrigerant evaporator 16 outlet side, temperature and pressure based on refrigerant evaporator 16 outlet side refrigerant detects the degree of superheat of refrigerant evaporator 16 outlet side refrigerant, becomes the mode of the value of the prescribed limit preset by mechanical institutional adjustment valve opening (cold medium flux) to make the degree of superheat of refrigerant evaporator 16 outlet side refrigerant.
Refrigerant evaporator 16 is following heat exchanger for coolings: be configured in the housing 31 of room conditioning unit 30, make to utilize the low pressure refrigerant of temperature-type expansion valve 15 puffing carry out heat exchange with the wind pushing air blowed to the indoor air-supply of car and low pressure refrigerant is evaporated, thus wind pushing air is cooled.The refrigerant suction inlet of compressor 11 is connected with in the refrigerant exit side of refrigerant evaporator 16.
Next, room conditioning unit 30 is described.Room conditioning unit 30 is configured in the inner side of the instrument board (dashboard console) of the indoor forefront of car, in the housing 31 forming its shell, contain pressure fan 32, described refrigerant evaporator 16, electric heater 36 etc.
Housing 31 is formed with the air flue of wind pushing air blowed to car indoor therein, by the elasticity had to a certain degree and the also good resin (such as, polypropylene) of intensity be shaped.Wind pushing air flowing side, most upstream in housing 31 is configured with the inside and outside gas switching device shifter 33 switching and import car room air (internal gas) and extraneous gas.
Inside and outside gas switching device shifter 33 is formed the extraneous gas introducing port of the internal gas introducing port importing internal gas in housing 31 and importing extraneous gas.And, be configured with inside and outside gas in the inside of inside and outside gas switching device shifter 33 and switch door, this inside and outside gas switches the aperture area that door adjusts internal gas introducing port and extraneous gas introducing port continuously, and the air quantity ratio of the air quantity of internal gas and the air quantity of extraneous gas is changed.
The pressure fan 32 blowed to car indoor by the air sucked via inside and outside gas switching device shifter 33 is configured with in the air flow downstream side of inside and outside gas switching device shifter 33.This pressure fan 32 is the electric blowing machines by electrical motor driven centrifugal multi-blade fan (Sirocco fan), and its revolution (air output) is controlled by the control voltage exported from control device.
In the air flow downstream side of pressure fan 32, be configured with refrigerant evaporator 16 and electric heater 36 successively relative to the flowing of wind pushing air.In other words, refrigerant evaporator 16 is configured in the flow direction upstream side of wind pushing air relative to electric heater 36.Electric heater 36 has PTC element (positive temperature coefficient thermis), to be generated heat by control device to PTC component feeding electric power thus is heated by the heating arrangements of the air after refrigerant evaporator 16.
And, in the air flow downstream side of refrigerant evaporator 16 and the air of electric heater 36 flowing upstream side is configured with air mix door 34, this air mix door 34 adjust in the wind pushing air after by refrigerant evaporator 16, by the air quantity ratio of electric heater 36.In addition, be provided with blending space 35 in the air flow downstream side of electric heater 36, this blending space 35 make to carry out heat exchange via electric heater 36 and refrigerant and by warmed-up wind pushing air with walk around electric heater 36 and do not mixed by the wind pushing air heated.
Be configured with at the blow-off outlet of the mixed air-conditioning wind direction of blending space 35 as the indoor blowout of car of cooling object space in the air flowing most downstream portion of housing 31.Specifically, the facial blow-off outlet towards the upper part of the body blowout air-conditioner wind of the passenger of car indoor, the foot blow-off outlet of pin limit blowout air-conditioner wind towards passenger and the defrosting blow-off port (all not shown) towards vehicle front windshield medial surface blowout air-conditioner wind is provided with as this blow-off outlet.
Therefore, adjusted by the ratio of air mix door 34 to the air quantity by electric heater 36, thus the temperature of the air-conditioner wind be mixed with at blending space 35 is adjusted, the temperature of the air-conditioner wind blown out from each blow-off outlet is adjusted.In other words, air mix door 34 forms the temperature adjusting mechanism of adjustment to the temperature of the air-conditioner wind of the indoor air-supply of car.It should be noted that, the not shown servo motor driven that air mix door 34 is controlled by the control signal exported from control device by action.
Further, the defrosting door (all not shown) of the facial door of the aperture area adjusting facial blow-off outlet, the foot door of the aperture area of adjustment foot blow-off outlet, the aperture area of adjustment defrosting blow-off port is configured with respectively at the air flowing upstream side of facial blow-off outlet, foot blow-off outlet and defrosting blow-off port.
These facial doors, foot door, defrosting door form the blow-off outlet pattern switching mechanism switching blow-off outlet pattern, the not shown servo motor driven controlled by the control signal exported from control device by its action via linkage etc.
Next, cooling water circulation loop 40 is described.Cooling water circulation loop 40 makes the cooling water (such as, glycol water) as thermal medium circulate in the cooling water path of inside being formed at the traveling electro-motor MG as the mobile unit generated heat adjoint during action and cool the thermal medium closed circuit of traveling electro-motor MG.Cooling water pump 41, radiator 43 is configured with in this cooling water circulation loop 40.
Cooling water pump 41 is the DYN dynamic water pumps carrying cooling water in cooling water circulation loop 40 to the cooling water path pressure of the inside being formed at traveling electro-motor MG, and its revolution (flow) is controlled by the control signal exported from control device.
Further, when control device makes cooling water pump 41 action, cooling water is according to the sequential loop of cooling water pump 41 → traveling electro-motor MG → radiator 43 → cooling water pump 41.Therefore, cooling water pump 41 forms the thermal medium flow rate adjusting mechanism (second fluid flow rate adjusting mechanism) of the inflow flow of the cooling water that adjustment flows into radiator 43.
Radiator 43 is configured in engine room, makes the cooling water (second fluid) that flows out from the cooling water path of the inside being formed at traveling electro-motor MG and extraneous gas (the 3rd fluid) heat exchange that transports from Air Blast fan 13 and the heat externally gas heat release heat exchanger of releasing that cooling water is had.
Therefore, in this cooling water circulation loop 40, when control device makes cooling water pump 41 action, cooling water by traveling with electro-motor MG when, absorb the used heat of traveling electro-motor MG and cool traveling electro-motor MG.Further, the externally gas heat release and being cooled of the used heat of traveling electro-motor MG and cooling water inflow radiator 43 after heating up is absorbed.In other words, traveling electro-motor MG plays the function as the external heat source adding hot cooling water.
Next, the detailed construction of Fig. 2 ~ Fig. 6 to compound heat exchanger 70 is used to be described.First, compound heat exchanger 70 is that refrigerant radiator 12 and radiator 43 are configured to the compound heat exchanger of one as a heat exchanger.Refrigerant radiator 12 and radiator 43 are configured to the heat exchanger of so-called container-cast, and a pair set with the set or distribution making many pipe 12a, 43a of refrigerant or cooling water circulation respectively, be configured in the both end sides of these many pipes and carry out refrigerant or the cooling water circulated in each pipe divides adapted container 12b, 43b etc.
Compound heat exchanger 70 possesses at internal circulation as the refrigerant pipe 12a of the refrigerant of first fluid and at the cooling water pipe 43a of internal circulation as the cooling water of second fluid.
At this, multiple refrigerant pipe 12a is divided into multiple groups, the multiple groups of passages being the refrigerant making to distribute from the same space respectively and flowing to same direction of refrigerant pipe 12a.In addition, refrigerant pipe 12a has the passage of most downstream side and the most downstream side refrigerant pipe 121a (most downstream side first is managed) of final passage that form refrigerant flow direction.
Compound heat exchanger 70 has the first core 701 be only made up of most downstream side refrigerant pipe 121a and the second core 702 be made up of refrigerant pipe 12a and these both sides of cooling water pipe 43a.In other words, in compound heat exchanger 70, the heat exchange department be only made up of most downstream side refrigerant pipe 121a i.e. the first core 701 is arranged independently with other heat exchange departments i.e. the second core 702.
In the present embodiment, second core 702 forms the condensation part making the high pressure refrigerant heat release of circulating in refrigerant pipe 12a and condensation, and the liquid phase refrigerant that the first core 701 is formed flowing out from the second core 702 (condensation part) carries out overcooled supercooling portion.
More particularly, the upstream side heat exchange department 71 that compound heat exchanger 70 possesses laminated configuration refrigerant pipe 12a and cooling water pipe 43a and forms.Upstream side heat exchange department 71 is refrigerants of making to circulate in refrigerant pipe 12a and carry out heat exchange at the air as the 3rd fluid (extraneous gas from Air Blast fan 13 transports) of the ambient dynamic of refrigerant pipe 12a and make the cooling water circulated among cooling water pipe 43a and the heat exchange department carrying out heat exchange at the air (extraneous gas from Air Blast fan 13 transports) of the ambient dynamic of cooling water pipe 43a.
The position of formation first core 701 in upstream side heat exchange department 71 only laminated configuration most downstream side refrigerant pipe 121a and forming.On the other hand, the position of formation second core 702 in upstream side heat exchange department 71 alternately laminated configuration refrigerant pipe 12a and cooling water pipe 43a and forming.
The extraneous gas flow downstream side of upstream side heat exchange department 71 is provided with laminated configuration refrigerant pipe 12a and the downstream heat exchange department 72 formed.In other words, downstream heat exchange department 72 is only made up of refrigerant pipe 12a.Downstream heat exchange department 72 is the refrigerant making to circulate in refrigerant pipe 12a and the heat exchange department carrying out heat exchange at the air (extraneous gas from Air Blast fan 13 transports) of the ambient dynamic of refrigerant pipe 12a.
As refrigerant pipe 12a and cooling water pipe 43a, the shape adopting long side direction vertical section is the flat tube of flat pattern.More particularly, as refrigerant pipe 12a, adopt the pipe with the section shape of flat porous shape be shaped by extrusion process.In addition, as cooling water pipe 43a, the pipe with the section shape of flat two hole shapes by being formed by a sheet metal bending is adopted.
The refrigerant pipe 12a and the cooling water pipe 43a that form the second core 702 of upstream side heat exchange department 71 separate the predetermined distance alternately laminated configuration in ground in the mode that the tabular surface in its outer surface is parallel and opposed each other.Similarly, the most downstream side refrigerant pipe 121a forming the first core 701 of upstream side the heat exchange department 71 and refrigerant pipe 12a forming downstream heat exchange department 72 also separates predetermined distance ground laminated configuration respectively.
The refrigerant pipe 12a of formation second core 702 in upstream side heat exchange department 71 is configured between cooling water pipe 43a, and cooling water pipe 43a is configured between refrigerant pipe 12a.In addition, when observing from the flow direction of the extraneous gas transported by Air Blast fan 13, the refrigerant pipe 12a forming downstream heat exchange department 72 overlaps with the refrigerant pipe 12a or cooling water pipe 43a that form upstream side heat exchange department 71 and configures.
In heat exchanger 70, be formed in the space between refrigerant pipe 12a and cooling water pipe 43a that forms upstream side heat exchange department 71 and the space be formed between the adjacent refrigerant pipe 12a forming downstream heat exchange department 72 and form extraneous gas path 70a (the 3rd fluid path) for the outside air passes transported by Air Blast fan 13.
And, outside fin 70b is configured with in this extraneous gas path 70a, this outside fin 70b promotes refrigerant and the heat exchange of extraneous gas and the heat exchange of cooling water and extraneous gas, and the heat that can realize between the refrigerant that circulates in the refrigerant pipe 12a of formation upstream side heat exchange department 71 and the cooling water circulated in cooling water pipe 43a moves and the refrigerant heat each other that circulates in the adjacent refrigerant pipe 12a forming downstream heat exchange department 72 moves.
As this outside fin 70b, adopt the rugose corrugated fin that to be shaped by the light sheet bending of the metal of excellent thermal conductivity, in the present embodiment, by being engaged with the refrigerant pipe 12a and these both sides of cooling water pipe 43a forming upstream side heat exchange department 71 by this outside fin 70b, thus the heat that can realize between refrigerant pipe 12a and cooling water pipe 43a moves.Further, by outside fin 70b and the adjacent refrigerant pipe 12a forming downstream heat exchange department 72 being engaged with each other, the heat that can realize thus between adjacent refrigerant pipe 12a moves.
Outside fin 70b has the refrigerant pipe 12a thermally coupled portion of hot linked medium side (the first thermally coupled portion) 71b and by refrigerant pipe 12a and the thermally coupled portion of the hot linked cooling water side of cooling water pipe 43a (the second thermally coupled portion) 72b each other.Specifically, be configured in refrigerant pipe 12a outside fin 70b each other and there is the thermally coupled portion 71b of medium side.On the other hand, the outside fin 70b be configured between refrigerant pipe 12a and cooling water pipe 43a has medium side thermally coupled portion 71b and thermally coupled these both sides of portion 72b of cooling water side.
As mentioned above, the first core 701 of present embodiment only has most downstream side refrigerant pipe 121a.Therefore, in the first core 701, the number of the thermally coupled portion 72b of cooling water side is 0.Thus, in the first core 701, the number of medium side thermally coupled portion 71b is more than the number of cooling water side thermally coupled portion 72b.
The illusory pipe 77 that either party being configured with in refrigerant and cooling water does not all circulate between the most downstream side refrigerant pipe 121a and the cooling water pipe 43a forming the second core 702 of formation first core 701.This illusory pipe 77 can be hollow barrel-type shape, also can be solid (in other words, be not hollow) column.
Next, upstream side container part 73 and downstream container part 74 are described.Compound heat exchanger 70 possesses the upstream side container part 73 extended on the stacked direction of the refrigerant pipe 12a and cooling water pipe 43a that form upstream side heat exchange department 71 and the downstream container part 74 extended on the stacked direction of the refrigerant pipe 12a of formation downstream heat exchange department 72.
Be formed in upstream side container part 73 and carry out forming the set of cooling water or the upstream side cooling water space 731 of distribution of circulating in the cooling water pipe 43a of upstream side heat exchange department 71.In addition, the set of refrigerant pipe 12a or the downstream refrigerant space 741 of distribution carrying out forming downstream heat exchange department 72 is formed in downstream container part 74.
Upstream side container part 73 and downstream container part 74 form as one.Below, the parts that upstream side container part 73 is integrated with downstream container part 74 are called header tank 75.
Header tank 75 has: the tube plate 751 fixed for the refrigerant pipe 12a and these both sides of cooling water pipe 43a that are configured to two row on the flow direction of extraneous gas; Be fixed on the intermediate plate component 752 of tube plate 751; And container forms component 753.
Container forms component 753 and forms above-mentioned upstream side cooling water space 731 and downstream refrigerant space 741 therein by being fixed on tube plate 751 and intermediate plate component 752.Specifically, container forms component 753 by being formed as being two mountain shapes (W shape) when observing from its long side direction to flat metal enforcement punch process.
Further, engaged with intermediate plate component 752 by the central portion 753c of two mountain shapes container being formed component 753, thus mark off upstream side cooling water space 731 and downstream refrigerant space 741.
As shown in the sectional view of Fig. 4 and Fig. 5, intermediate plate component 752 is formed with multiple depressed part 752a, multiple depressed part 752a forms be communicated with cooling water pipe 43a multiple and connects the universal space 76 between tube plate 751 by being fixed on tube plate 751.
Be formed at the position corresponding with downstream refrigerant space 741 of the extraneous gas flow downstream side of depressed part 752a, i.e. downstream container part 74 through its show to carry on the back the first through hole 752b.Thus, connect the universal space 76 to be communicated with the downstream refrigerant space 741 of downstream container part 74.
Therefore, flow into from the refrigerant pipe 12a forming upstream side heat exchange department 71 refrigerant connecting the universal space 76 to flow out from the first through hole 752b to downstream refrigerant space 741.Thus, this connects the function of the universal space 76 performance as the access making the refrigerant pipe 12a of formation upstream side heat exchange department 71 be communicated with the downstream refrigerant space 741 of downstream container part 74.
Even the universal space 76 is along forming the refrigerant pipe 12a of upstream side heat exchange department 71 and form the direction extension connected to each other of in the refrigerant pipe 12a of downstream heat exchange department 72, overlap the refrigerant pipe 12a configured when the flow direction of extraneous gas is observed end.More particularly, connect the flow direction of the universal space 76 in the end of the refrigerant pipe 12a of the refrigerant pipe 12a and formation downstream heat exchange department 72 that form upstream side heat exchange department 71 along extraneous gas to extend.
In addition, intermediate plate component 752, the position corresponding with the cooling water pipe 43a forming upstream side heat exchange department 71 be provided with through its and show the second through hole 752c of carrying on the back.Form cooling water pipe 43a this second through hole through 752c of upstream side heat exchange department 71.Thus, the cooling water pipe 43a forming upstream side heat exchange department 71 be formed in the upstream side cooling water space 731 that container formed in component 753 and be communicated with.
Further, as shown in Figure 3, in the end of header tank 75 side of upstream side heat exchange department 71, cooling water is more outstanding to header tank 75 side than refrigerant pipe 12a with pipe 43a.In other words, the end of the end of header tank 75 side of refrigerant pipe 12a and header tank 75 side of cooling water pipe 43a does not line up configuration.
On the other hand, intermediate plate component 752, be provided with through its with not corresponding with connecting refrigerant pipe 12a that the universal space 76 the is communicated with position in the refrigerant pipe 12a forming downstream heat exchange department 72 and show the 3rd through hole 752d that carries on the back.Form in the refrigerant pipe 12a of downstream heat exchange department 72 not with the through 3rd through hole 752d of refrigerant pipe 12a connecting the universal space 76 and be communicated with.Thus, form in the refrigerant pipe 12a of downstream heat exchange department 72 not with connect refrigerant pipe 12a that the universal space 76 is communicated with and be formed in the downstream refrigerant space 741 that container formed in component 753 and be communicated with.
Further, as shown in Figure 3, in the end of header tank 75 side of downstream heat exchange department 72, with to connect the refrigerant pipe 12a that is communicated with of the universal space 76 more outstanding to header tank 75 side than the refrigerant pipe 12a be communicated with the company universal space 76.In other words, the end of adjacent refrigerant pipe 12a does not line up configuration each other.
It should be noted that, container forms the central portion 753c of component 753 and is formed as and the matched shape of depressed part 752a formed on intermediate plate component 752, and upstream side cooling water space 731 and downstream refrigerant space 741 are become by the model split that can not spill from the junction of tube plate 751 and intermediate plate component 752 with the cooling water of inside or refrigerant.
In addition, as shown in Figure 2, the long side direction end side (on the left of the paper in figure) of upstream side container part 73 (hereinafter referred to as the first upstream side container part 730a) of the long side direction end side (on the upside of the paper in figure) being configured at cooling water pipe 43a be connected with cooling water is flowed out from upstream side cooling water space 731 cooling water flow out of pipe arrangement 435.Be connected with in another side of long side direction (on the right side of the paper in figure) of upstream side container part 73 (hereinafter referred to as the second upstream side container part 730b) of another side of long side direction (on the downside of the paper in figure) being configured at cooling water pipe 43a and make the cooling water cooling water that upstream side cooling water space 731 flows into flow into pipe arrangement 434.
In addition, being connected with in the long side direction end side (on the left of the paper in figure) of downstream container part 74 (hereinafter referred to as the first downstream container part 740a) of the long side direction end side (on the upside of the paper in figure) being configured at refrigerant pipe 12a makes the refrigerant that refrigerant flows out from downstream refrigerant space 741 flow out pipe arrangement 125.Be connected with the refrigerant that refrigerant is flowed into downstream refrigerant space 741 in another side of long side direction (on the right side of the paper in figure) of downstream container part 74 (hereinafter referred to as the second downstream container part 740b) of another side of long side direction (on the downside of the paper in figure) being configured at refrigerant pipe 12a and flow into pipe arrangement 124.
In addition, as shown in the schematic stereogram of Fig. 6, be configured with at the first downstream container part 740a and downstream refrigerant space 741 is separated into two-part first downstream partition member 742a on the long side direction of the first downstream container part 740a.
Below, by in two the downstream refrigerant spaces 741 be separated out by the first downstream partition member 742a, the space that is communicated with the refrigerant pipe 12a beyond most downstream side refrigerant pipe 121a is called the first downstream refrigerant space 741a, to be directly communicated with flowing out pipe arrangement 125 with refrigerant and the space be communicated with most downstream side refrigerant pipe 121a is called the second downstream refrigerant space 741b.
In addition, be configured with at the second downstream container part 740b downstream refrigerant space 741 is separated into two-part second downstream partition member 742b on the long side direction of the second downstream container part 740b.
Below, by in two the downstream refrigerant spaces 741 be separated out by the second downstream partition member 742b, to flow into the space that pipe arrangement 124 is directly communicated with refrigerant and be called the 3rd downstream refrigerant space 741c, the space be communicated with most downstream side refrigerant pipe 121a and these both sides of refrigerant pipe 12a in addition thereof is called the 4th downstream refrigerant space 741d.
At this, when observing from the flow direction X of extraneous gas, the first downstream partition member 742 is configured in the side of flowing out pipe arrangement 125 than the second downstream partition member 742b near refrigerant.
Therefore, in the heat exchanger 70 of present embodiment, as shown in the schematic stereogram of Fig. 6, flow into via refrigerant a part that pipe arrangement 124 flow into the refrigerant of the 3rd downstream refrigerant space 741c of the second downstream container part 740b to flow into the refrigerant pipe 12a of the second core 702 forming downstream heat exchange department 72, flow towards upside from the downside figure in this refrigerant pipe 12a.In addition, flow into another part of the refrigerant of the 3rd downstream refrigerant space 741c of the second downstream container part 740b via the company's universal space 76 be formed between tube plate 751 and intermediate plate component 752, refrigerant to the second core 702 forming upstream side heat exchange department 71 flows into pipe 12a, flows in this refrigerant pipe 12a from the downside figure towards upside.
Gather at the first downstream refrigerant space 741a of the first downstream container part 740a from the refrigerant of the second core 702 forming downstream heat exchange department 72 with the refrigerant that pipe 12a flows out.In addition, the refrigerant flowed out from the refrigerant pipe 16a of the second core 702 forming upstream side heat exchange department 71, via the company's universal space 76 be formed between tube plate 751 and intermediate plate component 752, is gathered at the first downstream refrigerant space 741a of the first downstream container part 740a.
Refrigerant after the first downstream refrigerant space 741a of the first downstream container part 740a gathers flows from the right side figure towards left side.Then, the part of refrigerant after the first downstream refrigerant space 741a of the first downstream container part 740a gathers flows into the refrigerant of the second core 702 forming downstream heat exchange department 72 with pipe 16a, flows in this refrigerant pipe 16a from the upside figure towards downside.In addition, another part of refrigerant after the first downstream refrigerant space 741a of the first downstream container part 740a gathers is via the company's universal space 76 be formed between tube plate 751 and intermediate plate component 752, refrigerant to the second core 702 forming upstream side heat exchange department 71 flows into pipe 16a, flows in this refrigerant pipe 16a from the upside figure towards downside.
Gather at the 4th downstream refrigerant space 741d of the second downstream container part 740b from the refrigerant of the second core 702 forming downstream heat exchange department 72 with the refrigerant that pipe 16a flows out.In addition, the refrigerant flowed out from the refrigerant pipe 16a of the second core 702 forming upstream side heat exchange department 71, via the company's universal space 76 be formed between tube plate 751 and intermediate plate component 752, is gathered at the 4th downstream refrigerant space 741d of the second downstream container part 740b.
Refrigerant after the 4th downstream refrigerant space 741d of the second downstream container part 740b gathers flows from the right side figure towards left side.Then, the part of refrigerant after the 4th downstream refrigerant space 741d of the second downstream container part 740b gathers flows into the most downstream side refrigerant of the first core 701 forming downstream heat exchange department 72 with pipe 121a, flows in this most downstream side refrigerant pipe 121a from the downside figure towards upside.In addition, another part of refrigerant after the 4th downstream refrigerant space 741d of the second downstream container part 740b gathers is via the company's universal space 76 be formed between tube plate 751 and intermediate plate component 752, most downstream side refrigerant to the first core 701 forming upstream side heat exchange department 71 flows into pipe 121a, flows in this most downstream side refrigerant pipe 121a from the downside figure towards upside.
Gather at the second downstream refrigerant space 741b of the first downstream container part 740a from the most downstream side refrigerant of the first core 701 forming downstream heat exchange department 72 with the refrigerant that pipe 121a flows out.In addition, the refrigerant flowed out from the most downstream side refrigerant pipe 121a of the first core 701 forming upstream side heat exchange department 71, via the company's universal space 76 be formed between tube plate 751 and intermediate plate component 752, is gathered at the second downstream refrigerant space 741b of the first downstream container part 740a.
Refrigerant after the second downstream refrigerant space 741b of the first downstream container part 740a gathers flows from the right side figure towards left side, flows out pipe arrangement 125 flow out from refrigerant.
On the other hand, in the heat exchanger 70 of present embodiment, as shown in the schematic stereogram of Fig. 6, the cooling water flowing into the upstream side cooling water space 731 of the second upstream side container part 730b via cooling water inflow pipe arrangement 434 flows into the cooling water pipe 43a forming upstream side heat exchange department 71, flows in this cooling water pipe 43a from the downside figure towards upside.
The cooling water flowed out from the cooling water pipe 43a forming upstream side heat exchange department 71 is gathered at the upstream side cooling water space 731 of the first upstream side container part 730a.Then, the cooling water after the upstream side cooling water space 731 of the first upstream side container part 730a is gathered, flows towards left side from the right side figure, and flows out from cooling water flow out of pipe arrangement 435.
In the present embodiment, the stream total sectional area forming multiple most downstream side refrigerant pipe 121a of the final passage (the first core 701) of refrigerant flowing is less than the stream total sectional area of side refrigerant pipe 122a (in front of most downstream, side first is managed) in front of multiple most downstreams of the passage before being formed near the refrigerant flowing of final passage.Namely, when observing heat exchanger 70 from the flow direction X of extraneous gas, the length of the stacked direction of the pipe 12a of the first core 701 is shorter near the heat exchange department (laminated configuration has the position of side refrigerant pipe 122a in front of multiple most downstream) of the passage before final passage than forming.
In above-mentioned heat exchanger 70, form refrigerant radiator 12 by the refrigerant pipe 16a forming upstream side heat exchange department 71 and these both sides of refrigerant pipe 16a of forming downstream heat exchange department 72, form radiator 43 by the cooling water pipe 43a forming upstream side heat exchange department 71.
In addition, refrigerant pipe 16a, the cooling water pipe 43a of above-mentioned heat exchanger 70, each component parts of header tank 75 and outside fin 70b are formed by identical metal material (being aluminium alloy in the present embodiment).Further, tube plate 751 and container form component 753 and fix by riveting under the state clipping intermediate plate component 752.
Further, heat exchanger 70 entirety of the state after riveted joint is fixing is put into heating furnace and is heated, and the solder be coated in advance on each component parts surface is melted, then, be cooled to solder and again solidify, thus each component parts is brazed integral.Thus, refrigerant radiator 12 and radiator 43 are integrated.
Refrigerant pipe 16a can be used as an example of the first pipe at internal circulation first fluid, and cooling water pipe 43a can be used as an example of the second pipe at internal circulation second fluid.In the present embodiment, as an example of first fluid, use refrigerant, as an example of second fluid, use cooling water.
Next, the electric control portion of present embodiment is described.Air conditioning control device is made up of the known microcomputer and peripheral circuit thereof comprising CPU, ROM and RAM etc., carry out various computing, process based on the air-conditioning control program be stored in its ROM, control the action of the various air-conditioning control equipments 11,13,41 be connected with outlet side etc.
In addition, the input side of air conditioning control device be connected with inspection vehicle indoor temperature internal gas sensor, detect the extraneous gas sensor of extraneous gas temperature, the sunshine amount of inspection vehicle indoor sunshine recorder, detect the blow out air temperature (evaporator temperature) of refrigerant evaporator 16 evaporator temperature sensor, detect compressor 11 and discharge the discharge refrigerant temperature sensor of refrigerant temperature, detect the sensor group of the various airconditioning control such as outlet refrigerant temperature sensor of refrigerant radiator 12 outlet side refrigerant temperature Te.
Further, be connected with the not shown guidance panel be configured near the indoor anterior instrument board of car at the input side of air conditioning control device, the operation signal from the various air-conditioning console switch be arranged on this guidance panel inputs to air conditioning control device.As the various air-conditioning console switch be arranged on guidance panel, be provided with the step switch of air conditioner for vehicles 1, the car indoor temperature configuration switch of setting car indoor temperature, the selector switch etc. of operation mode.
It should be noted that, air conditioning control device is that the controlling organization of the electro-motor 11b of control compressor 11 etc. is integrally constituted and controls the device of their action, but the structure of the action of the control compressor 11 in the present embodiment, in air conditioning control device (hardware and software) forms refrigerant discharges capability control unit.
Further, the air conditioning control device of the present embodiment detection signal had based on the sensor group of above-mentioned airconditioning control judges whether to produce at refrigerant radiator 12 structure (frosting decision mechanism) of frosting.Specifically, in the frosting decision mechanism of present embodiment, when the speed of a motor vehicle of vehicle be the predetermined benchmark speed of a motor vehicle (being 20km/h in the present embodiment) below and refrigerant radiator 12 outlet side refrigerant temperature Te is below 0 DEG C time, be judged as creating frosting at refrigerant radiator 12.
Next, the action of the air conditioner for vehicles 1 of the present embodiment in said structure is described.When under the state connecting (ON) at not shown vehicle starter switch, the step switch of the air conditioner for vehicles 1 of guidance panel connects (ON), control device performs the program of the airconditioning control be stored in advance in memory circuit.When executed, the programs, control device reads the detection signal of sensor group and the operation signal of guidance panel of above-mentioned airconditioning control.
Then, target temperature to the air of the indoor blowout of car and target blowout temperature TAO is calculated based on the value of detection signal and operation signal.Further, the operating state of the various air-conditioning control equipments be connected with the outlet side of control device is determined based on the target blowout temperature TAO calculated and the detection signal of sensor group.
Such as, the refrigerant of compressor 11 discharges ability, the control signal that namely exports to the electro-motor of compressor 11 determines as described below like that.First, based target blowout temperature TAO, maps the target evaporator blowout temperature TEO deciding refrigerant evaporator 16 with reference to the control be pre-stored within control device.
Then, based on this target evaporator blowout temperature TEO and the deviation of the blow out air temperature Te from refrigerant evaporator 16 that detected by evaporator temperature sensor, use FEEDBACK CONTROL gimmick, determine to make the blow out air temperature from refrigerant evaporator 16 control signal exported to the electro-motor of compressor 11 close to the mode of target evaporator blowout temperature TEO.
In addition, about the control signal that the servo motor to air mix door 34 exports, based target blowout temperature TAO and the blow out air temperature from refrigerant evaporator 16, map with reference to the control be pre-stored within control device, become to make the temperature to the air of the indoor blowout of car and determined by the mode of the temperature desired by the passenger of car indoor temperature configuration switch setting.
Further, the control signal etc. determined as described above is exported to various air-conditioning control equipment.Then, before being required that by guidance panel the action of air conditioner for vehicles 1 stops, in the control cycle of each regulation, repeat the control programs such as the operating state decision → control voltage of calculating → various air-conditioning control equipment of the reading of above-mentioned detection signal and operation signal → target blowout temperature TAO and the output of control signal.
Therefore, in heat pump circulating system 10, the discharge refrigerant of discharging from compressor 11 flows into refrigerant radiator 12, carries out heat exchange and heat release with the extraneous gas transported from Air Blast fan 13.It should be noted that, experimental study according to the present inventor is learnt, in this heat pump circulating system 10, when usually operating, the pressure of discharging refrigerant is more than benchmark refrigerant pressure P 1 (specifically about 1.5MPa), and the surface temperature (wall surface temperature) of the refrigerant pipe 12a of refrigerant radiator 12 now rises to 60 DEG C ~ about 65 DEG C under the effect of the high temperature refrigerant of discharging from compressor 11.
From refrigerant radiator 12 flow out refrigerant at holder 14 by gas-liquid separation.The liquid phase refrigerant flowed out from holder 14 is depressurized to be expanded to via temperature-type expansion valve 15 and becomes low pressure refrigerant.Now, temperature-type expansion valve 15 is with the mode regulating valve aperture making the degree of superheat of refrigerant evaporator 16 outlet side refrigerant become the value of the prescribed limit preset.
Be depressurized the low pressure refrigerant after expansion via temperature-type expansion valve 15 to flow into refrigerant evaporator 16, evaporate from the wind pushing air heat absorption transported by pressure fan 32.Thus, the wind pushing air to the indoor conveying of car is cooled.Sucked by compressor 11 from the refrigerant of refrigerant evaporator 16 outflow and be re-compressed.
On the other hand, in wind pushing air (cold wind) after being cooled via refrigerant evaporator 16, the wind pushing air (cold wind) of the air quantity corresponding to the aperture of air mix door 34 is electrically heated device 36 and heats, and in blending space 35 with walk around electric heater 36 wind pushing air come that flows and mix and adjusted temperature.Then, by the air-conditioner wind after adjustment temperature from blending space 35 via each blow-off outlet to the indoor blowout of car.
Under the air-conditioning wind action to the indoor blowout of this car, when the internal air temperature of car indoor is cooled to lower than extraneous gas temperature, realize the refrigeration of car indoor, internal air temperature is heated above the situation of extraneous gas temperature, realize the heating of car indoor.
As described above, in the present embodiment, the final passage flowed by refrigerant, as the first core 701 only formed by most downstream side refrigerant pipe 121a, forms supercooling portion by this first core 701.Therefore, the outside fin 70b being configured at the first core 701 does not arrange the thermally coupled portion 72b of cooling water side, the number of medium side thermally coupled portion 71b is more than the number of the thermally coupled portion 72b of cooling water side.Thus, the whole region being configured at the outside fin 70b of the first core 701 is used to the heat externally gas releasing that discharge refrigerant is had.
Therefore, according to the present embodiment, in the first core 701, the heat that the discharge refrigerant circulated in most downstream side refrigerant pipe 121a can be made to have is externally gas releasing fully, makes the refrigerant of refrigerant radiator 12 outlet side have desired degree of subcooling.
Thus, without the need to lengthening the most downstream side refrigerant pipe 121a forming the minimum supercooling portion (the first core 701) of the coefficient of overall heat transmission, namely without the need to shortening the refrigerant pipe 12a forming the large condensation part (the second core 702) of the coefficient of overall heat transmission, therefore, it is possible to suppress the reduction of the heat exchange performance of heat exchanger 70 entirety.
At this, the relation of the exothermicity of in compound heat exchanger, degree of subcooling and medium side is shown in Figure 7.In the figure 7, the experimental result of the compound heat exchanger 70 representing present embodiment is marked and drawed by four directions.First core 701 is not set by triangle plotting expression and in the whole region of heat exchanger, is configured with the experimental result of the heat exchanger of the comparative example of cooling water pipe 43a.
As shown in Figure 7, when when going for the degree of subcooling of the regulation in compound heat exchanger, in the heat exchanger of comparative example, owing to being subject to the impact of the heat release of cooling water side, therefore the exothermicity of medium side reduces.On the other hand, as in this embodiment, by arranging the first core 701, thus the exothermicity of medium side can be made to increase.
In addition, in the present embodiment, form refrigerant pipe 12a and the cooling water pipe 43a alternately laminated configuration of the second core 702, refrigerant pipe 12a and cooling water pipe 43a is thermally coupled via outside fin 70b.Therefore, when the surface temperature of cooling water pipe 43a and the surface temperature of refrigerant pipe 12a there are differences, in outside fin 70b, correspondingly adjusted by with temperature difference with the scope of the heat externally gas heat release making refrigerant have for the heat scope that externally gas is released making cooling water have, thus the heat that has of cooling water and discharge heat that refrigerant has by suitably externally gas release.
Such as, when needing the heat that cooling water and the cooling water of discharging in refrigerant have to release, cooling water pipe 43a surface temperature uprises, and compares greatly with refrigerant pipe 12a with the temperature difference of extraneous gas.Now, in outside fin 70b, for cooling water is had heat externally the gas scope of releasing than the heat making refrigerant have, externally the gas scope of releasing is large, the heat that cooling water has externally gas releasing.
Thus, in refrigerant radiator 12, the heat that discharge refrigerant can be made to have externally gas is released, and in radiator 43, the heat that cooling water can be made to have externally gas is released.Consequently, suitable heat exchange can be carried out between the fluid of multiple fluid.
At this, the refrigerant of the second core 702 of the downstream heat exchange department 72 in formation upstream side heat exchange department 71 and downstream heat exchange department 72 is with in pipe 12a and cooling water pipe 43a, the surface temperature of two pipe 12a, 43a and the difference of extraneous gas temperature diminish, in as described above, outside fin 70b for cooling water is had heat externally the gas scope of releasing and the heat that refrigerant is had externally the gas scope of releasing diminished by the effect correspondingly adjusted with temperature difference.
On the other hand, in the present embodiment, in upstream side heat exchange department 71 and downstream heat exchange department 72, at least the second core 702 of upstream side heat exchange department 71 refrigerant pipe 12a and cooling water pipe 43a alternately laminated configuration is formed.Thus, in outside fin 70b, for cooling water is had heat externally the gas scope of releasing and the heat scope that externally gas is released that refrigerant is had correspondingly adjusted by with temperature difference, the heat that cooling water can be made to have and discharge the heat suitably externally gas releasing that refrigerant has.
In addition, in the present embodiment, the illusory pipe 77 that either party being configured with in refrigerant and cooling water does not all circulate between the most downstream side refrigerant pipe 121a and the cooling water pipe 43a forming the second core 702 of formation first core 701.Therefore, it is possible to suppress to cause producing the thermal stress of adjoint thermal deformation in pipe 12a, 43a or header tank 75 because of the different of the thermal expansion amount caused by the temperature difference of the refrigerant flowed in most downstream side refrigerant pipe 121a and the cooling water flowed in cooling water pipe 43a, make the situation of pipe 12a, 43a or header tank 75 breakage.
It should be noted that, in the first core 701 forming supercooling portion, in most downstream side refrigerant pipe 121a, flowing has liquid phase refrigerant, and therefore the pressure loss of refrigerant is little, but flow velocity is slow, and the coefficient of overall heat transmission is little.
On the other hand, in the present embodiment, the stream total sectional area forming multiple most downstream side refrigerant pipe 121a of the final passage (the first core 701) of refrigerant flowing is less near the stream total sectional area of side refrigerant pipe 122a in front of multiple most downstreams of the passage before final passage than being formed.Thereby, it is possible to accelerate the flow velocity of the refrigerant in the first core 701, improve the heat exchange performance of the first core 701.Thus, without the need to increasing the area of the first core 701 to obtain desired degree of subcooling, therefore, it is possible to increase the area of the second core 702, improve the heat exchange performance as heat exchanger 70 entirety.
(the second embodiment)
Next, based on Fig. 8, the second embodiment of the present invention is described.The difference of this second embodiment compared with above-mentioned first embodiment is, the first core 701 also has cooling water pipe 43a.It should be noted that, in fig. 8, in order to make diagram clear and definite, representing refrigerant pipe 12a with diagonal line, representing cooling water pipe 43a with a hatching.
As shown in Figure 8, in the first core 701 of the compound heat exchanger 70 of present embodiment, cooling water pipe 43a is provided with.In the present embodiment, at the first core 701, the radical (in this example being 9) of refrigerant pipe 12a is more than the radical (in this example being 1) of cooling water pipe 43a.In addition, on the surface of outside fin 70b, the flow direction along extraneous gas offers the vent window 700 being formed with multiple blind shaped.
Between in outside fin 70b, adjacent on the stacked direction of pipe 12a, 43a most downstream side refrigerant pipe 121a and cooling water pipe 43a, be formed with the table back of the body of through outside fin 70b and the first slit pore 70c of the externally flow direction extension of gas.The heat between most downstream side refrigerant pipe 121a adjacent on the stacked direction of pipe 12a, 43a and cooling water pipe 43a is suppressed to move by this first slit pore 70c.
In addition, be configured at the central portion of flow direction in the outside fin 70b between adjacent most downstream side refrigerant pipe 121a and cooling water pipe 43a, extraneous gas, be formed with the second slit pore 70d that the stacked direction along pipe 12a, 43a extends.The heat between most downstream side refrigerant pipe 121a adjacent on the flow direction of extraneous gas and cooling water pipe 43a is suppressed to move by this second slit pore 70d.
Thus, the first slit pore 70c of present embodiment and the second slit pore 70d uses as an example of insulation part of the present invention.It should be noted that, the first slit pore 70c and the second slit pore 70d also can be interconnected.
In the present embodiment, when the first core 701 is provided with cooling water pipe 43a, first slit pore 70c and the second slit pore 70d is set being configured at the outside fin 70b between most downstream side refrigerant pipe 121a and cooling water pipe 43a, thus suppresses the heat between most downstream side refrigerant pipe 121a and cooling water pipe 43a to move.In other words, be only provided with the thermally coupled portion 71b of medium side at the outside fin 70b being configured at the first core 701, the thermally coupled portion 72b of cooling water side is not set.
Thus, be configured at the outside fin 70b of the first core 701, the number of medium side thermally coupled portion 71b more than the number of the thermally coupled portion 72b of cooling water side, therefore, it is possible to obtain the effect same with above-mentioned first embodiment.
(the 3rd embodiment)
Next, based on Fig. 9, the 3rd embodiment of the present invention is described.The difference of this 3rd embodiment compared with above-mentioned first embodiment is, the flowing of the refrigerant in the first core 701 is different.
As shown in Figure 9, be configured with in the second upstream side container part 730b the interior of the container of upstream side cooling water space 731, second upstream side container part 730b is separated into two-part upstream side partition member 732a on long side direction.In two interior of the container be separated out by upstream side partition member 732a, (following near the space of the side (on the left of paper) of the first core 701, be called upstream side refrigerant space 731a) be communicated with most downstream side refrigerant pipe 121a, be not communicated with cooling water pipe 43a.Be connected with refrigerant at this upstream side refrigerant space 731a and flow out pipe arrangement 125.
In the present embodiment, refrigerant after the 4th downstream refrigerant space 741d of the second downstream container part 740b gathers flows into the most downstream side refrigerant of the first core 701 forming downstream heat exchange department 72 with pipe 121a, flows in this most downstream side refrigerant pipe 121a from the downside figure towards upside.The refrigerant flowed out from the most downstream side refrigerant pipe 121a of the first core 701 forming downstream heat exchange department 72 is via the company's universal space 76 be formed between tube plate 751 and intermediate plate component 752, most downstream side refrigerant to the first core 701 forming upstream side heat exchange department 71 flows into pipe 121a, and flows from the upside figure towards downside in this most downstream side refrigerant pipe 121a.
Gather at the upstream side refrigerant space 731a of the second upstream side container part 730b from the most downstream side refrigerant of the first core 701 forming upstream side heat exchange department 71 with the refrigerant that pipe 121a flows out.Refrigerant after the upstream side refrigerant space 731a of the second upstream side container part 730b gathers flows from the right side figure towards left side, flows out pipe arrangement 125 flow out from refrigerant.
As described above, in the present embodiment, at the first core 701, the refrigerant flowed out from the most downstream side refrigerant pipe 121a forming downstream heat exchange department 72 flows into the most downstream side refrigerant pipe 121a forming upstream side heat exchange department 71.In other words, the flow direction of refrigerant in the first core 701 and the flow direction of extraneous gas become counter current flow.Thus, in the first core 701, the heat that the refrigerant flowed in most downstream side refrigerant pipe 121a can be made to have is externally gas releasing expeditiously.
(the 4th embodiment)
Next, based on Figure 10, the 4th embodiment of the present invention is described.This 4th embodiment difference compared with the first embodiment is, the flow of cooling water in heat exchanger 70 is different.
As shown in Figure 10, the long side direction end side (on the left of the paper in figure) of the second upstream side container part 730b be connected with cooling water is flowed out from upstream side cooling water space 731 cooling water flow out of pipe arrangement 435.Be connected with in another side of long side direction (on the right side of the paper in figure) of the first upstream side container part 730a and make the cooling water cooling water that upstream side cooling water space 731 flows into flow into pipe arrangement 434.
Therefore, in the heat exchanger 70 of present embodiment, the cooling water flowing into the upstream side cooling water space 731 of the first upstream side container part 730a via cooling water inflow pipe arrangement 434 flows into the cooling water pipe 43a forming upstream side heat exchange department 71, flows in this cooling water pipe 43a from the upside figure towards downside.
The cooling water flowed out from the cooling water pipe 43a forming upstream side heat exchange department 71 is gathered at the upstream side cooling water space 731 of the second upstream side container part 730b.Then, the cooling water after the upstream side cooling water space 731 of the second upstream side container part 730b is gathered flows from the right side figure towards left side, flows out from cooling water flow out of pipe arrangement 435.
In the present embodiment, the flow direction of the refrigerant circulated in side refrigerant pipe 122a in front of most downstream with most downstream in front of the adjacent configuration of side refrigerant pipe 122a cooling water pipe 43a in the flow direction of cooling water that circulates be equidirectional.In other words, the flowing of the refrigerant circulated in side refrigerant pipe 122a in front of most downstream with most downstream in front of the adjacent configuration of side refrigerant pipe 122a cooling water pipe 43a in the flowing of cooling water of circulating be parallel flow.
According to the present embodiment, can suppress in the passage before the final passage flowed near refrigerant, the refrigerant circulated in side refrigerant pipe 122a in front of most downstream and the cooling water circulated in cooling water pipe 43a carry out the situation of heat exchange via outside fin 70b.The heat heating that water has therefore, it is possible to the refrigerant before suppression inflow first core 701 is cooled.
(the 5th embodiment)
Next, based on Figure 11 ~ Figure 13, the 5th embodiment of the present invention is described.In the present embodiment, as shown in the overall structure figure of Figure 11 ~ Figure 13, the example of the formation changing heat pump circulating system 10 and cooling water circulation loop 40 relative to the first embodiment is described.
The heat pump circulating system 10 of present embodiment is in air conditioner for vehicles 1, play subtend carries out the steam compression type of the function heating or cool cooling cycle system as the indoor wind pushing air of car of the indoor conveying of car of air-conditioning object space.Therefore, this heat pump circulating system 10 can perform warming operation (adding heat run) that heating heats to car indoor as the indoor wind pushing air of car of heat exchange subject fluid, the indoor wind pushing air of cooling vehicle and the cooling operation (cooling running) that freezes to car indoor by switching refrigerant flow.
And, in this heat pump circulating system 10, defrosting running can also being performed, in defrosting running, being removed as making the evaporimeter of the refrigerant evaporation frost played on the outdoor heat converter 160 of the described later compound heat exchanger 70 of function melt when making to be attached to warming operation.It should be noted that, in the overall structure figure shown in the heat pump circulating system 10 of Figure 11 ~ Figure 13, the flowing of refrigerant when representing each running with solid arrow.
The refrigerant inlet side as the indoor condenser 120 utilizing side heat exchanger is connected with in the coolant outlet port of compressor 11.Indoor condenser 120 be the room conditioning unit 30 being configured in air conditioner for vehicles 1 housing 31 in and make the HTHP refrigerant circulated and the heat-up heat exchanger being carried out heat exchange by the indoor wind pushing air of the car after indoor evaporator 20 described later therein.It should be noted that, about the detailed construction of room conditioning unit 30 in rear explanation.
When being connected with warming operation in the refrigerant exit side of indoor condenser 120 as the mechanism of decompressor of the warming operation of the refrigerant puffing that condenser 120 is indoor flowed out heating fixed restriction part 130.As this heating fixed restriction part 130, throttle orifice, capillary etc. can be adopted.The refrigerant inlet side of the outdoor heat converter 160 of compound heat exchanger 70 is connected with at the outlet side of heating fixed restriction part 130.
Further, be connected with in the refrigerant exit side of indoor condenser 120 and make refrigerant that condenser 120 indoor flows out walk around heating fixed restriction part 130 and the fixed restriction that guides to outdoor heat converter 160 side is walked around with path 140.Walk around in this fixed restriction, with being configured with in path 140, the open and close valve 15a carrying out opening and closing with path 140 is walked around to fixed restriction.Open and close valve 15a is the magnetic valve that its on-off action is controlled by the control voltage exported from air conditioning control device.
In addition, refrigerant is minimum with respect to the pressure loss produced during fixed restriction part 130 by the pressure loss produced during open and close valve 15a.Therefore, the refrigerant that condenser 120 flows out indoor is walked around via fixed restriction when open and close valve 15a opens and is flowed into path 140 side direction outdoor heat converter 160, flows into via heating fixed restriction part 130 when open and close valve 15a closes to outdoor heat converter 160.
Thus, open and close valve 15a can switch the refrigerant flow of heat pump circulating system 10.Therefore, the open and close valve 15a of present embodiment plays the function as refrigerant flow switching mechanism.It should be noted that, as such refrigerant flow switching mechanism, the triple valve etc. switching the refrigerant loop be connected with heating fixed restriction part 130 entrance side by indoor condenser 120 outlet side and the electric indoor condenser 120 outlet side being walked around the refrigerant loop be connected with path 140 entrance side with fixed restriction also can be adopted.
Outdoor heat converter 160 is the heat exchange departments making to carry out at refrigerant and the extraneous gas transported from Air Blast fan 17 of the internal circulation of heat exchanger 70 heat exchange.This outdoor heat converter 160 is configured in engine room, when warming operation, the evaporation heat exchanger (evaporimeter) playing heat-absorbing action as making low pressure refrigerant evaporate plays function, at cooling operation constantly as making the heat release heat exchanger (radiator) of high pressure refrigerant heat release play function.
In addition, Air Blast fan 17 is electrodynamic type pressure fan that running rate, i.e. revolution (wind pushing air amount) are controlled by the control voltage exported from air conditioning control device.
Further, in the heat exchanger 70 of present embodiment, above-mentioned outdoor heat converter 160 is formed integratedly with the radiator 43 making the cooling water of cooling traveling electro-motor MG and the extraneous gas transported from Air Blast fan 17 carry out heat exchange.
Therefore, the Air Blast fan 17 of present embodiment forms the outdoor draft fan structure carrying extraneous gas towards outdoor heat converter 160 and these both sides of radiator 43.It should be noted that, the detailed construction of the compound heat exchanger 70 that outdoor heat converter 160 and radiator 43 are formed integratedly is identical with above-mentioned first embodiment, therefore detailed description is omitted, but specifically, make the refrigerant radiator 12 of the first embodiment in compound heat exchanger 70 play function as outdoor heat converter 160.
The triple valve 15b of electric is connected with at the outlet side of outdoor heat converter 160.The action of this triple valve 15b is controlled by the control voltage exported from air conditioning control device, forms refrigerant flow switching mechanism together with above-mentioned open and close valve 15a.In air conditioning control device, to control the action of various equipment 15a, 15b of forming refrigerant flow switching mechanism Structure composing refrigerant flow controlling organization, controls the Structure composing chilled(cooling) water return (CWR) controlling organization of the action of the triple valve 42 of the loop switch mechanism forming cooling water.The outlet refrigerant temperature sensor 51 of sensing chamber's outer heat-exchanger 160 outlet side refrigerant temperature Te is provided with in present embodiment.
More particularly, triple valve 15b switches to the refrigerant flow be connected with the entrance side of reservoir 18 described later by the outlet side of outdoor heat converter 160 when warming operation, switch to the refrigerant flow be connected with the entrance side of cooling fixed restriction part 19 by the outlet side of outdoor heat converter 160 when cooling operation.
The mechanism of decompressor of the cooling operation of cooling fixed restriction part 19 makes heat exchanger 160 outdoor flow out refrigerant puffing when being cooling operations, its basic structure is identical with heating fixed restriction part 130.The refrigerant inlet side of indoor evaporator 20 is connected with at the outlet side of cooling fixed restriction part 19.
Indoor evaporator 20 be configured in the housing 31 of room conditioning unit 30 than indoor condenser 120 by air flowing upstream side, make the indoor wind pushing air of the refrigerant that circulates and car carry out the heat exchanger for cooling of heat exchange and cooling vehicle indoor wind pushing air therein.The entrance side of reservoir 18 is connected with in the refrigerant exit side of indoor evaporator 20.
Reservoir 18 is the gas-liquid separation of refrigerant by flowing into its inside thus stores the gas-liquid separator of the low-pressure side refrigerant of the unnecessary refrigerant in the circulatory system.The suction side of compressor 11 is connected with in the gas phase refrigerant outlet of reservoir 18.Therefore, this reservoir 18 suppresses liquid phase refrigerant to be sucked by compressor 11, thus realizes the function preventing the liquid compression of compressor 11.
In the heat pump circulating system 10 of present embodiment, when cooling operation, the temperature of the refrigerant that the temperature of the cooling water flowed out from the radiator 43 of heat exchanger 70 flows out lower than the outdoor heat converter 160 from heat exchanger 70.Thus, at outdoor heat converter 160 as when making the heat release heat exchange department of high pressure refrigerant heat release play the cooling operation of function, the degree of subcooling of the refrigerant that heat exchanger 160 outdoor can be made to flow out rises, therefore, it is possible to improve circulatory system efficiency.
On the other hand, in the heat pump circulating system 10 of present embodiment, when warming operation, the temperature of the refrigerant that the temperature of the cooling water of radiator 43 inside of heat exchanger 70 flows out higher than the outdoor heat converter 160 from heat exchanger 70.Thus, when outdoor heat converter 160 to play heat-absorbing action evaporation heat exchanger as making low pressure refrigerant evaporate plays the warming operation of function, refrigerant is heated by the heat absorbing cooling water and have, and promotes the evaporation of refrigerant.
Next, about room conditioning unit 30, only the part different from above-mentioned first embodiment is described.Room conditioning unit 30 is configured in the inner side of the instrument board (dashboard console) of the indoor forefront of car, in the housing 31 forming its shell, contain pressure fan 32, described indoor condenser 120, indoor evaporator 20 etc.
In the air flow downstream side of pressure fan 32, be configured with indoor evaporator 20 and indoor condenser 120 successively relative to the flowing of the indoor wind pushing air of car.In other words, indoor evaporator 20 is configured in the flow direction upstream side of the indoor wind pushing air of car for indoor condenser 120.
Further, in the air flow downstream side of indoor evaporator 20 and the air of indoor condenser 120 flowing upstream side, adjustment is configured with by the air mix door 34 of the air quantity ratio by indoor condenser 120 in the wind pushing air after indoor evaporator 20.In addition, be provided with blending space 35 in the air flow downstream side of indoor condenser 120, this blending space 35 make to carry out heat exchange via indoor condenser 120 and refrigerant and by warmed-up wind pushing air with walk around indoor condenser 120 and do not mixed by the wind pushing air heated.
Next, about cooling water circulation loop 40, only the part different from above-mentioned first embodiment is described.Be configured with in this cooling water circulation loop 40 cooling water pump 41, the triple valve 42 of electric, compound heat exchanger 70 radiator 43, walk around this radiator 43 and Cooling Water flowing bypass 44 etc.The cooling-water temperature sensor 52 detecting cooling water temperature is configured with at the outlet side of cooling water pump 41.
Triple valve 42 switches and is connected with the outlet side of radiator 43 by the entrance side of cooling water pump 41 and makes cooling water to the chilled(cooling) water return (CWR) that radiator 43 flows into and be connected with the outlet side of bypass 44 by the entrance side of cooling water pump 41 and the chilled(cooling) water return (CWR) making cooling water walk around radiator 43 to flow.The action of this triple valve 42 is controlled by the control voltage exported from air conditioning control device, and this triple valve 42 forms the loop switch mechanism of chilled(cooling) water return (CWR).It should be noted that, triple valve 42 also plays as the function of control towards the cooling water influx controlling organization of the influx of the cooling water of radiator 43 by switching chilled(cooling) water return (CWR).
In other words, in the cooling water circulation loop 40 of present embodiment, as shown in the dotted arrows such as Figure 11, the chilled(cooling) water return (CWR) of the sequential loop making cooling water according to cooling water pump 41 → traveling electro-motor MG → radiator 43 → cooling water pump 41 can be switched and make cooling water according to the chilled(cooling) water return (CWR) of the sequential loop of cooling water pump 41 → traveling electro-motor MG → bypass 44 → cooling water pump 41.
Therefore, traveling electricity consumption move in the action of motor MG, when triple valve 42 switch to make cooling water walk around radiator 43 flow chilled(cooling) water return (CWR) time, cooling water not via radiator 43 heat release, and makes its temperature rise.In other words, when triple valve 42 being switched to make cooling water walk around chilled(cooling) water return (CWR) that radiator 43 flows, the heat (caloric value) that traveling electro-motor MG has is stored in cooling water.
In the cooling water circulation loop 40 of present embodiment, the temperature of the cooling water flowed out from the radiator 43 of heat exchanger 70 becomes predetermined fiducial temperature (being 65 DEG C in the present embodiment) below.Thereby, it is possible to protect the inverter of traveling electro-motor MG from high temperature.
Outdoor heat converter 160 is configured in engine room, plays function as the heat release heat exchanger making cooling water and the extraneous gas transported from Air Blast fan 17 carry out heat exchange.As mentioned above, radiator 43 forms compound heat exchanger 70 together with outdoor heat converter 160.
Next, the action of the air conditioner for vehicles 1 of the present embodiment in said structure is described.In the air conditioner for vehicles 1 of present embodiment, can perform the indoor warming operation heated of car and the cooling operation freezed to car indoor, and defrosting running can be performed when warming operation.Action in each running is below described.
(a) warming operation
When under the state that the step switch at guidance panel connects (ON), during by selector switch selection warming operation pattern, warming operation starts.Further, when warming operation, defrosting running is performed when being judged that by frosting decision mechanism outdoor heat converter 160 creates frosting.
First, when common warming operation, air conditioning control device is closed open and close valve 15a and triple valve 15b is switched to the refrigerant flow be connected with the entrance side of reservoir 18 by the outlet side of outdoor heat converter 160, and, make cooling water pump 41 carry the mode action of the cooling water of predetermined regulation flow with pressure, and the triple valve 42 of cooling water circulation loop 40 is switched to cooling water and walk around the chilled(cooling) water return (CWR) that radiator 43 flows.
Thus, heat pump circulating system 10 switches to the refrigerant flow that refrigerant flows as shown in the solid arrow of Figure 11, and cooling water circulation loop 40 switches to the chilled(cooling) water return (CWR) that cooling water flows as shown in the dotted arrow of Figure 11.
In the structure of this refrigerant flow and chilled(cooling) water return (CWR), air conditioning control device reads the detection signal of sensor group and the operation signal of guidance panel of above-mentioned airconditioning control.Further, target temperature to the air of the indoor blowout of car and target blowout temperature TAO is calculated based on the value of detection signal and operation signal.
Further, the operating state of the various air-conditioning control equipments be connected with the outlet side of air conditioning control device is determined based on the target blowout temperature TAO calculated and the detection signal of sensor group.
Such as, the refrigerant of compressor 11 discharges ability, the control signal that namely exports to the electro-motor of compressor 11 determines as described below.First, based target blowout temperature TAO, maps with reference to the control be stored in advance in air conditioning control device, determines the target evaporator blowout temperature TEO of indoor evaporator 20.
Then, based on the deviation of this target evaporator blowout temperature TEO with the blow out air temperature from indoor evaporator 20 detected by evaporator temperature sensor, use FEEDBACK CONTROL gimmick, determine to make the blow out air temperature from indoor evaporator 20 control signal exported to the electro-motor of compressor 11 close to the mode of target evaporator blowout temperature TEO.
In addition, about the control signal that the servo motor to air mix door 34 exports, use target blowout temperature TAO, from the blow out air temperature of indoor evaporator 20 and discharge refrigerant temperature etc. by discharging the compressor 11 that detects of refrigerant temperature sensor, becoming to make the temperature to the air of the indoor blowout of car and being decided by the mode of the temperature desired by the passenger of car indoor temperature configuration switch setting.
It should be noted that, when common warming operation and when defrosting operates, also the aperture of air mix door 34 can be controlled to whole air quantity of the indoor wind pushing air of the car making to transport from pressure fan 32 by indoor condenser 120.
Further, the control signal etc. determined as described above is exported to various air-conditioning control equipment.Then, before being required that by guidance panel the action of air conditioner for vehicles 1 stops, repeating the control programs such as the operating state decision → control voltage of calculating → various air-conditioning control equipment of the reading of above-mentioned detection signal and operation signal → target blowout temperature TAO and the output of control signal at the control cycle of each regulation.
It should be noted that, repeatedly also carrying out substantially equally when other operate of such control program.
In heat pump circulating system 10 when common warming operation, the high pressure refrigerant of discharging from compressor 11 flows into indoor condenser 120.Flow into refrigerant in indoor condenser 120 and to transport from pressure fan 32 and the indoor wind pushing air of car that have passed indoor evaporator 20 carries out heat exchange and carrys out heat release.Thus, the indoor wind pushing air of car is heated.
Because open and close valve 15a closes, therefore, the high pressure refrigerant that condenser 120 flows out indoor flows into heating fixed restriction part 130 and is depressurized expansion.Then, the low pressure refrigerant inflow outdoor heat exchanger 160 after expansion is depressurized via heating fixed restriction part 130.The low pressure refrigerant flow in outdoor heat converter 160 is evaporated from the extraneous gas heat absorption transported by Air Blast fan 17.
Now, in cooling water circulation loop 40, walk around the chilled(cooling) water return (CWR) of radiator 43 and flowing owing to switching to cooling water, therefore cooling water can not occur to the situation of refrigerant heat release of circulation in outdoor heat converter 160, cooling water from the situation of the refrigerant heat absorption of circulation outdoor heat converter 160.In other words, cooling water can not produce heat affecting to the refrigerant of circulation in outdoor heat converter 160.
Because triple valve 15b switches to the refrigerant flow be connected with the entrance side of reservoir 18 by the outlet side of outdoor heat converter 160, the refrigerant that therefore heat exchanger 160 flows out outdoor flows into reservoir 18 and by gas-liquid separation.Then, the gas phase refrigerant be separated via reservoir 18 is sucked by compressor 11 and is re-compressed.
As mentioned above, when common warming operation, the heat utilizing the refrigerant of discharging from compressor 11 to have in indoor condenser 120 heats the indoor wind pushing air of car, thus can enter the heating of running indoor.
(b) defrosting running
Next, defrosting running is described.At this, carry out heat exchange making refrigerant and extraneous gas as the heat pump circulating system 10 of present embodiment, in outdoor heat converter 160 and make in the refrigerating circulatory device of refrigerant evaporation, when the evaporator refrigerant temperature in outdoor heat converter 160 become frosting temperature (specifically 0 DEG C) below time, frosting may be produced on outdoor heat converter 160.
When producing such frosting, the extraneous gas path 70a of heat exchanger 70 can be inaccessible by frost, therefore causes the heat-exchange capacity of outdoor heat converter 160 obviously to reduce.Therefore, in the heat pump circulating system 10 of present embodiment, when warming operation, when being judged as that outdoor heat converter 160 creates frosting by frosting decision mechanism, perform defrosting running.
In this defrosting running, air conditioning control device makes the action of compressor 11 stop, and the action of Air Blast fan 17 is stopped.Therefore, when defrosting running, for during common warming operation, the cold medium flux of inflow outdoor heat exchanger 160 reduces, and the air quantity flowing into the extraneous gas of extraneous gas path 70a reduces.
Further, the triple valve 42 of cooling water circulation loop 40 is switched to the chilled(cooling) water return (CWR) making cooling water inflow radiator 43 as shown in the dotted arrow of Figure 12 by air conditioning control device.Thus, refrigerant does not circulate in heat pump circulating system 10, and cooling water circulation loop 40 switches to the chilled(cooling) water return (CWR) that refrigerant flows as shown in the dotted arrow of Figure 12.
Therefore, the heat that the cooling water circulated in the cooling water pipe 43a of radiator 43 has conducts to outdoor heat converter 160 via outside fin 70b, thus carries out the defrosting of outdoor heat converter 160.In other words, the defrosting of the used heat efficiently utilizing traveling electro-motor MG can be realized.
(c) cooling operation
When under the state that the step switch at guidance panel connects (ON), during by selector switch selection cooling operation pattern, cooling operation starts.When this cooling operation, open and close valve 15a opens by air conditioning control device, and triple valve 15b is switched to the refrigerant flow be connected with the entrance side of cooling fixed restriction part 19 by the outlet side of outdoor heat converter 160.Thus, heat pump circulating system 10 switches to the refrigerant flow that refrigerant flows as shown in the solid arrow of Figure 13.
Now, about the triple valve 42 of cooling water circulation loop 40, when cooling water temperature Tw becomes more than fiducial temperature, switch to the chilled(cooling) water return (CWR) that cooling water is flowed into radiator 43, when cooling water temperature Tw is less than predetermined fiducial temperature, switch to the chilled(cooling) water return (CWR) that cooling water walks around radiator 43 flowing.It should be noted that, in fig. 13, the flowing of cooling water when representing that cooling water temperature Tw becomes more than fiducial temperature with dotted arrow.
In heat pump circulating system 10 when cooling operation, the high pressure refrigerant of discharging from compressor 11 flows into indoor condenser 120, carries out heat exchange and carrys out heat release with transporting from pressure fan 32 by the indoor wind pushing air of car after indoor evaporator 20.Because open and close valve 15a opens, the high pressure refrigerant that therefore condenser 120 flows out indoor is walked around via fixed restriction and is flowed into outdoor heat converter 160 with path 140.Flow into the low pressure refrigerant of outdoor heat converter 160 to the further heat release of the extraneous gas transported by Air Blast fan 17.
Because triple valve 15b switches to the refrigerant flow be connected with the entrance side of cooling fixed restriction part 19 by the outlet side of outdoor heat converter 160, the refrigerant that therefore heat exchanger 160 flows out outdoor is depressurized expansion via cooling fixed restriction part 19.The refrigerant flowed out from cooling fixed restriction part 19 flows into indoor evaporator 20, evaporates from the indoor wind pushing air heat absorption of the car transported by pressure fan 32.Thus, the indoor wind pushing air of car is cooled.
The refrigerant that evaporimeter 20 flows out indoor flows into reservoir 18 and by gas-liquid separation.Further, in reservoir 18, isolated gas phase refrigerant is sucked by compressor 11 and is re-compressed.As mentioned above, when cooling operation, low pressure refrigerant is evaporated from the indoor wind pushing air heat absorption of car in indoor evaporator 20, and the indoor wind pushing air of car is cooled and can enters the refrigeration of running indoor thus.
In the air conditioner for vehicles 1 of present embodiment, as mentioned above, by switching the refrigerant flow of heat pump circulating system 10 and the chilled(cooling) water return (CWR) of cooling water circulation loop 40, various running can be performed.Further, in the present embodiment, owing to adopting the heat exchanger 70 with above-mentioned feature, therefore, it is possible to suitably adjust the heat exchange amount between refrigerant, cooling water, these three kinds of fluids of extraneous gas.
Certainly, in the heat pump circulating system 10 of present embodiment, also can use the heat exchanger 70 described in the second ~ four embodiment.
(the 6th embodiment)
Next, based on Figure 14 ~ Figure 16, the 6th embodiment of the present invention is described.In this 6th embodiment, the example changing the structure of heat pump circulating system 10 and cooling water circulation loop 40 relative to the 5th embodiment is described.It should be noted that, in Figure 14 ~ Figure 16, the flowing of the refrigerant in heat pump circulating system 10 indicated by the solid line, represents the flowing of the cooling water in cooling water circulation loop 40 with dotted arrow.
Specifically, the cooling water circulation loop 40 of present embodiment makes the cooling water as cooling medium (thermal medium) circulate in the cooling water path of inside being formed at the engine EG as one of the mobile unit generated heat adjoint during action thus carry out the cooling water circulation loop of cooled engine EG.That is, in the present embodiment, abolish the traveling electro-motor MG of the 5th embodiment, replace configuration engine EG.
Further, in the present embodiment, abolish the indoor condenser 120 of the 5th embodiment, in the housing 31 of room conditioning unit 30, configure the compound heat exchanger 70 of the 5th embodiment.Further, the outdoor heat converter 160 of the 5th embodiment in this heat exchanger 70 is made to play function as indoor condenser 120.
In addition, the recuperation of heat heat exchange department 45 making the radiator 43 of the 5th embodiment in heat exchanger 70 add hot cooling water as the heat utilizing refrigerant to have plays function.Thus, in the heat pump circulating system 10 of present embodiment, can also perform and utilize the heat of refrigerant add hot cooling water and carry out the warm-operation of the warming-up of engine.Recuperation of heat heat exchange department 45 is configured in the bypass 44 in cooling water circulation loop 40.
On the other hand, outdoor heat converter 160 is configured to make the single heat exchanger carrying out heat exchange at refrigerant and the extraneous gas transported from Air Blast fan 17 of internal circulation.Similarly, radiator 43 is configured to make the single heat exchanger carrying out heat exchange at cooling water and the extraneous gas transported from Air Blast fan 46 of internal circulation.
Other structures are identical with the 5th embodiment.In addition, in the present embodiment, although replace defrosting running and perform warm-operation, other action is identical with the 5th embodiment.
Below, warm-operation is described.At this, in order to suppress, engine EG's is overheated, the temperature of cooling water is maintained at below set upper limit temperature, and increases the friction loss caused in order to the viscosity of the lubrication oil reducing the inside enclosed in engine EG, and the temperature of preferred cooling water maintains more than the lower limit temperature of regulation.
Therefore, in the heat pump circulating system 10 of present embodiment, when warming operation, perform warm-operation when cooling water temperature Tw becomes below predetermined fiducial temperature.In this warm-operation, make the triple valve 15b of heat pump circulating system 10 when common warming operation in the same manner as action, the triple valve 42 of cooling water circulation loop 40 is switched to make cooling water as shown in the dotted arrow of Figure 15, to walk around radiator 43, namely to the chilled(cooling) water return (CWR) that recuperation of heat heat exchange department 45 flows into.
Therefore, as shown in the solid arrow of Figure 15, in the same manner as when high pressure-temperature refrigerant and the common warming operation of discharging from compressor 11, flow into indoor condenser 120.Because triple valve 42 switches to the chilled(cooling) water return (CWR) making cooling water flow into recuperation of heat heat exchange department 45, therefore, flow into heat that the HTHP refrigerant in indoor condenser 120 has to the wind pushing air heat conduction transported by pressure fan 32, and via outside fin 70b to cooling water heat conduction.Other action is identical with during common warming operation.
As mentioned above, when warm-operation, the heat utilizing the refrigerant of discharging from compressor 11 to have in indoor condenser 120 heats the indoor wind pushing air of car, thus can enter the heating of running indoor.Further, in indoor condenser 120, the heat that has of refrigerant of discharging from compressor 11 is via outside fin 70b also to cooling water heat conduction, and therefore the temperature of cooling water rises.Thus, the heat utilizing refrigerant to have can realize the warming-up of engine EG.
Certainly, in the heat pump circulating system 10 of present embodiment, also can use the heat exchanger 70 described in the second ~ four embodiment.
The present invention is not limited to above-mentioned embodiment, can carry out various distortion as described below without departing from the spirit and scope of the invention.
(1) in the above-described embodiment, describe in heat exchanger 70, the first core 701 be made up of refrigerant pipe 12a is configured at than the example of the second core 702 be made up of refrigerant pipe 12a and these both sides of cooling water pipe 43a by refrigerant flow downstream side, but multiple first core also can be set.
Such as, as shown in figure 17, also than the second core 702, the first core 703 be made up of refrigerant pipe 12a can be set by refrigerant flowing upstream side (specifically, the passage of the side, most upstream of refrigerant flowing).
(2) in the above-described embodiment, describe in the second core 702 of upstream side heat exchange department 71, by the example that refrigerant alternately configures one by one with pipe 12a and cooling water pipe 43a, but the configuration of refrigerant pipe 12a and cooling water pipe 43a is not limited to this.
Such as, in the second core 702 of upstream side heat exchange department 71, also can configure cooling water pipe 43a across two refrigerant pipe 12a.That is, in upstream side heat exchange department 71, also two refrigerant pipe 12a can be configured with between adjacent cooling water pipe 43a.
(3) in the first above-mentioned embodiment, describe and adopt the refrigerant of heat pump circulating system 10 as first fluid, adopt the cooling water of cooling water circulation loop 40 as second fluid and adopt the extraneous gas that transported by Air Blast fan 17 as the example of the 3rd fluid, but the first ~ three fluid is not limited to this.Such as, also can, as the 6th embodiment, adopt the indoor wind pushing air of car as the 3rd fluid.In addition, the 3rd fluid also can be cooling water.
Such as, first fluid can be the high-pressure side refrigerant of heat pump circulating system 10, also can be low-pressure side refrigerant.
Such as, second fluid also can adopt the electrical equipments etc. such as the inverter of subtend engine, traveling electro-motor MG supply electric power to carry out the cooling water cooled.In addition, as second fluid, also can adopt the oil of cooling, and make the second heat exchange department play function as oil cooler, as second fluid, can also heat-storage agent, agent for storage of coldness etc. be adopted.
And, when the heat pump circulating system 10 applying heat exchanger 70 of the present invention being applied to fixed aircondition, changes in temperature preservation storehouse, vending machine cooling/heating apparatus etc., as second fluid, the cooling water that the engine of the drive source to the compressor as heat pump circulating system 10, electro-motor and other electrical equipments etc. cool also can be adopted.
Further, in the above-described embodiment, describe the example applying heat exchanger 70 of the present invention in heat pump circulating system (cooling cycle system), but the application of heat exchanger of the present invention 70 is not limited thereto.That is, can be widely used in device carrying out heat exchange between three kinds of fluids etc.
Such as, can as the heat exchanger being applied to vehicle cooling system.And, first fluid can for the thermal medium of heat had with the first mobile unit of heating when being absorbed in action, second fluid can for the thermal medium of heat had with the second mobile unit of heating when being absorbed in action, and the 3rd fluid can be outdoor air.
More particularly, when being applied to motor vehicle driven by mixed power, the first mobile unit can be made to be engine EG, making first fluid be the cooling water of engine EG, make the second mobile unit be traveling electro-motor, make second fluid be the cooling water of traveling electro-motor.
The caloric value of these mobile units changes separately according to the transport condition (travel load) of vehicle, and therefore the temperature of the temperature of the cooling water of engine EG and the cooling water of traveling electro-motor also changes according to the transport condition of vehicle.Therefore, according to this example, the heat produced in the mobile unit that caloric value is large can be made not only to air heat release, be also sidelong heat to the mobile unit that caloric value is little.
In addition, as the first mobile unit or the second mobile unit, exhaust gas recirculation device (EGR), booster, power steering gear, battery etc. can also be adopted.In addition, heat exchange department also can be made to play function as the oil cooler etc. of cooler for recycled exhaust gas, intercooler, power steering fluid cooling.
(4) in the above-described embodiment, describe the example of the loop switch mechanism in the cooling medium loop adopting the triple valve 42 of electric as switching cooling water circulation loop 40, but loop switch mechanism is not limited to this.Such as, also thermostatic valve can be adopted.Thermostatic valve is the coolant temperature servo valve that the mechanical mechanism making spool displacement carry out opening and closing cooling medium path by the hot wax (temperature sensitive member) utilizing volume along with variations in temperature is formed.Therefore, by adopting thermostatic valve, cooling-water temperature sensor 52 can also be abolished.
(5) in the above-described embodiment, describe the example adopting common freon system refrigerant as refrigerant, but the kind of refrigerant is not limited to this.Also natural refrigerant, the hydrocarbon system refrigerants etc. such as carbon dioxide can be adopted.Further, heat pump circulating system 10 also can form compressor 11 and discharges the supercritical refrigeration cycle system that refrigerant becomes more than the critical pressure of refrigerant.
(6) in the 5th above-mentioned embodiment, describe by making high pressure refrigerant and wind pushing air carry out the example that wind pushing air is heated in heat exchange in indoor condenser 120, but also can replace indoor condenser 120 and setting example as the thermal medium closed circuit making thermal medium circulate, and in this thermal medium closed circuit configuration make high pressure refrigerant and thermal medium carry out the cool water media heat exchanger of heat exchange and make to be carried out heat exchange to heat the heat-up heat exchanger etc. of wind pushing air by warmed-up thermal medium and wind pushing air in water one refrigerant heat exchanger.
In other words, also using high pressure refrigerant as thermal source, indirectly wind pushing air can be heated via thermal medium.Further, when being applied to the vehicle with internal combustion engine, also can, using the cooling water of internal combustion engine as thermal medium, it be made to circulate in thermal medium closed circuit.In addition, in electric motor vehicle, also can, using the cooling water that cools battery, electrical equipment as thermal medium, it be made to circulate in thermal medium closed circuit.
(7) in the above-described 2nd embodiment, describe when to be provided with cooling water pipe 43a in the first core 701, be configured at the outside fin 70b between most downstream side refrigerant pipe 121a and cooling water pipe 43a and be provided with the example of the first slit pore 70c as insulation part and the second slit pore 70d, but be not limited thereto, also can not insulation part be set.
When not arranging insulation part, the outside fin 70b of the first core 701 has the thermally coupled portion 72b of cooling water side, but the number due to cooling water side thermally coupled portion 72b is less than the number of the thermally coupled portion 71b of medium side, therefore, in the outside fin 70b being configured at the first core 701, the heat had for making discharge refrigerant externally gas release region than for cooling water is had heat externally gas release region large.Therefore, it is possible to the heat that the refrigerant circulated in most downstream side refrigerant pipe 121a is had externally gas releasing fully.
(8) in the above-described 2nd embodiment, describe the example adopting slit pore 70c, 70d as insulation part, but insulation part is not limited thereto.Such as, also can replace slit pore 70c, 70d and form vent window, also can cut off outside fin 70b.
In addition, most downstream side refrigerant pipe 121a also can form downstream heat exchange department 72, and forming the refrigerant pipe 12a of upstream side heat exchange department 71 and cooling water pipe 43a also can alternately laminated configuration mutually.
Claims (12)
1. a heat exchanger, it possesses:
Inner multiple first pipes (12a) for first fluid circulation;
Inner multiple second pipes (43a) for second fluid circulation;
By described multiple first pipe (12a) and described multiple second pipe (43a) laminated configuration and the heat making described first fluid and described second fluid the have heat exchange department of releasing to the 3rd fluid;
The surrounding being located at described multiple first pipe (12a) and described multiple second pipe (43a), the 3rd fluid path (70a) circulated for described 3rd fluid; And
Be configured at described 3rd fluid path (70a), promote the outside fin (70b) of the heat exchange of the heat exchange of described first fluid and described 3rd fluid and described second fluid and described 3rd fluid,
Described outside fin (70b) have by described multiple first pipe (12a) each other hot linked first thermally coupled portion (71b) and will described multiple first manage (12a) and described multiple second manage (43a) hot linked second thermally coupled portion (72b)
Described multiple first pipe (12a) is divided into multiple groups,
Described multiple groups of described multiple first pipe (12a) is the passage that the described first fluid distributed from the same space is flowed to same direction respectively,
Described multiple first pipe (12a) has and forms the passage of most downstream side on described first fluid flow direction and the most downstream side first of final passage is managed (121a),
Described heat exchange department has the first core (701), and this first core (701) comprises described most downstream side first and manages (121a),
In described first core (701), the number in described first thermally coupled portion (71b) is more than the number in described second thermally coupled portion (72b).
2. heat exchanger according to claim 1, is characterized in that,
Described first core (701) manages (121a) by described most downstream side first and described at least one, multiple second pipe is formed,
In described first core (701), the position corresponding with described second thermally coupled portion (72b) of described outside fin (70b) is provided with insulation part (70c, 70d), and this insulation part (70c, 70d) suppresses the described first fluid of circulation in described most downstream side first manages (121a) and moves in the described multiple second heat of managing between (43a) middle described second fluid circulated.
3. heat exchanger according to claim 2, is characterized in that,
Described insulation part comprises the slit pore (70c, 70d) of the table back of the body of through described outside fin (70b).
4. heat exchanger according to any one of claim 1 to 3, is characterized in that,
Described first fluid is the refrigerant of the cooling cycle system of steam compression type,
Described heat exchange department makes described refrigerant condensation.
5. heat exchanger according to any one of claim 1 to 4, is characterized in that,
Described multiple first pipe (12a) has side first in front of most downstream and manages (122a), and in front of this most downstream, side first is managed (122a) and is formed near the passage before described final passage on first fluid flow direction,
The flow direction that described first fluid of circulation in (122a) is managed in side first in front of described most downstream with described most downstream in front of side first manage described multiple second of (122a) adjacent configuration to manage the flow direction of (43a) middle described second fluid circulated identical.
6. heat exchanger according to any one of claim 1 to 5, is characterized in that,
(43a) mutual alternately laminated configuration managed by described multiple first pipes (12a) and described multiple second not forming described final passage.
7. heat exchanger according to any one of claim 1 to 6, is characterized in that,
Described heat exchange department has upstream side heat exchange department (71) and is configured in the downstream heat exchange department (72) in flow direction downstream of described 3rd fluid of described upstream side heat exchange department (71),
Described most downstream side first is managed (121a) and is formed described downstream heat exchange department (72),
(43a) mutual alternately laminated configuration managed by described first pipe (12a) and described second forming described upstream side heat exchange department (71).
8. heat exchanger according to any one of claim 1 to 6, is characterized in that,
Described heat exchange department also has the second core (702), this second core (702) comprise described most downstream side first manage beyond (121a) described multiple first pipe (12a) and described multiple second manage,
In described second core (702), (43a) alternately laminated configuration managed by described multiple first pipe (12a) and described multiple second.
9. heat exchanger according to any one of claim 1 to 8, is characterized in that,
Manage (121a) and described multiple second in described most downstream side first and manage the illusory pipe (77) being configured with at least described first fluid and described second fluid between (43a) and not circulating.
10. heat exchanger according to any one of claim 1 to 9, is characterized in that,
Described multiple first pipe (12a) has side first in front of most downstream and manages (122a), and in front of this most downstream, side first is managed (122a) and is formed near the passage before described final passage on first fluid flow direction,
The stream total sectional area that the described most downstream side first forming described final passage manages (121a) is less than side first in front of described most downstream and manages the stream total sectional area of (122a).
11. heat exchangers according to any one of claim 1 to 10, is characterized in that,
Described heat exchange department has upstream side heat exchange department (71) and is configured in the downstream heat exchange department (72) in downstream of the described upstream side heat exchange department (71) on the flow direction of described 3rd fluid,
The described most downstream side first that described upstream side heat exchange department (71) comprises described first core (701) manages the part of (121a),
The described most downstream side first that described downstream heat exchange department (72) comprises described first core (701) manages the part of (121a),
Manage from the described most downstream side first forming described downstream heat exchange department (72) described first fluid that (121a) flow out to manage (121a) to the described most downstream side first forming described upstream side heat exchange department (71) and flow into.
12. heat exchangers according to any one of claim 1,4 to 11, is characterized in that,
The number in described second thermally coupled portion (72b) is 0,
Described core (701) is only managed (121a) by described most downstream side first and is formed.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012249441A JP5920175B2 (en) | 2012-11-13 | 2012-11-13 | Heat exchanger |
| JP2012-249441 | 2012-11-13 | ||
| PCT/JP2013/005997 WO2014076874A1 (en) | 2012-11-13 | 2013-10-08 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104781627A true CN104781627A (en) | 2015-07-15 |
| CN104781627B CN104781627B (en) | 2018-02-09 |
Family
ID=50730812
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380059310.4A Expired - Fee Related CN104781627B (en) | 2012-11-13 | 2013-10-08 | Heat exchanger |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20150292820A1 (en) |
| JP (1) | JP5920175B2 (en) |
| CN (1) | CN104781627B (en) |
| DE (1) | DE112013005408T5 (en) |
| WO (1) | WO2014076874A1 (en) |
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| JP2012201215A (en) * | 2011-03-25 | 2012-10-22 | Denso Corp | Heat exchange system |
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| CN105524663B (en) * | 2015-12-08 | 2018-06-22 | 廖冲 | The modification stove being used in conjunction with gasification furnace |
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| CN114245860A (en) * | 2019-12-24 | 2022-03-25 | 东芝开利株式会社 | Heat exchanger and refrigeration cycle device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5920175B2 (en) | 2016-05-18 |
| US20150292820A1 (en) | 2015-10-15 |
| WO2014076874A1 (en) | 2014-05-22 |
| CN104781627B (en) | 2018-02-09 |
| JP2014098498A (en) | 2014-05-29 |
| DE112013005408T5 (en) | 2015-07-30 |
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