CN102933924B - Heat pump cycle - Google Patents

Heat pump cycle Download PDF

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Publication number
CN102933924B
CN102933924B CN201180028589.0A CN201180028589A CN102933924B CN 102933924 B CN102933924 B CN 102933924B CN 201180028589 A CN201180028589 A CN 201180028589A CN 102933924 B CN102933924 B CN 102933924B
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China
Prior art keywords
heat
air
cooling fluid
refrigerant
cooling
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Active
Application number
CN201180028589.0A
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Chinese (zh)
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CN102933924A (en
Inventor
加藤吉毅
伊藤诚司
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Denso Corp
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Denso Corp
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Classifications

    • 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
    • B60H1/00357—Air-conditioning arrangements specially adapted for particular vehicles
    • B60H1/00385—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell
    • B60H1/004—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell for vehicles having a combustion engine and electric drive means, e.g. hybrid electric vehicles
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00949—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising additional heating/cooling sources, e.g. second evaporator
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00961—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising means for defrosting outside heat exchangers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

In a heat pump cycle, the same outer fins (50) are connected to refrigerant tubes (16a) of an outdoor heat exchanger (16) which functions as an evaporator which evaporates refrigerant, and to coolant tubes (43a) of a radiator (43) which dissipates the heat of the coolant from a running electric motor (MG) which is an external heat supply. The heat retained by the coolant flowing through the coolant tubes (43a) can transfer heat to the refrigerant tubes (16a) of the outdoor heat exchanger (16) via the outer fins (50). Thus, during defrosting operations, when the coolant is passed through the radiator (43) to defrost the outdoor heat exchanger (16), heat transfer loss is suppressed when heat retained by the coolant is transferred to the outdoor heat exchanger (16), enabling the effective use of heat supplied from the running electric motor (MG) to defrost the outdoor heat exchanger (16).

Description

Heat pump cycle
The application is based on the 2010-132891 Japanese patent application of filing an application on June 10th, 2010 and the 2011-123199 Japanese patent application of filing an application on June 1st, 2011, and the content of described application is incorporated in full at this by reference.
Technical field
The present invention relates to a kind of for performing defrost operation to remove the heat pump cycle be formed in as the frost in the heat exchanger of evaporimeter.More specifically, the present invention relates to a kind of heat pump cycle being applicable to be difficult to the vehicle air conditioning obtaining the thermal source of heating from the drive source for advancing.
Background technology
Traditionally, patent document 1 discloses a kind of Vapor Compression Refrigeration Cycle (heat pump cycle), and described Vapor Compression Refrigeration Cycle performs defrost operation to melt and to remove the frost be formed in the heat exchanger of the evaporimeter being used as vaporized refrigerant.
Disclosed in patent document 1, heat pump cycle is applied to the air regulator of hybrid vehicle.Heat pump cycle is designed to switch between heating operation and defrost operation, heating operation is used for the inside being carried out heated vehicle by heating as the heated air that heat-exchange fluid is blown in compartment, defrost operation is for removing the frost be formed in outdoor heat converter, and described outdoor heat converter is used as evaporimeter in heating operation.
More specifically, in defrost operation, when the frosting of outdoor heat converter is detected, internal combustion engine (engine) for exporting the driving force making vehicle advance is activated, and to be blown in outdoor heat converter from the hot-air that the radiator for distributing from the heat of engine coolant blows thus to defrost to outdoor heat converter.
In brief, heat pump cycle disclosed in patent document 1 is designed to by being used as the used heat of the engine of external heat source to melt frost to remove the frost be formed in outdoor heat converter.
Prior art document
Patent document 1: No. 2008-221997th, Japanese Unexamined Patent Publication
But, as in patent document 1, the structure passing to evaporimeter from engine for the heat cooled agent absorbed by air may be dispersed into by the heat of the air of radiators heat (hot-air) surrounding air, thus causes heat trnasfer to lose.In some cases, the used heat from the engine as external heat source not can be effectively used to defrost to evaporimeter.
As mentioned above, the used heat from engine not can be effectively used to defrost to evaporimeter, thus makes cost perform defrosting for a long time.In addition, during defrost operation, engine must work on, thus the fuel efficiency of vehicle is reduced.When heating operation stops during defrost operation, passenger can not fully feel warm.
Summary of the invention
Considered above-mentioned viewpoint and formed the present invention, the first object of the present invention is to provide a kind of heat pump cycle that effectively can use the heat supplied from external heat source during defrost operation.
Further, second object of embodiments of the invention is to provide a kind of heat pump cycle being applied to vehicle air conditioning, described heat pump cycle can obtain effective use of the heat from external heat source supply, and during defrost operation, prevent the insufficient heat supply to passenger.
In order to realize above object, according to the first embodiment of the present invention, a kind of heat pump cycle, comprising: the compressor of compression and refrigerant emission; User side heat exchanger, described user side heat exchanger is at heat-shift between the cold-producing medium and heat-exchange fluid of compressor discharge; Decompressor, described decompressor reduces pressure to the flow of refrigerant flowed out from user side heat exchanger; And outdoor heat converter, described outdoor heat converter makes to be depressurized the cold-producing medium of device decompression and extraneous air heat-shift to evaporate described cold-producing medium.Heat pump cycle is suitable for when outdoor heat converter is by the defrost operation performed during frosting for defrosting to outdoor heat converter.Heat pump cycle also comprises heat dissipation heat exchanger and cooling fluid circuit switching device shifter.Heat dissipation heat exchanger is arranged on for being used in the cooling fluid closed circuit of cooling fluid circulation of cooling external heat source, and is suitable for heat-shift between cooling fluid and extraneous air.Cooling fluid circuit switching device shifter be formed at for allow cooling fluid flow into cooling fluid circuit in heat dissipation heat exchanger and for allow cooling fluid to walk around heat dissipation heat exchanger cooling fluid circuit between switch.In heat pump cycle, outdoor heat converter comprises refrigerant pipe, the cold-producing medium being depressurized device decompression flows in described refrigerant pipe, formed for making the heat-absorption air passage coiling refrigerant tube of flow of external air, heat dissipation heat exchanger comprises cooling fluid pipe, cooling fluid flows in described cooling fluid pipe, formed around cooling fluid pipe for making the heat radiation air duct of flow of external air, heat-absorption air passage and heat radiation air duct are provided with outer fin, described outer fin can realize the heat trnasfer between refrigerant pipe and cooling fluid pipe, promote the heat exchange in outdoor heat converter and heat dissipation heat exchanger simultaneously, and cooling fluid circuit switching device shifter at least performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit in heat dissipation heat exchanger in defrost operation.
Because cooling fluid circuit switching device shifter performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit in heat dissipation heat exchanger during defrost operation, therefore flow through heat contained in the cooling fluid of cooling fluid pipe and can be delivered to outdoor heat converter to defrost to outdoor heat converter.
Now, outer fin is arranged in heat-absorption air passage and another heat radiation air duct can carry out heat trnasfer between a refrigerant pipe and another cooling fluid pipe.Via outer fin, the heat of cooling fluid can be delivered to outdoor heat converter.
Compared with the structure being delivered to the correlation technique of outdoor heat converter via air with heat contained in wherein cooling fluid, the loss in heat trnasfer can be suppressed, therefore can effectively for defrosting to outdoor heat converter from the heat of external heat source supply during defrost operation.Further, the time decreased needed for defrost operation can also be made.
According to the second example of the present invention, the heat pump cycle of above first example also comprises: indoor evaporator, and described indoor evaporator is for allowing the cold-producing medium in the downstream of outdoor heat converter and heat-exchange fluid heat-shift and vaporized refrigerant; And refrigerant flowpath switching device shifter, described refrigerant flowpath switching device shifter is configured to switch the refrigerant flowpath in heating operation and the refrigerant flowpath in cooling down operation, in refrigerant flowpath in heating operation, user side heat exchanger is flow into heat hot replacement fluids from the cold-producing medium of compressor discharge, in the refrigerant flowpath of cooling down operation, flow into indoor evaporator with heat of cooling replacement fluids at the cold-producing medium of outdoor heat converter place distribute heat.In addition, the flow direction flowing through the cold-producing medium of refrigerant pipe in heating operation is identical with the flow direction of the cold-producing medium flowing through refrigerant pipe in cooling down operation.
This layout of heat pump cycle can pass through user side heat exchanger heats heat-exchange fluid.In addition, heat pump cycle also comprises indoor heat converter, therefore can also utilize indoor heat converter heat of cooling replacement fluids.
During heating operation, the flow direction flowing through the cold-producing medium of refrigerant pipe is identical with the flow direction of the cold-producing medium flowing through refrigerant pipe during cooling down operation.From the flow direction of extraneous air, the position relationship between the heat exchange area of the heat exchange area of the refrigerant inlet side of outdoor heat converter and the refrigerant outlet side of outdoor heat converter does not change between heating operation and cooling down operation.
Therefore, outdoor heat converter and heat dissipation heat exchanger are macroscopically considered to a heat exchanger.In the cooling down operation for being distributed by outdoor heat converter from the heat of cold-producing medium, the flow direction of the heat exchange area of the refrigerant inlet side of the outdoor heat converter flowed at a relatively high temperature for making the cold-producing medium with the degree of superheat externally air overlaps the heat exchange area of the cooling fluid inlet side of the heat dissipation heat exchanger for making cooling fluid flow at a relatively high temperature.Further, the flow direction of the externally air of the heat exchange area for the refrigerant outlet side of the outdoor heat converter that makes the cold-producing medium with the degree of superheat flow at relatively low temperature overlaps the heat exchange area of the cooling fluid outlet side of the heat dissipation heat exchanger for making cooling fluid flow at relatively low temperature.By this layout, the flowing of the flowing and cooling fluid that flow through the cold-producing medium of two heat exchangers can be formed to be parallel.
Further, by this layout, for by the heating operation of outdoor heat converter vaporized refrigerant, the heat exchange area of the refrigerant inlet side of the outdoor heat converter that cold-producing medium passes through in relatively lower temp current downflow can the flow direction of externally air overlap in the heat exchange area of cooling fluid inlet side of the heat dissipation heat exchanger that cooling fluid flows through at a relatively high temperature.Therefore, the frosting produced in the heat exchange area of the refrigerant inlet side of the heat pump cycle of the present embodiment outdoor heat converter that can effectively suppress cold-producing medium to flow through at relatively low temperature.
According to the 3rd example of the present invention, the heat pump cycle of the above first or second example is constructed such that: in defrost operation, compared with before being transformed into defrost operation, and the inflow flow flowing into the cold-producing medium in outdoor heat converter reduces.
Therefore, in defrost operation, the heat passing to outdoor heat converter via outer fin can be prevented to be inhaled in the cold-producing medium of the refrigerant pipe flowing through outdoor heat converter.Therefore, may be used for more effectively defrosting to outdoor heat converter from the heat of external heat source supply during defrost operation.
In addition, as in the 4th example of the present invention, decompressor can be variable restriction mechanism, in described variable restriction mechanism, throttling opening degree is variable, and compared with before being transformed into defrost operation, decompressor can increase throttling opening degree in defrost operation.Therefore, in defrost operation, easily can flow into outdoor heat converter from the high temperature refrigerant of compressor discharge, thus accelerate the defrosting to outdoor heat converter
In addition, as in the 5th example of the present invention, heat pump cycle can also comprise outflow flow control valve, the outflow flow of the cold-producing medium that described outflow flow control valve is configured to regulate heat exchanger outdoor to flow out, and compared with before being transformed into defrost operation, flow out the outflow flow that flow control valve can reduce cold-producing medium in defrost operation.
In addition, as in the 6th example of the present invention, flow out flow control valve can be configured to the cold-producing medium for outdoor heat converter go out interruption-forming one.Therefore, the coolant channel volume from the discharge port side of compressor to the entrance side of outflow flow control valve can be reduced, thus the refrigerant flow that reduction flow in outdoor heat converter.
According to the 7th example of the present invention, the heat pump cycle of any one in first to the 6th example also comprises outdoor blowers, described outdoor blowers blows extraneous air towards outdoor heat converter and heat dissipation heat exchanger, and compared with before stopping compressor, when the compressor is stopped, outdoor blowers increases blowability.
When the compressor is stopped, the ability that blows of outdoor blowers can be increased thus promptly the temperature of outdoor heat converter is increased to the level identical with extraneous air, thus can reduce defrosting time further.Term " when the compressor is stopped " represents that compressor not only stops during defrost operation, and also stops in the normal operation period.
In the 8th example of the present invention, be configured to: according to the heat pump cycle of any one in the first to the 7th example in defrost operation, compared with before being transformed into defrost operation, the heating efficiency for the user side heat exchanger of heat hot replacement fluids reduces.
Therefore, the heating efficiency for the user side heat exchanger of heat-exchange fluid reduces, make it possible to reduce at outdoor heat converter place from the heat of refrigerant suction with promotes defrost.Concrete grammar for reducing the heating efficiency of the user side heat exchanger for heat-exchange fluid can comprise the flow reducing to flow through the cold-producing medium of circulation and the refrigerant pressure reducing heat exchanger place, user side.
According to the 9th example of the present invention, according in any one heat pump cycle in the first to the 8th example, heat-absorption air passage and heat radiation air duct are constructed such that the volume of the extraneous air flow in heat-absorption air passage and heat radiation air duct reduces in defrost operation.
Therefore, therefore the heat inhalation flow that heat pump cycle can suppress to pass to outdoor heat converter via outer fin during defrost operation by the extraneous air of heat-absorption air passage and heat radiation air duct, and more effectively can use from the heat of external heat source supply to defrost to outdoor heat converter in defrost operation.
Particularly, outdoor blowers can be arranged for extraneous air to blow towards outdoor heat converter and heat dissipation heat exchanger.During defrost operation, the ability that blows of outdoor blowers can be lowered thus reduce the volume of the extraneous air flow in heat-absorption air passage and heat radiation air duct.
Further, shutoff device (passage interruption device) can be arranged for opening and closing the inflow path for allowing extraneous air to flow into heat-absorption air passage and dispel the heat in air duct.During defrost operation, shutoff device can reduce the area of passage of the ingress path of extraneous air, thus reduces the volume of the extraneous air flow in heat-absorption air passage and heat radiation air duct.
Term " reduces the volume of extraneous air " and not only represents the volume reducing air compared with flowing into the existing volume of air, and represent the volume settings of air to be zero (0) (that is, not allowing extraneous air to flow in heat-absorption air passage and heat radiation air duct).
In the tenth example of the present invention, also comprise outdoor blowers according to the heat pump cycle of any one in the of the present invention first to the 9th example, described outdoor blowers blows extraneous air towards outdoor heat converter and heat dissipation heat exchanger.In this case, heat dissipation heat exchanger is positioned at the windward side of the flow direction of the extraneous air blowed by outdoor blowers relative to outdoor heat converter.
Because heat is flowed in outdoor heat converter by the extraneous air that heat dissipation heat exchanger absorbs, therefore the heat of cooling fluid not only can be delivered to outdoor heat converter via outer fin via air.Therefore, at least during defrost operation, can more effectively for defrosting to outdoor heat converter from the heat of external heat source supply.
In the 11 example of the present invention, according in the heat pump cycle of any one in the first to the tenth example, at least one in refrigerant pipe is between cooling fluid pipe, at least one in cooling fluid pipe is between refrigerant pipe, and heat-absorption air passage is formed as an air duct with at least one in heat radiation air duct.
Therefore, compare with the situation of outdoor heat converter relative to the flow direction arranged in series of extraneous air with heat dissipation heat exchanger, cooling fluid pipe and refrigerant pipe can be arranged to close to each other.In other words, cooling fluid pipe can be oriented to the frost near being formed in refrigerant pipe.Therefore, during defrost operation, can be delivered effectively to outdoor heat converter from the heat of external heat source supply to perform defrost operation.
According to the 12 example of the present invention, in first to the 11 example, the heat pump cycle of any one can be applied to vehicle air conditioning, and can comprise: Inside Air Temperature test section, described Inside Air Temperature test section is configured to the Inside Air Temperature detecting vehicle interior; With frosting determination portion, described frosting determination portion is configured to the frosting determining outdoor heat converter.In this case, heat-exchange fluid is the air being blown into vehicle interior, external heat source is the car-mounted device producing heat in operation, cooling fluid is the cooling agent for cooling car-mounted device, and when being determined by frosting determination portion that frost is formed in outdoor heat converter place and the Inside Air Temperature of vehicle interior is equal to or greater than predetermined reference Inside Air Temperature, cooling fluid circuit switching device shifter performs the switching be switched to for making cooling fluid flow into the cooling fluid circuit in heat dissipation heat exchanger.
By this layout, by frosting determination portion determination frosting, and when the temperature of the inner air in compartment is equal to or greater than predetermined reference Inside Air Temperature, frosting operation starts.After the Inside Air Temperature of vehicle interior is warmed up to a certain degree, defrost operation can be started.Therefore, during defrost operation, even if using in the device for reducing the heating efficiency of the air in the heat exchanger of user side, heat pump cycle also can prevent passenger from feeling dissatisfied to heating.
According to the 13 example of the present invention, in the first to the 12 example, the heat pump cycle of any one can be applied to vehicle air conditioning.In this case, heat pump cycle comprises the frosting determination portion of the frosting for determining outdoor heat converter further.In addition, heat-exchange fluid is the air being blown into vehicle interior, external heat source is the car-mounted device producing heat in operation, cooling fluid is the cooling agent for cooling car-mounted device, user side heat exchanger is arranged in the housing, form air duct in described housing, and the inner air in housing will be introduced in arrange in the housing with the inner/outer air switching device shifter of the introducing ratio of extraneous air for changing.In addition, when determining that frost is formed in outdoor heat converter place by frosting determination portion, cooling fluid circuit switching device shifter performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit of heat dissipation heat exchanger, and when determining that frost is formed in outdoor heat converter place by frosting determination portion, compared with before being transformed into defrost operation, inner/outer air switching device shifter increases the introducing ratio of inner air and extraneous air.
Therefore, even if use in the situation of the device of the heating efficiency for reducing the air in the heat exchanger of user side during defrost operation, there is the introducing of the volume of the inner air of high temperature and the volume of extraneous air than increasing, thus can prevent passenger from feeling dissatisfied to heating.
According to the 14 example of the present invention, in the first to the 13 example, the heat pump cycle of any one is applied to vehicle air conditioning, and heat pump cycle also comprises the frosting determination portion of the frosting being configured to determine outdoor heat converter.In this case, heat-exchange fluid is the air being blown into vehicle interior, external heat source is the car-mounted device producing heat in operation, cooling fluid is the cooling agent for cooling car-mounted device, user side heat exchanger is arranged in the housing, air duct is formed in described housing, for arranging in the housing by changing the air outlet slit mode-changeover device being used for being carried out between air outlet slit pattern to the opening/closing state of the air outlet slit of vehicle interior by blow air switching, at least for blow air is set to described air outlet slit to foot's air outlet slit of the foot of passenger, when determining that frost is formed in outdoor heat converter place by frosting determination portion, cooling fluid circuit switching device shifter performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit in heat dissipation heat exchanger, and when determining that frost is formed in outdoor heat converter place by frosting determination portion, air outlet slit mode-changeover device performs the switching be switched to for the air outlet slit pattern from foot's air outlet slit blow air.
Further, even if when using the device for reducing the heating efficiency of user side heat exchanger during defrost operation, perform the switching be switched to for the air outlet slit pattern from foot's air outlet slit blow air.Such as, compared with situation about blowing towards the face of passenger with air, heat pump cycle can prevent passenger to be unsatisfied with adding hotness.
According to the 15 example of the present invention, in the first to the 14 example, the heat pump cycle of any one is applied to vehicle air conditioning, and heat pump cycle also comprises the frosting determination portion of the frosting being configured to determine outdoor heat converter.In this case, heat-exchange fluid is the air being blown into vehicle interior, external heat source is the car-mounted device producing heat in operation, cooling fluid is the cooling agent for cooling car-mounted device, user side heat exchanger is arranged in the housing, air duct is formed in described housing, air blast for being blowed towards vehicle interior by air is arranged in the housing, when determining that frost is formed in outdoor heat converter place by frosting determination portion, cooling fluid circuit switching device shifter performs the switching be switched to for making cooling fluid flow into the cooling fluid circuit in heat dissipation heat exchanger, and compared with before determining frosting, air blast reduces blowability.
In addition, even if when using the device for reducing the heating efficiency of the air in the heat exchanger of user side during defrost operation, air blast reduces it and blows ability, thus passenger can be prevented to be unsatisfied with adding hotness.
According to the 16 example of the present invention, in the first to the 15 example, the heat pump cycle of any one can be applied to vehicle air conditioning, and heat pump cycle can comprise the frosting determination portion of the frosting for determining outdoor heat converter.In this case, heat-exchange fluid is the air being blown into vehicle interior, external heat source is the car-mounted device producing heat in operation, cooling fluid is for cooling the cooling agent of car-mounted device, when being equal to or less than predetermined reference speed when the speed of a motor vehicle and being equal to or less than 0 DEG C when the temperature of the cold-producing medium of the outlet side of outdoor heat converter, frosting determination portion can determine that frost is formed in outdoor heat converter place, and when determining that frost is formed in outdoor heat converter place by frosting determination portion, cooling fluid circuit switching device shifter performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit in heat dissipation heat exchanger.
Particularly, when frost is formed in outdoor heat converter place, the heat be included in car-mounted device can effectively for defrosting to outdoor heat converter.Further, when the speed of vehicle is equal to or less than predetermined reference car speed and the temperature of the cold-producing medium of the outlet side of outdoor heat converter is equal to or less than 0 DEG C, frosting determination portion determines that frost is formed in outdoor heat converter place.Like this, consider that car speed performs suitably determining of frosting.
According to the 17 example of the present invention, in the heat pump cycle of the 16 example, when the speed of traveling vehicle is equal to or less than predetermined reference speed, and when the temperature of the cold-producing medium of the outlet side of outdoor heat converter is equal to or less than 0 DEG C, frosting determination portion can determine that frost is formed in outdoor heat converter place.Term " traveling vehicle " expression speed is not equal to the vehicle of zero, does not namely comprise the vehicle of stopping.
According to the 18 example of the present invention, the heat pump cycle of in example ten two to ten seven also comprises the coolant temperature test section of the temperature being configured to detect the cooling agent flow in car-mounted device.In this case, when the coolant temperature detected by coolant temperature test section is equal to or greater than predetermined reference temperature, cooling fluid circuit switching device shifter performs to be switched to states for making the switching that cooling fluid flows into the cooling fluid circuit in heat dissipation heat exchanger.
Like this, heat contained in cooling agent distributes from heat dissipation heat exchanger, thus car-mounted device can be prevented overheated.The heat distributed from heat dissipation heat exchanger can be delivered to outdoor heat converter, is then inhaled in cold-producing medium.In the normal operating of heat pump cycle, room air can be effectively heated.Therefore, the heating properties of vehicle air conditioner can be improved.
According to the 19 example of the present invention, in the heat pump cycle of in the first to the 18 example, when the execution of cooling fluid circuit switching device shifter is switched to for making cooling fluid walk around the switching of the cooling fluid circuit of heat dissipation heat exchanger, described cooling fluid closed circuit stores the heat be included in external heat source within it.
Therefore, when not needing defrost operation, cooling fluid circuit switching device shifter performs the switching be switched to for allowing chilled fluid flow to walk around the cooling fluid circuit of heat dissipation heat exchanger, thus heat contained in external heat source can be stored in heat pump cycle.Therefore, the heat stored during defrost operation may be used for completing defrosting in the short time.
Such as, according to the 20 example of the present invention, the heat pump cycle of the 19 example is applied to vehicle air conditioning.In this case, heat-exchange fluid can be the air being blown into vehicle interior, external heat source can be the car-mounted device producing heat in operation, cooling fluid can be the cooling agent for cooling car-mounted device, and when the execution of cooling fluid circuit switching device shifter is switched to for allowing cooling fluid to walk around the switching of the cooling fluid circuit of heat dissipation heat exchanger, the heat distributed from car-mounted device can be stored in cooling agent by cooling fluid closed circuit.
According to the 21 example of the present invention, the heat pump cycle of the 19 example is applied to vehicle air conditioning.In this case, heat-exchange fluid can be the air being blown into vehicle interior, external heat source can be the heating element heater for being produced heat by supply electric power, cooling fluid can be the cooling agent for cooling heating element heater, and when the execution of cooling fluid circuit switching device shifter is switched to for allowing cooling fluid to walk around the switching of the cooling fluid circuit of heat dissipation heat exchanger, the heat distributed from heating element heater can be stored in cooling agent by cooling fluid closed circuit.
According to the 22 example of the present invention, the heat pump cycle of the 21 example is applied to vehicle air conditioning.In this case, heat-exchange fluid can be the air being blown into vehicle interior, the car-mounted device of generation heat in operation and the heating element heater for being produced heat by supply electric power can be set up as external heat source, cooling fluid can be the cooling agent for cooling heating element heater and car-mounted device, and when the execution of cooling fluid circuit switching device shifter is switched to for allowing cooling fluid to walk around the switching of the cooling fluid circuit of heat dissipation heat exchanger, cooling fluid closed circuit can be stored in from least one heat distributed in car-mounted device and heating element heater in cooling agent.
In addition, as in the 23 example of the present invention, the heat that heating element heater produces can control according to external air temperature.Therefore, may be limited in heating element heater and consume unnecessary electric power.
According to the 24 example of the present invention, heat pump cycle can also comprise: outdoor unit bypass passageways, and described outdoor unit bypass passageways makes the cold-producing medium being depressurized device decompression walk around outdoor heat converter and cold-producing medium is directed to the refrigerant outlet side of outdoor heat converter; With outdoor unit bypass passageways switching device shifter, described outdoor unit bypass passageways switching device shifter is formed at the refrigerant loop for the cold-producing medium being depressurized device decompression being directed to outdoor heat converter and is used for switching being depressurized between refrigerant loop that cold-producing medium that device reduces pressure guides towards outdoor unit bypass passageways.In this case, in defrost operation, outdoor unit bypass passageways switching device shifter performs the switching be switched to for the cold-producing medium being depressurized device decompression being directed to the refrigerant loop of outdoor unit bypass passageways.
Outdoor unit bypass passageways switching device shifter performs the cold-producing medium be used for being depressurized device decompression and is directed to the switching of the refrigerant loop of outdoor unit bypass passageways in defrost operation, thus the heat passing to outdoor unit heat exchanger via outer fin can be prevented from during defrost operation to be inhaled into flow through in the cold-producing medium of outdoor heat converter.
Therefore, may be used for more effectively defrosting to outdoor heat converter from the heat of external heat source supply during defrost operation.Such as, when being applied to vehicle air conditioning, air can by user side heat exchanger heats to realize the heating to vehicle interior.
According to the 25 example of the present invention, heat pump cycle can also comprise: indoor evaporator, and described indoor evaporator is heat-shift between the cold-producing medium and heat-exchange fluid in the downstream of outdoor heat converter; Evaporator bypass passage, described evaporator bypass passage makes the cold-producing medium in the downstream of outdoor heat converter walk around indoor evaporator and cold-producing medium is directed to the refrigerant outlet of indoor evaporator; With evaporator bypass channel switching device, the described evaporator bypass channel switching device cold-producing medium be formed at for the downstream by outdoor heat converter is directed between the refrigerant loop of indoor evaporator and the refrigerant loop being used for the cold-producing medium in the downstream of outdoor heat converter to be directed to evaporator bypass passage and switches.In defrost operation, evaporator bypass channel switching device performs the switching that the cold-producing medium be switched to for the downstream by outdoor heat converter is directed to the refrigerant loop of indoor evaporator.
Therefore, during defrost operation, the cold-producing medium in the downstream of outdoor heat converter is directed to indoor evaporator side by evaporator bypass channel switching device, makes the indoor evaporator when cold-producing medium is evaporated can by heat absorption effect heat of cooling replacement fluids.Such as, when being applied to vehicle air conditioning, the dehumidifying heating operation that the air that can realize wherein being cooled by indoor evaporator is heated again by user side heat exchanger.
According to the 26 example of the present invention, heat pump cycle can be applied to vehicle air conditioning.In this case, heat-exchange fluid is the air being blown into vehicle interior, user side heat exchanger is arranged in the housing, blast channel is formed in described housing, and auxiliary heater is arranged in described housing, uses and produced adding hot fluid and carrying out the air of heated blown to described vehicle interior by least one generation in the heating element heater of heat of supply electric power as heating source of the car-mounted device heating of heat in operation.
Therefore, even if during defrost operation when the heating efficiency of the user side heat exchanger for air reduces due to the discharge refrigerant ability reduction of compressor, air also can be heated by auxiliary heater.This layout can suppress the reduction of the temperature of the air being blown into vehicle interior, and therefore can prevent passenger from feeling discontented to heating.
Accompanying drawing explanation
Fig. 1 is the overall schematic of display according to the flow of refrigerant in the heating operation of the heat pump cycle of the first embodiment;
Fig. 2 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the first embodiment;
Fig. 3 is that display collects the overall schematic of the flow of refrigerant in operation according to the used heat of the heat pump cycle of the first embodiment;
Fig. 4 is the overall schematic of display according to the flow of refrigerant in the cooling down operation of the heat pump cycle of the first embodiment;
Fig. 5 is the schematic diagram of display according to the detailed construction of the room air regulon of the first embodiment;
Fig. 6 is the overall schematic of display according to the flow of refrigerant in the heating operation of the heat pump cycle of the second embodiment;
Fig. 7 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the 3rd embodiment;
Fig. 8 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the 4th embodiment;
Fig. 9 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the 5th embodiment;
Figure 10 is the perspective view of the heat converter structure according to the 6th embodiment;
Figure 11 is the decomposition diagram of the heat converter structure according to the 6th embodiment;
Figure 12 is the cross-sectional view intercepted along the line A-A in Figure 10;
Figure 13 is for illustration of the exemplary perspective view according to the flowing of cold-producing medium in the heat converter structure of the 6th embodiment and the flowing of cooling agent;
Figure 14 is the flow chart of display according to the control flow of the vehicle interior coordinated signals of the 7th embodiment;
Figure 15 is the flow chart of display according to another control flow of the vehicle interior coordinated signals of the 7th embodiment;
Figure 16 is the flow chart of display according to another control flow of the vehicle interior coordinated signals of the 7th embodiment;
Figure 17 is the flow chart of display according to another control flow of the vehicle interior coordinated signals of the 7th embodiment;
Figure 18 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the 8th embodiment;
Figure 19 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the 9th embodiment;
Figure 20 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the tenth embodiment; And
Figure 21 is the overall schematic of display according to the flow of refrigerant in the defrost operation of the heat pump cycle of the 11 embodiment.
Detailed description of the invention
First embodiment
With reference to Fig. 1-5, below the first embodiment of the present invention is described.In this embodiment of the invention, heat pump cycle 10 is applied to the air regulator 1 of the vehicle of so-called hybrid electric vehicle, and wherein said hybrid electric vehicle can from internal combustion engine (engine) and the driving force of motor MG acquisition for advancing for advancing.Fig. 1 shows the overall structure figure of the vehicle air conditioner 1 of the present embodiment.
Hybrid electric vehicle can switch by between another travel condition of making engine running or stop the travel condition that obtains driving force to advance from engine and the motor MG for advancing and vehicle only to obtain driving force to advance from the motor MG for advancing by making engine stop according to the travel load on vehicle etc. at vehicle.Therefore, with only obtain the general-utility car of the driving force for advancing from engine compared with, hybrid electric vehicle can improve fuel efficiency.
Heat pump cycle 10 in vehicle air conditioner 1 for heat or air in coolant compartment to be blown into as in the vehicle interior in the space for air conditioning.Therefore, heat pump cycle 10 can switch between refrigerant flowpath, thus performs heating operation (heater operation) and cooling down operation (cooler operation).Heating operation is suitable for coming heated vehicle inside by the air as heat-exchange fluid (as normal operating) in vehicle cabin.Cooling down operation is suitable for cooling vehicle interior by the cooling air be blown in compartment.
Then, heat pump cycle 10 can also perform defrost operation and used heat collects operation, defrost operation for melting and remove the frost at outdoor heat converter 16 place being formed at the evaporimeter being used as vaporized refrigerant in heating operation, described used heat collect operation be used for absorbing in the refrigerant in heating operation as external heat source for heat contained in the motor MG that advances.In the overall structure figure of the heat pump cycle 10 shown in Fig. 1-4, the flowing of the cold-producing medium in each operation is represented by filled arrows.
The heat pump cycle 10 of the present embodiment adopts common fluorine-based cold-producing medium as cold-producing medium, and forms subcritical refrigeration cycle, and the high-pressure side refrigerant pressure of described subcritical refrigeration cycle is no more than the critical pressure of cold-producing medium.Refrigerator oil for lubricate compressors 11 is mixed in cold-producing medium, and a part for refrigerator oil cycles through described heat pump cycle together with cold-producing medium.
First, compressor 11 is positioned in engine room, and in heat pump cycle 10 suck, compression and refrigerant emission.Compressor is by utilizing motor 11b to drive the motor compressor with the fixed displacement compressor 11a of fixed discharge ability.Particularly, various types of compressing mechanisms of such as scroll compressor structure or blade compresses mechanism can be adopted to fixed displacement compressor 11a.
Motor 11b is the motor that its operation (revolution) is controlled by the control signal exported from the air conditioning controller with function that will be described subsequently.Motor 11b can use AC motor or DC motor.The discharge refrigerant ability of the control break compressing mechanism 11 of the revolution of motor.Therefore, in the present embodiment, motor 11b is used as the discharge capacity changing section of compressor 11.
The discharge refrigerant port of compressor 11 is connected to the refrigerant inlet side of the indoor condenser 12 as user side heat exchanger.Indoor condenser 12 is arranged in the housing 31 of the room air regulon 30 of vehicle air conditioner 1.Indoor condenser 12 is heat exchangers of heating, and described heat exchanger is flowing through the high-temperature high-pressure refrigerant of described heat exchanger and will to be blown in interior compartment and by heat-shift between the air of indoor evaporator 20 that describes subsequently.The detailed construction of room air regulon 30 is described subsequently.
The fixed restriction device 13 of heating is connected to the refrigerant outlet side of indoor condenser 12.Fixed restriction device 13 is used as the decompressor of heating operation, and described decompressor makes the cold-producing medium that condenser 12 flows indoor reduce pressure and expand in heating operation.The fixed restriction device 13 of heating can use aperture, capillary etc.The outlet side of the fixed restriction device 13 of heating is connected to the refrigerant inlet side of outdoor heat converter 16.
Bypass passageways 14 for fixed restriction device 13 is connected to the refrigerant outlet side of indoor condenser 12.Bypass passageways 14 makes the cold-producing medium that condenser 12 flows indoor walk around the fixed restriction device 13 of heating and be directed in outdoor heat converter 16 by described cold-producing medium.Be arranged in the bypass passageways 14 for fixed restriction device for the open/closed valve 15a opened and closed for the bypass passageways 14 of fixed restriction device.Open/closed valve 15a is magnetic valve, and its opening and closing operation is controlled by the control voltage exported from air conditioning controller with function.
With when cold-producing medium is by compared with the pressure loss that causes during fixed restriction device 13, when cold-producing medium is minimum by the pressure loss caused during open/closed valve 15a.Therefore, when open/closed valve 15a opens, the flow of refrigerant that condenser 12 flows out indoor flow into outdoor heat converter 16 via the bypass passageways 14 for fixed restriction device.On the contrary, when open/closed valve 15a closes, cold-producing medium flow in outdoor heat converter 16 via the fixed restriction device 13 of heating.
Therefore, open/closed valve 15a can switch between multiple refrigerant flowpath of heat pump cycle 10.The open/closed valve 15a of the present embodiment is used as refrigerant flowpath switching device shifter.Alternatively, as this refrigerant flowpath switching device shifter, can provide electric T-shaped valve etc. with the refrigerant loop of the entrance side at the fixed restriction device 13 for the outlet side of indoor condenser 12 being connected to heating be used for connecting indoor condenser 12 outlet side and be used for fixed restriction device bypass passageways 14 entrance side another refrigerant loop between switch.
Outdoor heat converter 16 is flowing through heat-shift between the low pressure refrigerant of this outdoor heat converter 16 and the extraneous air blowed from blower fan 17.Outdoor heat converter 16 is being arranged on the heat exchanger in engine room, and to be used as in heating operation for evaporating low pressure cold-producing medium show the evaporimeter of endothermic effect, and described heat exchanger is also as the radiator distributing heat from high-pressure refrigerant in cooling down operation.
Blower fan 17 is electric blowers, the operating ratio of described electric blower, that is, the revolution (volume of air) of described electric blower, is controlled by the control voltage exported from air conditioning controller with function.The outdoor heat converter 16 of the present embodiment forms one, for heat-shift between the cooling agent for cooling the motor MG for advancing and the extraneous air blowed from blower fan 17 with the radiator 43 that will be described subsequently.
The blower fan 17 of the present embodiment is used as the outdoor blowers blowed towards both outdoor heat converter 16 and radiator 43 by extraneous air.The detailed construction of outdoor heat converter 16 integral with one another and radiator 43 (hereinafter referred to as " heat converter structure 70 ") will be described in detail following.
The outlet side of outdoor heat converter 16 is connected to electric T-shaped valve 15b.The operation of triple valve 15b is controlled by the control voltage exported from air conditioning controller with function.Triple valve 15b is used as refrigerant flowpath switching device shifter together with above-mentioned open/closed valve 15a.
More specifically, in heating operation, triple valve 15b performs the switching of the refrigerant flowpath of the entrance side be switched to for the outlet side of outdoor heat converter 16 being connected to the accumulator 18 that will be described subsequently.On the contrary, in cooling down operation, triple valve 15b performs the switching of the refrigerant flowpath of the entrance side of the fixed restriction device 19 for the outlet side of outdoor heat converter 16 being connected to cooling.
The fixed restriction device 19 of cooling is used as the decompressor of cooler operation (cooling down operation), and described decompressor is used for the cold-producing medium that decompression and the heat exchanger 16 outdoor that expands flow out in cooling down operation.Fixed restriction device 19 has the basic structure identical with the basic structure of the fixed restriction device 13 heated above.The outlet side of the fixed restriction device 19 of cooling is connected to the refrigerant inlet side of indoor evaporator 20.
Indoor evaporator 20 is arranged on the upstream side of air stream in the housing 31 of room air regulon 30 relative to indoor condenser 12.Indoor evaporator 20 is the heat exchangers for cooling, described heat exchanger heat-shift thus cool the air of vehicle interior between vehicle interior air and the cold-producing medium flowing through described heat exchanger.The refrigerant outlet side of indoor evaporator 20 is connected to the entrance side of accumulator 18.
Therefore, the refrigerant flowpath for allowing cold-producing medium to flow to the entrance side of accumulator 18 from triple valve 15b in heating operation is used as the evaporator bypass passage 20a allowing the cold-producing medium in the downstream of outdoor heat converter 16 to walk around indoor evaporator 20.Triple valve 15b is used as evaporator bypass channel switching device, and described evaporator bypass channel switching device is used for being directed between the refrigerant loop of indoor evaporator 20 and another refrigerant loop being used for the cold-producing medium in the downstream of outdoor heat converter 16 to be directed to evaporator bypass passage 20a at the cold-producing medium for the downstream by outdoor heat converter 16 switching.
Accumulator 18 is the gas-liquid separators for low side refrigerant, and the cold-producing medium flow in described gas-liquid separator is separated into liquid and gas by described gas-liquid separator, and stores the excess refrigerant in circulation in described gas-liquid separator.The vapor phase refrigerant outlet of accumulator 18 is connected to the suction side of compressor 11.Therefore, liquid phase refrigerant is drawn in compressor 11 for restriction by accumulator 18, thus prevents the compression of liquid in compressor 11.
Next, Fig. 5 is below used to describe room air regulon 30.Fig. 5 shows the detailed structure view of amplification, and described structure chart represents the room air regulon 30 shown in Fig. 1-4.Room air regulon 30 is arranged in the inside of instrument board (instrument face plate) at the forefront place in compartment.Described unit 30 holds air blast 32, above-mentioned indoor condenser 12 and indoor evaporator 20 in the housing 31 being used as shell.
Housing 31 forms the air duct be communicated with compartment, and air is blown in vehicle interior by described air duct.Housing 31 is formed by the resin (such as, polypropylene) with certain elasticity and excellent strength.Inner/outer air switch 33 for carrying out switching to introduce selected air between the air (inner air) and extraneous air of vehicle interior is arranged on the side, most upstream of vehicle interior air stream in housing 31.
Inner/outer air switch 33 is inner/outer air switching device shifters, described inner/outer air switching device shifter is used for switching by inner/outer air the ratio that aperture area that door regulates the aperture area for inner air being incorporated into the internal air inlet in housing 31 continuously and be used for extraneous air to be incorporated into the outside air inlet in housing 31 introduces to continuously change inner air and extraneous air, thus switches between suction ports pattern.
Inner/outer air switch 33 is provided with for inner air being incorporated into the internal air inlet in housing 31 and being used for the outside air inlet that is incorporated into by extraneous air in housing 31.Inner/outer air switches door and is positioned at the aperture area of the aperture area and outside air inlet that regulate internal air inlet continuously in inner/outer air switch 33, thus changes the ratio of the volume of inner air and the volume of extraneous air.Inner/outer air switches door and is driven by electric actuator (not shown), and the operation of described electric actuator is controlled by the control signal exported from air conditioning controller with function.
The suction ports pattern switched by inner/outer air switch 33 comprises inner air pattern, exterior air patterns and internal-external air mixed mode, described inner air pattern is used for being incorporated into by inner air in housing 31 by opening internal air inlet completely while closing outside air inlet completely, described exterior air patterns is used for closing internal air inlet completely and being incorporated into by extraneous air in housing 31 while opening outside air inlet completely, described internal-external air mixed mode is used for opening internal air inlet and outside air inlet simultaneously.
For the blow air sucked via inner/outer air switch 33 to be arranged on the downstream of the air stream of inner/outer air switch 33 to the air blast 32 in vehicle interior.Air blast 32 is electric blowers, described electric blower comprises the centrifugal multiblade fan (Sirocco fan) driven by motor, and the revolution of described electric blower (volume of air) is controlled by the control voltage exported from air conditioning controller with function.
Indoor evaporator 20 and indoor condenser 12 are set in sequence in the downstream of the air-flow of air blast 32 successively relative to the flowing of the air of vehicle interior.In brief, indoor evaporator 20 is arranged on upstream side relative to indoor condenser 12 along the flow direction of vehicle room air.
The upstream side of the air-flow in the downstream of the air-flow in air mix door 34 evaporimeter disposed in the interior 20 and indoor condenser 12.Air mix door 34 regulates the volume ratio of air in the air by indoor evaporator 20 by indoor condenser 12.The downstream of the air-flow in blending space 35 condenser disposed in the interior 12 with mixing with cold-producing medium heat-shift and at indoor condenser 12 place by the air that heats with walk around indoor condenser 12 and not by the air heated.
For using the adjustment blow air of the mixing in mixing chamber 35 to as the most downstream side open pore in the vehicle interior in cooled space interested being arranged on the air stream in housing 31.Particularly, the open pore inner side comprised for the front glass towards vehicle blows and regulates the defrosting open pore 36a of air, for blowing the facial open pore 36b that regulates air and the foot open pore 36c for the foot regulating air towards passenger being blowed towards the upper body of the passenger in compartment.
The respective downstream side of the air stream of defrosting open pore 36a, facial open pore 36b and foot open pore 36c is via forming the tubes connection of respective air passage to the defrost air outlet be arranged in compartment, facial air outlet slit and foot's air outlet slit.
Air mix door 34 regulates the volume flow of the air through indoor condenser 12, thus regulates the temperature of the adjustment air of mixing in mixing chamber 35, thus controls the temperature of the adjustment air blowed from each air outlet slit.That is, air mix door 34 is used as the temperature-adjusting device of the temperature regulating the adjustment air be blown in vehicle interior.
In brief, air mix door 34 is used as heat exchange amount adjusting device, for regulating the heat exchanged between the air of the vehicle interior the cold-producing medium discharged from compressor 11 and the indoor condenser 12 being used as user side heat exchanger.Air mix door 34 is driven by servomotor (not shown), and the operation of wherein said servomotor is controlled according to the control signal exported from air conditioning controller with function.
Defrosting open pore 36a, facial open pore 36b and foot open pore 36c have for regulating the defrosting door 37a of the aperture area of defrosting open pore 36a, for regulating the facial door 37b of the aperture area of facial open pore 36b and for regulating the foot door 37c of the aperture area of foot open pore 36c respectively in the respective upstream side of its air stream.
Defrosting door 37a, facial door 37b and foot door 37c are used as and change for by the air outlet slit mode changing apparatus of blow air to the opening/closing state of each air outlet slit in vehicle interior, and driven by electric actuator (not shown), the operation of wherein said electric actuator is controlled according to the control signal exported from air conditioning controller with function.
Air outlet slit pattern comprises facial model, two-stage pattern and foot's pattern, described facial model is used for being blowed by the upper part of the body of air towards the passenger vehicle interior from facial air outlet slit by opening facial air outlet slit completely, described two-stage pattern is used for being blowed towards the upper part of the body of the passenger in vehicle interior and foot by air by opening facial air outlet slit and foot's air outlet slit simultaneously, and described foot pattern is used for opening defrost air outlet and main from foot's air outlet slit blow air a little by opening foot's air outlet slit completely simultaneously.
Passenger can switch on the described subsequently guidance panel of manual operation, thus setting is used for by opening defrost air outlet completely by air from defrost air outlet towards the defrosting mode that the inner surface of the windshield of vehicle blows.
Next, coolant circulation circuit 40 is below described.Coolant circulation circuit 40 be for by allow as cooling fluid cooling agent (such as, glycol water) cycle through the cooling fluid closed circuit that the coolant channel be formed in the above-mentioned motor MG for advancing cools the motor MG for advancing, described motor MG is of producing in operation in the car-mounted device of heat.
Coolant circulation circuit 40 is provided with cooling medium pump 41, electric T-shaped valve 42, radiator 43 and the bypass passageways 44 for allowing cooling agent to flow around radiator 43.
Cooling medium pump 41 is electrodynamic pumps, for being expressed to by cooling agent in the coolant channel in the motor MG that to be formed in coolant circulation circuit 40 for advancing, and the revolution of described cooling medium pump 41 (flow) is controlled by the control signal exported from air conditioning controller with function.Therefore, cooling medium pump 41 is used as by changing the cooling capacity adjusting portion regulating cooling capacity for the flow of the cooling agent cooling the motor MG for advancing.
Triple valve 42 makes cooling agent flow to the cooling fluid circuit in radiator 43 for the outlet side by the entrance side of cooling medium pump 41 being connected to radiator 43 and the outlet side be used for by the entrance side of cooling medium pump 41 being connected to bypass passageways 44 makes cooling agent walk around between another cooling fluid circuit that radiator 43 flows to switch.Operate the triple valve 42 controlled by the control voltage exported from air conditioning controller with function and be used as cooling fluid circuit switching device shifter.
Namely, as shown in by the dotted arrow of Fig. 1 etc., the coolant circulation circuit 40 of the present embodiment can for make cooling agent from cooling medium pump 41, motor MG, radiator 43 and cooling medium pump 41 for advancing according to this sequential loop cooling fluid circuit and for making cooling agent perform switching between the cooling fluid circuit of cooling medium pump 41, motor MG, bypass passageways 44 and cooling medium pump 41 for advancing sequential loop according to this.
Therefore, during the operation at the motor MG for advancing, triple valve 42 performs when being switched to for allowing cooling agent to walk around the cooling fluid circuit of radiator 43, cooling agent when not by its dissipate heat to radiator 43 temperature increase.That is, when triple valve 42 perform be switched to for allowing cooling agent to walk around the cooling fluid circuit of radiator 43 time, be stored in cooling agent for heat (heat of generation) contained in the motor MG that advances.
Radiator 43 is heat dissipation heat exchangers, and described heat dissipation heat exchanger is arranged in engine room, and between cooling agent and the extraneous air blowed from blower fan 17 heat-shift.As mentioned above, radiator 43 and outdoor heat converter 16 are configured to one to form heat converter structure 70.
The details of heat converter structure 70 is below described.Outdoor heat converter 16 in the present embodiment and each in radiator 43 are made up of so-called case tubing heat exchanger, described case tubing heat exchanger comprises multiple pipe for allowing cold-producing medium or cooling agent to flow through and for a pair header tank collected and distribute, described header tank is positioned at the both sides of pipe and is designed to collect or distribute the cold-producing medium or the cooling agent that flow through pipe.
More specifically, outdoor heat converter 16 comprises the multiple refrigerant pipe 16a for making flow of refrigerant pass through.Further, refrigerant pipe 16a is the flat tube in a direction perpendicular to the lengthwise direction with flattened cross-sectional.Each refrigerant pipe 16a is stacked with the predetermined gap between described refrigerant pipe, makes the flat surface of the outer surface of described refrigerant pipe in a parallel manner toward each other.
Therefore, for making the heat-absorption air passage 16b of the flow of external air blowed from blower fan 17 be formed around refrigerant pipe 16a, that is, be formed between adjacent refrigerant tubes 16a.
Radiator 43 comprises multiple cooling fluid pipe 43a, and described multiple cooling fluid pipe 43a flows through described cooling fluid pipe for allowing cooling agent, and has flattened cross-sectional in a direction perpendicular to the lengthwise direction.Be similar to refrigerant pipe 16a, cooling fluid pipe 43a is stacked with the predetermined gap between described cooling fluid pipe.For making the heat radiation air duct 43b of the flow of external air blowed from blower fan 17 be formed around cooling fluid pipe 43a, that is, be formed between adjacent cooling fluid pipe 43a.
In the present embodiment, outdoor heat converter 16 is partly made up of identical material for each header tank collected with distribute with radiator 43, and heat-absorption air passage is provided with heat radiation air duct the outer fin 50 be made up of identical material.Outer fin 50 joins pipe 16a and 43a to, make outdoor heat converter 16 and radiator 43 integrally formed with each other to form heat converter structure 70.
Outer fin 50 in using is the corrugated fins formed by the metal sheet with excellent thermal conductivity is bent to wave shape.Outer fin 50 be arranged on a part in heat-absorption air passage for promoting the heat exchange between cold-producing medium and extraneous air, and outer fin 50 be arranged on another part in heat radiation air duct for promoting the heat exchange between cooling agent and extraneous air.
Further, each outer fin 50 joins refrigerant pipe 16a and cooling fluid pipe 43a to, thus can realize the heat trnasfer between refrigerant pipe 16a and cooling fluid pipe 43a.
In above-mentioned the present embodiment, the refrigerant pipe 16a of outdoor heat converter 16, the cooling fluid pipe 43a of radiator 43, all to be formed by aluminium alloy for the header tank collected and distribute and outer fin 50, and mutually form one by soldering.In addition, in the present embodiment, the windward side of radiator 43 on the flow direction X of the extraneous air blowed by blower fan 17 is formed one with outdoor heat converter 16.
The electronic control unit of the present embodiment is below described.Air conditioning controller with function is made up of the known microcomputer and peripheral circuit thereof comprising CPU, ROM and RAM.Control unit to be operatively connected to the operation of each in the air conditioning controller with function 11 of the output of this control unit, 15a, 15b, 17,41 and 42 according to the air conditioning control program be stored in ROM by performing various operation and process.
One group of various sensor for controlling air conditioning is connected to the input side of air conditioning controller with function.Sensor comprise the Inside Air Temperature test section being used as the temperature detecting vehicle interior inner air sensor, for detect the temperature of extraneous air outside air sensor, for detecting the solar radiation sensor of the amount of the solar radiation of vehicle interior and the evaporator temperature sensor for the temperature (evaporator temperature) that detects the air that evaporimeter 20 indoor blows.In addition, sensor also comprises the coolant temperature sensor 52 of coolant temperature test section of the refrigerant emission temperature sensor of the temperature for detecting the cold-producing medium discharged from compressor 11, the coolant temperature Tw of the cooling agent detected for the outlet refrigerant temperature sensor 51 and being used as of the refrigerant temperature Te of the outlet side of sensing chamber's outer heat-exchanger 16 flowing into for being advanced motor MG.
In the present embodiment, coolant temperature sensor 51 detects the coolant temperature Tw of the cooling agent extruded from cooling medium pump 41.Alternatively.The coolant temperature Tw of the cooling agent be drawn in cooling medium pump 41 can be detected.
The guidance panel (not shown) that instrument board before compartment is arranged is connected to the input side of air conditioning controller with function.Operation signal is transfused to from all kinds air conditioning operation switch be arranged on guidance panel.The various air conditioning operation switches be arranged on panel comprise for the console switch of vehicle air conditioner, for setting the vehicle interior temperature configuration switch of the temperature of vehicle interior and the selector switch for select operating mode.
Air conditioning controller with function comprises the control part and mutual shape all-in-one-piece open/closed valve 15a etc. of the motor 11b for controlling compressor 11, and is designed to the operation controlling these parts.In the air conditioning controller with function of the present embodiment, for controlling the structure (hardware and software) of the operation of compressor 11 as discharge refrigerant capability control portion.Structure for controlling the operation of related device 15a and 15b being used as refrigerant flowpath switching device shifter is used as refrigerant flowpath control part.Structure for controlling the operation of the triple valve 42 of the cooling fluid circuit switching device shifter being used as cooling agent is used as cooling fluid circuit control part.
The air conditioning controller with function of the present embodiment comprises for determining whether frost is formed in the structure (frosting determination portion) at outdoor heat converter 16 place according to the detection signal from the above sensor group for air conditioning control.Particularly, when the speed of traveling vehicle is equal to or less than predetermined reference value (in the present embodiment, 20km/h), and when the refrigerant temperature Te of the outlet side of outdoor heat converter 16 is equal to or less than 0 DEG C, the frosting determination portion of the present embodiment is determined to produce frosting at outdoor heat converter 16 place.
The determination using frosting determination portion to carry out is not limited to this.Alternatively, such as, when vehicle stops (particularly, car speed=0km/h) and Vehicular system to keep running, and when the refrigerant temperature Te of the outlet side of outdoor heat converter 16 is equal to or less than 0 DEG C, can determine to produce frosting at outdoor heat converter 16 place.
Next, the operation of the vehicle air conditioner 1 with above layout in the present embodiment is below described.The vehicle air conditioner 1 of the present embodiment can perform for the heating operation of heated vehicle inside and the cooling down operation for cooling vehicle interior.In heating operation, defrost operation and used heat collection operation can also be performed.Each operation is below described
(a) heating operation
Time when the console switch of guidance panel opens (ON) by selector switch selection heating mode operation, heating operation starts.Then, in heating operation, when frosting determination portion determines that frost is formed in outdoor heat converter 16 place, perform defrost operation.When the coolant temperature Tw detected by coolant temperature sensor 52 is equal to or greater than predetermined reference temperature (in the present embodiment, 60 DEG C), performs used heat and collect operation.
In normal heating operation, air conditioning controller with function closes open/closed valve 15a, and triple valve 15b is switched to the refrigerant flowpath of the entrance side for the outlet side of outdoor heat converter 16 being connected to accumulator 18.Further, controller actuating cooling medium pump 41 thus extrude cooling agent with predetermined amount of flow, and the triple valve 42 of coolant circulation circuit 40 is switched to allows cooling agent to walk around the refrigerant flowpath of radiator 43.
Like this, heat pump cycle 10 is switched to and allows cold-producing medium as the refrigerant flowpath flowed shown in by the solid arrow in Fig. 1.Cooling fluid closed circuit 40 is also switched to and allows cold-producing medium as the cooling fluid flowing path of flowing shown in by the dotted arrow in Fig. 1.
The air conditioning controller with function with above-mentioned refrigerant flowpath and cooling fluid circuit reads from the detection signal of the sensor group controlled for air conditioning and the operation signal from guidance panel.According to detection signal and operation signal, target outlet air themperature TAO is calculated as the target temperature of the air that will be blown into vehicle interior.Further, determine to be connected to the mode of operation of the various air conditioning control assemblies of the outlet side of air conditioning controller with function according to the target outlet air themperature TAO calculated and the detection signal that carrys out sensor group.
Such as, the discharge refrigerant ability of compressor 11, namely, the control signal outputting to the motor of compressor 11 is determined as follows: first, determines the target evaporator outlet air temperature TEO of indoor evaporator 20 with reference to the control chart be stored in advance in air conditioning controller with function according to target outlet air themperature TAO.
According to target evaporator outlet air temperature TEO and the deviation indoor between the air themperature detected by evaporator temperature sensor that blows of evaporimeter 20, determine the control signal of the motor that will be output to compressor 11, thus the blow air temperature of the air making evaporimeter 20 indoor blow by utilizing feedback is close to target evaporator outlet air temperature TEO.
According to the control signal being determined the servomotor that will be output to air mix door 34 by the air themperature that blows and the temperature of the cold-producing medium detected by refrigerant emission temperature sensor of discharging from compressor 11 of target outlet air themperature TAO, indoor evaporator 20, the temperature of the air being blown into vehicle interior is become temperature that passenger uses temperature setting switch setting in vehicle chamber.
During normal heating operation, defrost operation and used heat collect operation, the opening degree of air mix door 34 can be controlled, make the air of the whole volume blowed from air blast 32 in vehicle interior through indoor condenser 12.
The control signal that will be output to the electric actuator of inner/outer air switch 33 is determined with reference to the control chart be stored in advance in air conditioning controller with function.In the present embodiment, substantially, the exterior air patterns for introducing extraneous air is given higher priority.But, when target outlet air themperature TAO becomes ultra-high temperature heating properties high with needs, or in defrost operation, select the inner air pattern for introducing inner air.
The control signal of the electric actuator that will be output to each air outlet slit mode changing apparatus 37a-37c is determined with reference to the control chart be stored in advance in air conditioning controller with function.In the present embodiment, when target outlet air themperature TAO is increased to high temperature range from low temperature range, air outlet slit pattern according to this order is switched to two-stage pattern from facial model, is then switched to foot's pattern.Therefore, in heating operation, tend to select foot's pattern.
Then, the control signal determined as mentioned above is output to various air conditioning control assembly.After this, until stopped by guidance panel request vehicle air conditioning, control program repeats in each predetermined controlled circulation.Control program comprises a series of process successively: read detection signal and operation signal, calculating target outlet air themperature TAO, determine various air conditioning control assembly mode of operation and export control voltage and control signal.This repetition of executive control program in an identical manner substantially in other operator scheme.
In heat pump cycle 10, during normal heating operation, the high-pressure refrigerant discharged from compressor 11 flow into indoor condenser 12.Flow into cold-producing medium in indoor condenser 12 by indoor evaporator 20 with the vehicle interior air heat-shift blowed from air blast 32 to distribute the heat from described indoor evaporator 20, vehicle interior air is heated.
Because open/closed valve 15a closes, the high-pressure refrigerant that therefore condenser 12 flows out indoor flow into the fixed restriction device 13 of heating to be depressurized by described throttling arrangement and to expand.The low pressure refrigerant reduced pressure by the fixed restriction device 13 of heating and expand flow in outdoor heat converter 16.The low pressure refrigerant flow in outdoor heat converter 16 absorbs heat to be evaporated from the extraneous air blowed by blower fan 17.
Now, in coolant circulation circuit 40, perform the switching be switched to for allowing cooling agent to walk around the cooling fluid circuit of radiator 43, thus prevent from cooling agent from distributing heat to flowing through the cold-producing medium of outdoor heat converter 16, and prevent cooling agent from flow through the refrigerant suction heat of outdoor heat converter 16.That is, cooling agent can produce heat affecting to the cold-producing medium flowing through outdoor heat converter 16 not at all.
Because triple valve 15b is switched to the refrigerant flowpath of the entrance side outlet side of outdoor heat converter 16 being connected to accumulator 18, the cold-producing medium that therefore heat exchanger 16 flows out outdoor to flow in accumulator 18 and to be separated into liquid and gas.The vapor phase refrigerant be separated by accumulator 18 is sucked by compressor 11 and is again compressed.
As mentioned above, in normal heating operation, the air of vehicle interior is heated by indoor condenser 12 by heat contained the cold-producing medium from compressor 11 discharge, thus can perform the heating operation of vehicle interior.
(b) defrost operation
Next, below defrost operation is described.For by outdoor heat converter 16 between cold-producing medium and extraneous air heat-shift come in the refrigerating circulatory device of vaporized refrigerant, be similar to the heat pump cycle 10 of the present embodiment, when one of the temperature as outdoor heat converter 16 refrigerant evaporating temperature (particularly, the temperature of the outer surface of outdoor heat converter 16, or the temperature of outdoor heat converter 16) become and be equal to or less than frosting temperature (particularly, 0 DEG C) time, frost may be formed in outdoor heat converter 16 place.
White this formation by the heat-absorption air passage 16b of white close chamber outer heat-exchanger 16, thus reduces the heat exchange performance of outdoor heat converter 16 hastily.In the heat pump cycle 10 of the present embodiment, when determining to produce frosting at outdoor heat converter 16 place by frosting determination portion in heating operation, defrost operation starts.
In defrost operation, air conditioning controller with function stops the operation of compressor 11, and the operation of the fan 17 that turns off the blast.Therefore, during defrost operation, compared with normal heating operation, the flow flowing into the cold-producing medium in outdoor heat converter 16 reduces, thus the volume causing the heat-absorption air passage 16b neutralization flowing into outdoor heat converter 16 to flow into the extraneous air in the heat radiation air duct 43b of radiator 43 reduces.
The triple valve 42 of coolant circulation circuit 40 is switched to and allows cooling agent as flowing into the cooling fluid circuit in radiator 43 shown in by the dotted arrow in Fig. 2 by air conditioning controller with function.Therefore, coolant circulation circuit 40 is switched to for making cold-producing medium not make cold-producing medium be circulated by heat pump cycle 10 as the cooling fluid circuit flowed shown in by the dotted arrow in Fig. 2.
Therefore, flow through heat contained in the cooling agent of the cooling fluid pipe 43a of radiator 43 is delivered to outdoor heat converter 16 heat-absorption air passage 16b via outer fin 50, perform the defrost operation of outdoor heat converter 16 by this.That is, the used heat of the motor MG for advancing can be effectively used to realize defrosting.
C () used heat collects operation
Next, below describe used heat and collect operation.Preferably, in order to suppress, the motor MG's for advancing is overheated, and the temperature of cooling agent is maintained at below predetermined upper limit temperature or described predetermined upper limit temperature.Further, the friction loss caused in order to the viscosity reducing the lubrication oil in the motor MG owing to being sealed to for advancing increases, preferably, the temperature of cooling agent is maintained at more than predetermined lower bound temperature or described predetermined lower bound temperature.
In the heat pump cycle 10 of the present embodiment, during heating operation when coolant temperature Tw is equal to or greater than predetermined reference temperature (being 60 DEG C in the present embodiment), perform used heat and collect operation.In defrost operation, the triple valve 15b of heat pump cycle 10 operates in the mode identical with normal heating operation, but the triple valve 42 of coolant circulation circuit 40 with the mode identical with defrost operation be switched to as shown in by the dotted arrow in 3 for making cooling agent flow to cooling fluid circuit in radiator 43.
Therefore, as shown in by the solid arrow of Fig. 3, from the air of high pressure, high temperature refrigerant in indoor condenser 12 heated vehicle inside that compressor 11 discharges, be then depressurized with the fixed restriction device 13 of the mode identical with normal heating operation by heating and expand to flow into outdoor heat converter 16.
Because triple valve 42 is switched to for making cooling agent flow to cooling fluid circuit in radiator 43, the low pressure refrigerant therefore flow in outdoor heat converter 16 absorbs and containedly in heat contained in the extraneous air blowed by blower fan 17 and cooling agent passes to the heat of described cooling agent to be evaporated via outer fin 50.Other actuating is identical with the actuating in normal heating operation.
As mentioned above, collect in operation at used heat, the air of vehicle interior utilizes the heat of the cold-producing medium discharged from compressor 11 to be heated at indoor condenser 12, thus can perform the heating of vehicle interior.Now, cold-producing medium not only absorbs heat contained in extraneous air, but also the heat passing to described cooling agent via outer fin 50 contained in absorption cooling agent, thus the used heat of the motor MG for advancing can be effectively used to realize the heating of vehicle interior.
(d) cooling down operation
Time when the console switch at guidance panel opens (ON) by selector switch selection cooling down operation pattern, cooling down operation starts.In cooling down operation, air conditioning controller with function opens open/closed valve 15a, and triple valve 15b is switched to the refrigerant flowpath of the entrance side of the fixed restriction device 19 for the outlet side of outdoor heat converter 16 being connected to cooling.Therefore, heat pump cycle 10 is switched to for making cold-producing medium as the refrigerant flowpath flowed shown in by the solid arrow in Fig. 4.
Now, when coolant temperature Tw is equal to or greater than reference temperature, the triple valve 42 of coolant circulation circuit 40 is switched to for making cooling agent flow to cooling fluid circuit in radiator 43.On the contrary, when coolant temperature Tw is less than predetermined reference temperature, triple valve 42 is switched to the cooling fluid circuit for allowing cooling agent to walk around radiator 43.The flowing of the cooling agent obtained when coolant temperature Tw is equal to or greater than reference temperature is represented by the dotted arrow in Fig. 4.
During cooling down operation, in heat pump cycle 10, the high-pressure refrigerant discharged from compressor 11 flow into indoor condenser 12, and with in the vehicle interior blowed from air blast 32 and by the air exchange heat of indoor evaporator 20 to dispel the heat.Because open/closed valve 15a opens, the high-pressure refrigerant that therefore condenser 12 flows indoor flow in outdoor heat converter 16 via the bypass passageways 14 for fixed restriction device.Flow into low pressure refrigerant in outdoor heat converter 16 further towards the extraneous air distribute heat blowed by blower fan 17.
Be switched to the refrigerant flowpath of the entrance side of the fixed restriction device 19 for the outlet side of outdoor heat converter 16 being connected to cooling due to triple valve 15b, the cold-producing medium that therefore heat exchanger 16 flows outdoor is depressurized by the fixed restriction device 19 of cooling and is expanded.The cold-producing medium flowed from the fixed restriction device 19 of cooling flow into indoor evaporator 20, and from the absorption of air heat of the vehicle interior blowed by air blast 32 to be evaporated.Like this, the air of vehicle interior can be cooled.
The cold-producing medium that evaporimeter 20 flows indoor flow in accumulator 18, is then separated into liquid and gas by accumulator.To be inhaled in compressor 11 by the vapor phase refrigerant that accumulator 18 is separated and by compressor 11 second compression again.As mentioned above, during cooling down operation, low pressure refrigerant is from the absorption of air heat of vehicle interior and evaporated in indoor evaporator 20, thus the air of cooling vehicle interior, thus the cooling of vehicle interior can be performed.
As mentioned above, the air conditioner for vehicle 1 in the present embodiment can perform switching between the refrigerant flowpath of heat pump cycle 10 and between the cooling fluid circuit of coolant circulation circuit 40, thus performs various operation.Further, as described later, in the defrost operation of the present embodiment, the used heat of the motor MG for advancing can be effectively used to defrost to outdoor heat converter 16.
More specifically, in the present embodiment, the heat-absorption air passage 16b of the outdoor heat converter 16 and heat radiation air duct 43b of radiator 43 is provided with the outer fin 50 be made up of identical metal material can carry out heat trnasfer between refrigerant pipe 16a and cooling fluid pipe 43a.Therefore, during defrost operation, heat contained in cooling agent can be delivered to outdoor heat converter 16 via outer fin 50.
Therefore, compared with the circulation being delivered to the correlation technique of outdoor heat converter 16 via air with heat contained in wherein cooling agent, the present embodiment can suppress the loss in heat trnasfer, therefore can effectively use the used heat of the motor MG for advancing to defrost to outdoor heat converter 16.In addition, the present embodiment can reduce the time of defrost operation.
During defrost operation, compared with the time before defrost operation, the operation of compressor 11 stops, and the flow flowing into the cold-producing medium in outdoor heat converter 16 reduces (particularly, be set to zero (0)), thus the heat passing to outdoor heat converter 16 via outer fin 50 can be prevented to be absorbed in the cold-producing medium flowing through refrigerant pipe 16a.Therefore, the used heat of the motor MG for advancing can be more effectively used to defrost to outdoor heat converter 16 during defrost operation.
In other words, during defrost operation, the operation of compressor 11 is stopped the heating efficiency (in the present embodiment, not showing heating efficiency) reduced for adding hot-air at indoor condenser 12 place, thus the heat that minimizing cold-producing medium absorbs in outdoor heat converter 16.Therefore, can more effectively use the used heat of the motor MG for advancing to defrost to outdoor heat converter 16 in defrost operation.
During defrost operation, the running of blower fan 17 is stopped to reduce the volume of the extraneous air flow in heat-absorption air passage 16b and heat radiation air duct 43b (particularly, be set to zero (0)), thus the heat passing to outdoor heat converter 16 via outer fin 50 can be prevented to be absorbed into flow through in the extraneous air of heat-absorption air passage 16b and heat radiation air duct 43b.Therefore, can more effectively use the used heat of the motor MG for advancing to defrost to outdoor heat converter 16 in defrost operation.
In the heat pump cycle 10 of the present embodiment, during normal heating operation, the triple valve 42 of coolant circulation circuit 40 is switched to the cooling fluid circuit for allowing cooling agent to walk around radiator 43, thus is stored in cooling agent by heat (heat of generation) contained in the motor MG being used for advancing.Therefore, during defrost operation, defrost operation can be completed at short notice by the heat stored.
In the heat converter structure 70 of the present embodiment, radiator 43 is arranged in the windward side of the flow direction X of the extraneous air blowed by blower fan 17 relative to outdoor heat converter 16.In other words, in heat converter structure 70, outdoor heat converter 16 and radiator 43 arranged in series, make extraneous air flow to outdoor heat converter 16 from radiator 43.
Therefore, heat contained in cooling agent not only can be delivered to outdoor heat converter 16 via outer fin 50, but also can be delivered to outdoor heat converter 16 via air.Namely, even if when blower fan 17 stops, heat contained in cooling agent also can be delivered to outdoor heat converter 16 through the extraneous air of heat converter structure 70 by the air pressure (ram-air pressure) on the direct of travel of traveling vehicle.Therefore, during defrost operation, can more effectively use the heat supplied from the motor MG for advancing to defrost to outdoor heat converter 16.
When car speed is equal to or less than with reference to car speed, and when the refrigerant temperature Te of the outlet side of outdoor heat converter 16 is equal to or less than 0 DEG C, the frosting determination portion be included in the air conditioning controller with function of the present embodiment determines that frost is formed in outdoor heat converter 16.Therefore, can consider that car speed suitably determines frosting.
That is, when vehicle is at low speed, ram-air pressure step-down and flow into the extraneous air in engine room volume reduce.Therefore, the volume flowing into the extraneous air of each in outdoor heat converter 16 and radiator 43 reduces.Therefore, in defrost operation, the heat passing to outdoor heat converter 16 via outer fin 50 can be prevented to be absorbed in extraneous air, thus effective defrosting can be realized.
Further, in the heat pump cycle 10 of the present embodiment, when the coolant temperature Tw detected by coolant temperature sensor 52 is equal to or greater than reference temperature, by triple valve 42 being switched to the cooling fluid circuit for making cooling agent flow in radiator 43, performing used heat and collecting operation.Therefore, heat contained in cooling agent is distributed by radiator 43, thus the motor MG for advancing can be prevented overheated.
In addition, collect in operation at used heat, be delivered to outdoor heat converter 16 by the heat that radiator 43 distributes, and can be absorbed in cold-producing medium, thus the coefficient of performance (COP) of heat pump cycle 10 can be improved, and therefore can the air of heated vehicle inside effectively.Therefore, the heating properties of vehicle air conditioner 1 can be improved.
In the present embodiment, the cooling fluid circuit that triple valve 42 is switched to for making cooling agent flow in radiator 43 according to the reference temperature of 60 DEG C collects operation to perform used heat.Described reference temperature can be determined by the heat exchange performance etc. of outdoor heat converter 16 grade.
Such as, when the weight that WW (g) is the cooling agent in coolant circulation circuit 40, WG (g) is formed in the amount of the frost in outdoor heat converter 16, TR (DEG C) is the temperature of air that blows of heat exchanger 16 outdoor, the store heat Qst be stored in the cooling agent in coolant circulation circuit 40 is represented by following formula F 1, and is represented by following formula F 2 for heat (hereinafter referred to as " the defrosting heat ") Qdf defrosting required:
Specific heat × (Tw-TR) of Qst=WW × cooling agent ... (F1)
The latent heat of vaporization-specific heat of water × TR+ outdoor heat converter 16 × thermal capacity × the TR+ of Qdf=WG × water is dispersed into the heat in air ... (F2)
The heat Qst wherein stored needs to exceed defrosting heat Qdf to guarantee the defrosting of outdoor heat converter 16.
Further, when the outdoor heat converter 16 in formula F 2 thermal capacity and be left in the basket not-time when being dispersed in air heat, melt the minimum defrosting heat Qdf2 required for frost being formed in outdoor heat converter 16 place and represented by following formula F 3:
The latent heat of vaporization-specific heat of water × the TR of Qdf2=WG × water ... (F3)
Therefore, in order to perform defrosting, at least following formula F 4 must be satisfied:
Qst＞Qdf2…(F4)
Formula (F1) and (F3) are substituted in above formula (F4) following formula (F5) can be produced:
Tw > TR+ (latent heat of vaporization-specific heat of water × TR of WG × water)/(specific heat of WW × cooling agent) ... (F5)
Therefore, the temperature Tw meeting above formula F 5 can be confirmed as reference temperature.
In other words, the heat pump cycle of the present embodiment comprises the coolant temperature test section (coolant temperature sensor 52) of the coolant temperature Tw for detecting the cooling agent flow in the car-mounted device (the motor MG for advancing) producing in operation heat and the outdoor blow air temperature detecting part for the air themperature TR that detects the air that heat exchanger 16 outdoor blows.When the coolant temperature Tw detected by coolant temperature test section (coolant temperature sensor 52) and the air themperature TR that detected by outdoor blow air temperature detecting part meets following relation, cooling fluid circuit switching device shifter (triple valve 42) can perform the switching be switched to for allowing cooling fluid (cooling agent) to flow into the cooling fluid circuit in heat dissipation heat exchanger (radiator 43):
Tw > TR+ (latent heat of vaporization-specific heat of water × TR of WG × water)/(specific heat of WW × cooling agent)
In the heat pump cycle 10 of the present embodiment, in heating operation (heater operation) period, the flow direction flowing through the cold-producing medium of the refrigerant pipe 16a of outdoor heat converter 16 is identical with the flow direction flowing through the cold-producing medium of refrigerant pipe 16a in cooling down operation (cooler operates) period.When viewed from the flow direction of extraneous air, the position relationship between the heat exchange area of the heat exchange area of the refrigerant inlet side of outdoor heat converter 16 and the refrigerant outlet side of described outdoor heat converter 16 can not change between heating operation and cooling down operation.Therefore, the position relationship between the Temperature Distribution of the Temperature Distribution of the heat exchange area of outdoor heat converter 16 and the heat exchange area of heat dissipation heat exchanger 43 can not change.
That is, outdoor heat converter 16 and heat dissipation heat exchanger 43 are thought a heat converter structure 70 by macroscopic view.In this case, for at outdoor heat converter 16 place from during the cooling down operation of refrigerant loses heat, the flow direction of externally air can overlap the heat exchange area of the cooling fluid inlet side of the heat dissipation heat exchanger 43 for making cooling fluid flow at a relatively high temperature for making the heat exchange area of the refrigerant inlet side of the outdoor heat converter 16 of the flow of refrigerant at a relatively high temperature with the degree of superheat.Further, for making the heat exchange area of the refrigerant outlet side of the outdoor heat converter 16 of the flow of refrigerant at relatively low temperature with the degree of superheat flow direction of externally air can overlap the heat exchange area of the cooling fluid outlet side of the heat dissipation heat exchanger 43 for making cooling fluid flow at relatively low temperature.By this layout, can make by the flowing of the cold-producing medium of outdoor heat converter 16 parallel with the flowing of the cooling fluid by heat dissipation heat exchanger 43 to realize effective heat exchange.
Further, for in the heating operation of outdoor heat converter 16 place vaporized refrigerant, the heat exchange area of the refrigerant inlet side of the outdoor heat converter 16 flowed at relatively low temperature for making cold-producing medium the flow direction of externally air can overlap the heat exchange area of the cooling fluid inlet side of the heat dissipation heat exchanger 43 for making cooling fluid flow at a relatively high temperature.Therefore, frost can be effectively prevented to be formed in the heat exchange area of the refrigerant inlet side of the outdoor heat converter 16 for allowing cold-producing medium to flow through at relatively low temperature.
Second embodiment
Different from the first embodiment, in the present embodiment, as shown in the overall structure schematic diagram of Fig. 6, indoor condenser 12 is removed, and brine loop 60 is configured to for circulating brine, that is, as the example adding hot fluid.Fig. 6 is the overall structure schematic diagram of refrigerant flowpath etc. during heating operation in display the present embodiment, and the flowing of the cold-producing medium wherein in heat pump cycle 10 is represented by solid line, and the flowing of cooling agent in coolant circulation circuit 40 is represented by dotted arrow.
In figure 6, identical or equivalent with the parts of the first embodiment parts are represented by identical Reference numeral.To other accompanying drawing following too.
Salt solution in the present embodiment adds hot fluid for what the heat comprised in the cold-producing medium discharged from compressor 11 is passed to the air that is blown into vehicle interior.Be similar to the cooling agent as cooling fluid, can glycol water be used.Brine loop 60 comprises brine pump 61, salt solution-refrigerant heat exchanger 62 and heater core 63.
Brine pump 61 is the electrodynamic pumps for being forced into by salt solution in the heater core 63 of salt solution-refrigerant heat exchanger 62.Brine pump 61 has the basic structure identical with the basic structure of the cooling medium pump 41 of coolant circulation circuit 40.Salt solution-refrigerant heat exchanger 62 is for discharging from compressor 11 and flowing through the heat exchanger carrying out heat exchange between the cold-producing medium of coolant channel 62b and the salt solution flowing through brine channel 62a.
Particularly, salt solution-refrigerant heat exchanger 62 can adopt double-tube type heat converter structure, and described double-tube type heat converter structure is made up of for the formation of pipe in coolant channel 62b with being arranged in outer tube the outer tube forming brine channel 62a.Alternatively, coolant channel 62b can be formed as outer tube, and brine channel 62a can be formed as interior pipe.The refrigerant pipe forming coolant channel 62b can pass through together with soldered joint with the refrigerant pipe forming brine channel 62a to form heat exchange structure etc.
Heater core 63 is arranged in the housing 31 of the room air regulon 30 of vehicle air conditioner 1.Heater core 63 is heat exchangers of heating, and described heat exchanger is by heat-shift between the salt solution of described heat exchanger and the vehicle interior air passing through indoor evaporator 20.Therefore, the heater core 63 of the present embodiment is used as user side heat exchanger, and this is identical with indoor condenser 12.The structure of the structure of other parts of the present embodiment and operation and other parts in the first embodiment with operate identical.
Therefore, even the operation of the vehicle air conditioner 1 of the present embodiment can provide the effect identical with the vehicle air conditioner of the first embodiment.Further, owing to providing brine loop 60 in the present embodiment, therefore can extrude by the cooling agent changing brine pump 61 heating efficiency that ability easily regulates heater core 63.
Be similar to cooling agent, during normal heating operation, the salt solution in brine pump 61 can also store heat contained the cold-producing medium discharged from compressor 11.Therefore, even if when in defrost operation, compressor 11 stops, brine pump 61 also can operate the auxiliary heating operation performing vehicle interior.
3rd embodiment
Be different from the heat pump cycle 10 of the first embodiment, as shown in the overall structure schematic diagram of Fig. 7, in the present embodiment, outdoor unit bypass passageways 64 is increased to allow from the fixed restriction device 13 heated or to walk around outdoor heat converter 16 for the cold-producing medium that the bypass passageways 14 of fixed restriction device flows.In addition, open/closed valve 15c is increased further to open and close outdoor unit bypass passageways 64.
Fig. 7 be in display the present embodiment during defrost operation the overall structure schematic diagram of refrigerant flowpath, the flowing of the cold-producing medium wherein in heat pump cycle 10 is represented by solid line, and the flowing of cooling agent in coolant circulation circuit 40 is represented by dotted arrow.
Open/closed valve 15c has and is arranged on for the identical basic structure of the basic structure of the open/closed valve 15a in the bypass passageways 14 of fixed restriction device.The pressure loss produced in by the cold-producing medium of open/closed valve 15c when open/closed valve 15c opens than when cold-producing medium much smaller by the pressure loss produced in the refrigerant during outdoor heat converter 16.
Therefore, when open/closed valve 15c opens, from the fixed restriction device 13 of heating or flow into outdoor unit bypass passageways 64 for most of cold-producing mediums that the bypass passageways 14 of fixed restriction device flows, and almost not flow in outdoor heat converter 16.
In the present embodiment, in defrost operation, when not stopping the running of compressor 11, air conditioning controller with function opens open/closed valve 15c, and in other operator scheme, open/closed valve 15c closes.Therefore, during defrost operation, the flow flowing into the cold-producing medium in outdoor heat converter 16 reduces.The structure of the structure of other parts in the present embodiment and operation and other parts in the first embodiment with operate identical.
Therefore, even the operation of the vehicle air conditioner 1 of the present embodiment also can provide the effect identical with the vehicle air conditioner of the first embodiment.Further, due to compressor 11 in the present embodiment operate in defrost operation during do not stop, therefore indoor condenser 12 can utilize calorimeter contained the cold-producing medium discharged from compressor 11 to reveal air heat ability, thus performs the heating operation of vehicle interior.
Now, in defrost operation, identical with the flow direction in heating operation (normal operating) by the flow direction of the cold-producing medium of the refrigerant pipe 16a of outdoor heat converter 16, thus promptly can be transformed into defrost operation from normal operating, or be transformed into normal operating from defrost operation.Therefore, defrosting time can be reduced further.
From the flow direction of extraneous air, positioning relation between the heat exchange area of the heat exchange area of the refrigerant inlet side of outdoor heat converter 16 and the refrigerant outlet side of outdoor heat converter 16 can not change relative to the heat exchange area of radiator 43, thus the cold-producing medium of the refrigerant pipe 16a flowing through outdoor heat converter 16 can be suppressed and flow through radiator 43 cooling fluid pipe 43a cooling fluid between the larger fluctuation of amount of heat trnasfer.
Namely, in the related, when performing heat exchange via outer fin 50 between the refrigerant pipe 16a and the cooling fluid pipe 43a of radiator 43 of outdoor heat converter 16, relation between the flowing of the whole cold-producing medium in outdoor heat converter 16 and the flowing of the whole cooling agent in radiator 43 may become parallel from contrary, or from parallel changeabout.But the present embodiment can avoid this situation.
Therefore, the heat pump cycle of the present embodiment can suppress the larger fluctuation of the amount of the heat trnasfer flowed through between the cold-producing medium of refrigerant pipe 16a and the cooling fluid flowing through cooling fluid pipe 43a, thus improves the flexibility of the design of outdoor heat converter 16 and radiator 43.
4th embodiment
The present embodiment has the loop structure roughly the same with the loop structure of the heat pump cycle 10 of the 3rd embodiment, but in defrost operation, have the control form of different air conditioning controller with functions, and this will be described in an illustrative manner following.
Particularly, in the present embodiment, during defrost operation, when not stopping the running of compressor 11, air conditioning controller with function opens open/closed valve 15a and open/closed valve 15c, and triple valve 15b is switched to the refrigerant flowpath of the entrance side of the fixed restriction device 19 for the outlet side (particularly, the outlet side of outdoor unit bypass passageways 64) of outdoor heat converter 16 being connected to cooling.
Therefore, in the present embodiment, in defrost operation, as shown in Figure 8, heat pump cycle 10 is switched to the circulation for circulating refrigerant in the following order: from compressor 11, to the fixed restriction device 19 of indoor condenser 12 (outdoor unit bypass passageways 64), cooling, indoor evaporator 20, accumulator 18 and compressor 11.
From cooling fixed restriction device 19 flow cold-producing medium when indoor evaporator 20 is evaporated from the absorption of air latent heat of vaporization, air can be cooled.Then, when the cold-producing medium discharged from compressor 11 is at indoor condenser 12 distribute heat, cooling-air is reheated.The structure of the structure of other parts in the present embodiment and operation and other parts in the first embodiment with operate identical.
Therefore, even the operation of the vehicle air conditioner 1 of the present embodiment can provide the effect identical with the vehicle air conditioner of the 3rd embodiment.Further, in the present embodiment, by cooled air again can be heated by indoor condenser 12 in defrost operation at indoor evaporator 20 place's vaporized refrigerant, thus defrosting and the heating of vehicle interior can be realized.
5th embodiment
Different from the heat pump cycle 10 of the first embodiment, as shown in the overall structure schematic diagram of Fig. 9, in the present embodiment, in an illustrative manner, increase shutoff device (passage interruption device) to be used to open or close for making extraneous air flow into inflow path in radiator 43.Fig. 9 is the overall structure schematic diagram of the refrigerant flowpath etc. in the defrost operation of display the present embodiment, and the flowing of the cold-producing medium wherein in heat pump cycle 10 is represented by solid line, and the flowing of cooling agent in coolant circulation circuit 40 is represented by dotted arrow.
Particularly, shutoff device 65 is formed by merging multiple cantilever door-plate.Shutoff device 65 is designed to by making door-plate open for making extraneous air flow into inflow path in radiator 43 at the upper in-migration in the direction of the flowing of the air from blower fan 17, and by making door-plate close for making extraneous air flow into inflow path in radiator 43 from the upper in-migration in direction of the air stream of blower fan 17 in crosscut.
Radiator 43 is positioned at the windward side of the flow direction X of the extraneous air blowed by blower fan 17 relative to outdoor heat converter 16.Shutoff device 65 cuts out for making extraneous air flow into inflow path in radiator 43, thus blocking flows into inflow path in outdoor heat converter 16 for making extraneous air.
Shutoff device 65 can be made up of sliding door etc.Shutoff device 65 is driven by servomotor (not shown), and the operation of wherein said servomotor is controlled by the control signal exported from air conditioning controller with function.
In the present embodiment, in defrost operation, shutoff device 65 operates to cut out for making extraneous air flow into inflow path in radiator 43, and in other operator scheme, and shutoff device 65 is operated to open for making extraneous air flow into inflow path in radiator 43.Therefore, during defrost operation, the volume flowing into the extraneous air in heat-absorption air passage 16b and heat radiation air duct 43b reduces.The structure of the structure of other parts in the present embodiment and operation and other parts in the first embodiment with operate identical.
Therefore, even the operation of the vehicle air conditioner 1 of the present embodiment can provide the effect identical with the vehicle air conditioner of the first embodiment.Further, in the present embodiment, during defrost operation, shutoff device 65 operates to cut out for making extraneous air flow into access path in radiator 43, and this can prevent because the advance ram-air pressure extraneous air of period of vehicle flows in heat-absorption air passage 16b and heat radiation air duct 43b.
6th embodiment
In the present embodiment, different from the first embodiment, the ad hoc structure of heat converter structure 70 is modified, and this will describe in an illustrative manner following.Figure 10-13 is below used to describe the details of heat converter structure 70.Figure 10 shows the perspective view of the profile of the heat converter structure 70 of the present embodiment.Figure 11 is the decomposition diagram of heat converter structure 70.Figure 12 is the cross-sectional view intercepted along the line A-A in Figure 10.Figure 13 is the exemplary perspective view for illustration of the flowing of the cold-producing medium in heat converter structure 70 and the flowing of cooling agent.
First, as shown in the exploded perspective view of figure 11, in the heat converter structure 70 of the present embodiment, on the flow direction X of the extraneous air blowed by blower fan 17, the refrigerant pipe 16a of outdoor heat converter 16 is arranged to two row, and the cooling fluid pipe 43a of radiator 43 is also arranged to two row.Further, refrigerant pipe 16a and cooling fluid pipe 43a is alternately arranged with each other and stacked.
Therefore, in the present embodiment, heat-absorption air passage 16b and heat radiation air duct 43b forms a space.The outer fin 50 identical with the outer fin of the first embodiment is arranged in the heat-absorption air passage 16b in a formation space and dispels the heat in air duct 43b, and corresponding outer fin 50 joins pipe 16a and 43a to.
A side (lower end side shown in Figure 10-13) on the longitudinal direction of refrigerant pipe 16a and cooling fluid pipe 43a, arranges refrigerant side header tank 16c for collecting or distributing the cold-producing medium flowing through refrigerant pipe 16a.Another side (upper end side shown in Figure 10-13) in a longitudinal direction, arranges cool stream side header tank 43c, for the cold-producing medium collecting or distribute the pipe 43a flowed through for cooling fluid.
Refrigerant side header tank 16c and cool stream side header tank 43c has identical basic structure.First, refrigerant side header tank 16c comprises for being connected to the cold-producing medium side plate 161 of refrigerant pipe 16a and the cooling fluid pipe 43a being arranged to two row respectively and will being fixed to refrigerant side intermediate plate 162 and the refrigerant side header tank 163 of refrigerant side connecting plate 161.
As shown in the cross-sectional view of Figure 12, refrigerant side intermediate plate 162 is fixed to refrigerant side connecting plate 161 to form multiple recess 162b between refrigerant side connecting plate 161 and refrigerant side intermediate plate 162 itself, and described multiple recess forms the multiple spaces be communicated with cooling fluid pipe 43a.These spaces are used as the cooling fluid pipe 43a connection making to be arranged to two row on the flow direction X of extraneous air and the connected space for cooling fluid be connected together.
Cross section around the recess 432 that Figure 12 display is arranged in cool stream side intermediate plate 432 is clearly to illustrate.As mentioned above, because refrigerant side header tank 16c has the basic structure identical with the basic structure of cool stream side header tank 43c, therefore refrigerant side connecting plate 161 and recess 162b are illustrated in bracket.
The part corresponding with refrigerant pipe 16a that through hole 162a is arranged on refrigerant side intermediate plate 162 sentences the both sides through refrigerant side intermediate plate 162.Refrigerant pipe 16a inserts in through hole.Therefore, on one end of refrigerant side header tank 16c, compared with cooling fluid pipe 43a, refrigerant pipe 16a gives prominence to towards refrigerant side header tank 16c.
Refrigerant side header tank 163 is fixed to refrigerant side connecting plate 161 and refrigerant side intermediate plate 162 to be formed for collecting the collection space 163a of cold-producing medium and the allocation space 163b for assignment system cryogen within it.Particularly, refrigerant side header tank 163 is formed by stamped metal sheets is become the two mountains shape shape (W shape shape) when observing in a longitudinal direction.
The center of two mountains shape shape of refrigerant side header tank 163 joins refrigerant side intermediate plate 162 to and participates in collection space 163a and allocation space 163b to make header tank 163.In the present embodiment, collection space 163a is arranged on the windward side of flow direction X of extraneous air, and allocation space 163b is arranged on the leeward side of the flow direction X of extraneous air.
Refrigerant side header tank 163 one end is along the longitudinal direction connected to for making cold-producing medium flow into cold-producing medium inflow pipe 164 in allocation space 163b, and is connected to the cold-producing medium effuser 165 for making cold-producing medium flow out from collection space 163a.Refrigerant side header tank 163 another end is along the longitudinal direction closed component and closes.
On the other hand, there is mutually isostructural cool stream side header tank 43c as above also to comprise cooling fluid side connecting plate 431, be fixed to the cool stream side intermediate plate 432 of cooling fluid side connecting plate 431 and cool stream side header tank 433.
Shown in cross-sectional view as shown in figure 12, the cold-producing medium connected space that two row refrigerant pipe 16a are connected together is formed by the recess 432b in the cool stream side intermediate plate 432 be arranged between cooling fluid side connecting plate 431 and cool stream side intermediate plate 432 by the flow direction X of extraneous air.
The part corresponding with cooling fluid pipe 43a that through hole 432a is arranged on cool stream side intermediate plate 432 sentences the both sides through cool stream side intermediate plate 432.Cooling fluid pipe 43a inserts in through hole.Therefore, in the side of cool stream side header tank 43c, compared with refrigerant pipe 16a, cooling fluid pipe 43a gives prominence to towards cool stream side header tank 43c.
Further, cool stream side header tank 433 is fixed to cooling fluid side connecting plate 431 and cool stream side intermediate plate 432 to be formed for collecting the collection space 433a of cooling medium and the allocation space 433b for distributing cooling medium wherein.Particularly, in the present embodiment, allocation space 433b is arranged on the windward side of the flow direction X of extraneous air, and collection space 433a is arranged on the leeward side of the flow direction X of extraneous air.
The cooling fluid that one end in a longitudinal direction of cool stream side header tank 433 is connected to for making cooling fluid flow in allocation space 433b flows into pipe 434, and is connected to for making the cooling fluid that cooling fluid flows out from collection space 433a flow out pipe 435.The cool stream side header tank 43c other end is in a longitudinal direction closed by enclosed member.
Therefore, in the heat converter structure 70 of the present embodiment, as shown in the exemplary perspective view of Figure 13, the flow direction X that the cold-producing medium flow into via cold-producing medium inflow pipe 164 in the allocation space 163b of refrigerant side header tank 16c flow into the extraneous air between the refrigerant pipe 16a being arranged to two row is arranged in each refrigerant pipe 16a of leeward side.
In addition, the cold-producing medium flowed out from each refrigerant pipe 16a being arranged on leeward side is arranged on each refrigerant pipe 16a of windward side via the flow direction X being formed in the space formed between the cooling fluid side connecting plate 431 of cool stream side header tank 43c and cool stream side intermediate plate 432 and flowing into externally air.
Then, as shown in by the solid arrow in Figure 13, the cold-producing medium flowed out from the refrigerant pipe 16a being arranged on windward side is collected into the collection space 163a of refrigerant side header tank 16c, then flows out from refrigerant outlet pipe 165.That is, in the heat converter structure 70 of the present embodiment, cold-producing medium is from the refrigerant pipe 16a of leeward side to cool stream side header tank 43c with the refrigerant pipe 16a flow divert in order of windward side.
Similarly, as shown in by the dotted arrow in Figure 13, the cooling fluid pipe 43a of cooling fluid from the cooling fluid pipe 43a flow divert of windward side to refrigerant side header tank 16c and against the wind side in order.The structure of the structure of other parts in the present embodiment and operation and other parts of the first embodiment with operate identical.Even the operation of the car air-conditioner 1 of the present embodiment can provide the effect identical with the operation of the car air-conditioner of the first embodiment.
Further, in the present embodiment, the refrigerant pipe 16a in heat converter structure 70 and cooling fluid pipe 43a alternately arranges and stacked, makes can effectively defrost to outdoor heat converter 16 during defrost operation.
That is, in the heat converter structure 70 of the present embodiment, refrigerant pipe 16a is arranged between cooling fluid pipe 43a, and cooling fluid pipe 43a is arranged between refrigerant pipe 16a, and heat-absorption air passage 16b and heat radiation air duct 43b forms an air duct by this.
Situation about being arranged in series relative to the flow direction X of extraneous air with radiator 43 and outdoor heat converter 16 is compared, and in the present embodiment, can be arranged to close to each other for the pipe 43ab of cooling fluid and refrigerant pipe 16a.Therefore, cooling fluid pipe 43a can be positioned adjacent to the frost produced in refrigerant pipe 16a.Therefore, can effectively defrost to outdoor heat converter 16 in defrost operation.The heat converter structure 70 of the present embodiment can be applied to the heat pump cycle 10 of the second to the 5th embodiment.
7th embodiment
In above first embodiment, in an illustrative manner, during defrost operation, air conditioning controller with function stops the running of compressor 11.If compressor 11 operate at defrost operation during stop, then indoor condenser 12 can not add hot-air.Therefore, controller may blow the air with the temperature lower than the temperature of the passenger's expectation in vehicle.Once defrost operation, passenger may feel dissatisfied to heating.
On the contrary, in the present embodiment, even if when not adding hot-air by indoor condenser 12 in defrost operation, vehicle interior coordinated signals can also be performed to suppress the loss to the heating of passenger.The flow chart shown in Figure 14-17 is below used to describe coordinated signals.
Figure 14 is the flow chart of the basic control flow of display vehicle interior coordinated signals.Basic control flow is performed as the subprogram of the interrupt procedure of the main program performed by vehicle air conditioner 1.When representing that the defrosting mark deffg performing defrost operation does not become 1 within the scheduled time of time of implementation being appointed as basic control flow, operation turns back to main program.
In the step S100 of basic control flow, perform defrosting deterministic process to determine whether frost is formed in outdoor heat converter 16 place and whether performs defrosting.Figure 15 is below used to describe the details of defrosting deterministic process.In the step S101 of Figure 15, defrosting mark deffg etc. is initialised.
Subsequently, in step s 102, determine whether frost is formed in outdoor heat converter 16 place.Particularly, when the temperature of the outer surface of heat exchanger 16 is determined to be equivalent to or is less than 0 DEG C, determine that frost is formed, then operation proceeds to step S103, and deffg remains 1 (deffg=1).On the contrary, when the temperature of the outer surface of outdoor heat converter 16 is confirmed as being not equal to or being less than 0 DEG C, determine not form frost, then, operation turns back to step S102 again, and deffg remains zero (deffg=0).
In step s 103, determine whether engine operates.When determining engine running in step s 103, deffg remains 1 (deffg=1), and operation proceeds to step S104.When determining that engine does not operate, the air conditioning mode shown in step S200 that operation proceeds to Figure 14 changes control.
In step S104, be similar to step S102, determine whether frost is formed in outdoor heat converter place.Particularly, when the temperature of the outer surface of outdoor heat converter 16 is determined to be equivalent to or is less than 0 DEG C, determine that frost is formed, then operation proceeds to step S105, and deffg remains 1 (deffg=1).When the temperature of the outer surface of outdoor heat converter 16 is confirmed as being not equal to or being less than 0 DEG C, determines not form frost, then operate and again turn back to step S102.
In step S105, determine whether coolant temperature Tw reaches predetermined defrosting reference temperature KTwdef.In step S105, when coolant temperature Tw is confirmed as reaching predetermined defrosting reference temperature KTwdef (in the present embodiment, 10 DEG C) time, can defrost to outdoor heat converter 16 by making cooling agent flow in radiator 43, then operation proceeds to step S106, and deffg remains 1 (deffg=1).
In step S105, when coolant temperature Tw is confirmed as not reaching predetermined defrosting reference temperature KTwdef, even if cooling agent flow in radiator 43, outdoor heat converter 16 can not be defrosted, and then operates and again turns back to step S102.
In step s 106, determine whether Inside Air Temperature (temperature of the vehicle interior) Tr detected by inner air sensor is equal to or greater than predetermined reference Inside Air Temperature KTr (in the present embodiment, 15 DEG C).In step s 106, when Inside Air Temperature Tr is determined to be equal to or greater than with reference to Inside Air Temperature KTr, the temperature of vehicle interior is enough hot to make general passenger can not feel cold and dissatisfied (hereinafter referred to as " preheat mode "), and then operation proceeds to step S107 and deffg remains 1 (deffg=1).
In step s 106, when Inside Air Temperature Tr is confirmed as being not equal to or greater than with reference to Inside Air Temperature KTr, Inside Air Temperature Tr is until preheat mode just can increase.In order to make the heating priority of vehicle interior in defrost operation, operation turns back to step S102 again.
In step s 107, whether the car speed during determining to advance is equal to or less than predetermined reference car speed (in the present embodiment, 20km/h).In step s 107, when car speed is determined to be equivalent to or be less than predetermined reference car speed, be similar to the first embodiment, effectively can perform defrosting together with the reduction of ram-air pressure.Then, the air conditioning mode shown in step S200 that operation proceeds to Figure 14 changes control, and deffg remains 1 (deffg=1).
As found out from the above description, the rate-determining steps S100 of the present embodiment is as the control part of the frosting determination portion of the frosting had for determining outdoor heat converter 16.More specifically, rate-determining steps S102 and S104 is used as frosting determination portion.
Then, below use Figure 16 to describe the air conditioning mode that will perform in step s 200 and change control.When determining that defrosting mark deffg is 1 by defrosting deterministic process in the step s 100, performing air conditioning mode change and controlling.
In step s 201, first, determine the control signal of the motor outputting to compressor 11, make compressor 11 can not show discharge refrigerant ability, that is, make compressor 11 stop.In following steps S202, determine the control signal that will output to air blast 32, make the blowability of air blast 32 reduce reservation capability value from existing ability.
In following steps S203, suction ports pattern is set to inner air pattern.That is, compared with the state before being converted to defrost operation, the introducing of inner air and extraneous air is than increasing.In step S204, air outlet slit pattern is set to foot's pattern.That is, the switching be switched to for the main pattern from foot's air outlet slit blow air is performed.Then, operate the defrosting shown in step S300 proceeding to Figure 14 and start control.
Below use Figure 17 to be described in the defrosting performed in step S300 and start control.In step S301, first, as described in the first embodiment, the triple valve 42 of coolant circulation circuit 40 is switched, and cooling agent is flow in radiator 43.Further, the cooling agent of cooling medium pump 41 extrudes ability and is maximized, and timer activated, and then operation proceeds to step S302.
In step s 302, whether the car speed during determining to advance is equal to or less than predetermined reference car speed (in the present embodiment, 20km/h).When determining that car speed is equal to or less than with reference to car speed in step s 302, can obtain effective defrosting, then operation proceeds to step S303.When car speed is determined to be not equal to or be less than with reference to car speed, can not perform effective defrosting, then operation proceeds to step S304.
In step S303, whether the elapsed time being used in the timer determination defrost operation activated in step S301 exceedes predetermined reference defrosting time.When determining that the elapsed time of defrost operation exceedes with reference to defrosting time, operation proceeds to step S304.In step s 304, now, triple valve 42 is switched and cooling agent is flow in bypass passageways 44.
Then, the cooling agent of cooling medium pump 41 extrudes ability and is changed to become the extrusion ability identical with the extrusion ability started before defrost operation, and timer is reset.After this, operate the air conditioning mode shown in step S400 proceeding to Figure 14 and return control.Air conditioning mode in step S400 returns in control, and the ability that blows, the suction ports pattern of air blast 32 are returned to the level identical with the level before defrost operation with air outlet slit pattern.Then, operation proceeds to step S500.
In step S500, determine whether the stopping of asking Vehicular system.When not requiring stop vehicle system, operation proceeds to step S100.When requiring stop vehicle system, control procedure stops.The structure of the structure of other parts of the present embodiment and operation and other parts of the first embodiment with operate identical.
Therefore, the present embodiment can obtain the effect identical with the effect of the first embodiment.In addition, in the present embodiment, even if when air conditioning controller with function stops the operation of compressor 11, and when indoor condenser 12 can not show heating efficiency during defrost operation, above vehicle interior coordinated signals also can be performed and feels dissatisfied to prevent passenger to heating.
That is, in the present embodiment, as described in rate-determining steps S106, after acquisition preheat mode, perform defrost operation, thus can prevent passenger from feeling dissatisfied to heating.As described in rate-determining steps S203, during defrost operation, suction ports pattern is changed to inner air pattern.The inner air with the temperature higher than extraneous air is recycled and blows, thus can also prevent passenger from feeling dissatisfied to heating.
As described in rate-determining steps S202, the ability that blows of air blast 32 reduces in defrost operation, even if thus when the temperature being blown into the air in compartment reduces, also can prevent passenger from feeling dissatisfied to heating.Now, as described in rate-determining steps S204, air outlet slit pattern is set to step pattern, thus compared with the situation being blown to the face of passenger with air, can effectively prevent passenger from feeling dissatisfied to heating.
As found out from above explanation, the present embodiment can be counted as example heat pump cycle 10 being applied to vehicle air conditioner 1.
That is, the present embodiment comprises a kind of heat pump cycle on the one hand, and described heat pump cycle has: for compressing the compressor with refrigerant emission; User side heat exchanger (indoor condenser 12), at heat-shift between the cold-producing medium and the air being blown into vehicle interior of compressor discharge; Decompressor (the fixed restriction device 13 of heating), for reducing pressure to the cold-producing medium flowed out from user side heat exchanger; Outdoor heat converter, for allowing to be depressurized the cold-producing medium of device decompression and extraneous air heat-shift to evaporate described cold-producing medium; Heat dissipation heat exchanger (radiator 43), described heat dissipation heat exchanger is arranged on for making cooling produce in operation in the cooling fluid closed circuit of cooling fluid circulation of the car-mounted device (the motor MG for advancing) of heat, and to be suitable between cooling fluid and extraneous air heat-shift to distribute the heat from cooling fluid; Cooling fluid circuit, flow in heat dissipation heat exchanger (43) for making cooling fluid, and cooling fluid circuit switching device shifter (42), for performing the switching being switched to and allowing cooling fluid to walk around another cooling fluid circuit of heat dissipation heat exchanger (43).The present embodiment also comprises: for detecting the Inside Air Temperature test section of the Inside Air Temperature in vehicle interior; With the frosting determination portion of the frosting for determining outdoor heat converter place.Outdoor heat converter comprises the refrigerant pipe for making the flow of refrigerant being depressurized device decompression.Formed around refrigerant pipe for making the heat-absorption air passage of flow of external air.Heat dissipation heat exchanger comprises the cooling fluid pipe for making cooling fluid flow.Formed around the pipe for cooling fluid for making the heat radiation air duct of flow of external air.Be provided with outer fin for the air duct that absorbs heat and the air duct for dispelling the heat, described outer fin can realize the heat trnasfer between refrigerant pipe and cooling fluid pipe, promotes the heat exchange between two heat exchangers simultaneously.When determining that frost is formed in outdoor heat converter place by frosting determination portion, and when the Inside Air Temperature Tr of vehicle interior is equal to or greater than predetermined reference Inside Air Temperature KTr, then cooling fluid circuit switching device shifter can perform and be switched to for making cooling fluid flow to the switching of the cooling fluid circuit of heat dissipation heat exchanger.
The present embodiment comprise on the other hand above heat pump cycle, for determine the frosting of outdoor heat converter frosting determination portion and for holding user side heat exchanger and the housing for the formation of air duct wherein.Inner/outer air switching device shifter (inner/outer air switch 33) is arranged in the housing to change the introducing ratio that will be introduced in the inner air in housing and extraneous air.When being determined by frosting determination portion to form frost in outdoor heat converter, cooling fluid circuit switching device shifter performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit of heat dissipation heat exchanger.When being determined by frosting determination portion to form frost in outdoor heat converter, compared with before being transformed into defrost operation, inner/outer air switching device shifter can increase the introducing ratio of inner air and extraneous air.
The present embodiment comprise on the other hand above heat pump cycle, for determine the frosting of outdoor heat converter frosting determination portion and for holding user side heat exchanger and the housing for the formation of air duct wherein.Air outlet slit mode-changeover device is arranged in the housing to be used for blow air to switch in air outlet slit pattern to the opening/closing state of the multiple air outlet slits in vehicle interior by changing.As air outlet slit, foot's air outlet slit is arranged for and is at least blowed towards the foot of passenger by air.When being determined by frosting determination portion to form frost at outdoor heat converter place, cooling fluid circuit switching device shifter performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit of heat dissipation heat exchanger.When being determined by frosting determination portion to form frost at outdoor heat converter place, air outlet slit mode-changeover device can perform the switching be switched to for the air outlet slit pattern from foot's air outlet slit blow air.
The present embodiment comprise on the other hand above heat pump cycle, for determine the frosting at outdoor heat converter place frosting determination portion, for hold wherein user side heat exchanger and for the formation of air duct housing and arrange in the housing with the blowing device (such as, air blast 32) towards vehicle interior blow air.When being determined by frosting determination portion to form frost at outdoor heat converter place, cooling fluid circuit switching device shifter performs the switching be switched to for making cooling fluid flow into the cooling fluid circuit in heat dissipation heat exchanger.When being determined by frosting determination portion to form frost at external heat exchanger place, compared with before determining with frosting, blowing plant can reduce it and blow ability.
The another aspect of the present embodiment comprises above heat pump cycle and the frosting determination portion for the frosting of determining outdoor heat converter.When the car speed of traveling vehicle is equal to or less than predetermined reference car speed, and when the refrigerant temperature of the outlet side of outdoor heat converter is equal to or less than 0 DEG C, determine that frost is formed in outdoor heat converter place.When determining that frost is formed in outdoor heat converter place by frosting determination portion, cooling fluid circuit switching device shifter can perform and be switched to for making cooling fluid flow to the switching of the cooling fluid circuit of heat dissipation heat exchanger.
8th embodiment
Although above first and the 7th in embodiment, in an illustrative manner, compressor 11 operate at defrost operation during be stopped, but in the present embodiment shown in Figure 18, the loop structure of heat pump cycle 10 is changed the heating realizing vehicle interior, performs the defrost operation being similar to the 3rd embodiment provided in an illustrative manner simultaneously.Figure 18 is the overall structure schematic diagram of heat pump cycle 10 during defrost operation in the present embodiment corresponding with Fig. 2 of the first embodiment.
Particularly, the difference of the present embodiment and the first embodiment is: adopt the variable throttling device thereof 83 for heating, and described variable throttling device thereof 83 can change the opening degree of the throttling arrangement for heating operation as decompressor.The electric actuator of the throttling opening degree for changing valve body that variable throttling device thereof 83 for heating comprises the variable valve body of throttling opening degree and is made up of stepper motor.The operation of variable throttling device thereof 83 is controlled by the control signal exported from air conditioning controller with function.
In the present embodiment, air conditioning controller with function is collected in operation at heating operation and used heat and the valve opening degree of the variable throttling device thereof 83 being used for heating is controlled to prodefined opening degree, and to operate with used heat collection with heating operation and compare, in defrost operation, increase the valve opening degree of the variable flow device 83 for heating.Therefore, compared with before defrost operation, in defrost operation, the high-pressure refrigerant with higher temperature discharged from compressor 11 is easy to flow into outdoor heat converter 16.
The structure of the structure of other parts of the present embodiment and operation and other parts of the first embodiment with operate identical.Therefore, in the vehicle air conditioner 1 of the present embodiment, throttling opening degree for the variable throttling device thereof 83 heated increases in defrost operation, and the high-pressure refrigerant under high temperature can be flow in outdoor heat converter 16, thus promotes the defrosting of outdoor heat converter 16.Further, during defrost operation, the heating efficiency for the indoor condenser 12 adding hot-air can be shown to perform the heating to vehicle interior.
When from the flow direction of extraneous air, be similar to the 3rd embodiment, position relationship between the heat exchange area of the heat exchange area of the refrigerant inlet side of outdoor heat converter 16 and the refrigerant outlet side of outdoor heat converter 16 does not change relative to the heat exchanger section of radiator 43, thus can suppress the larger fluctuation of the amount of the heat trnasfer flowed through between the cold-producing medium of refrigerant pipe 16a and the cooling fluid flowing through cooling fluid pipe 43a.
9th embodiment
As shown in the overall structure schematic diagram of Figure 19, in the present embodiment, the loop structure of heat pump cycle 10 is changed the heating realizing vehicle interior, performs the defrost operation being similar to the 8th embodiment provided in an illustrative manner simultaneously.Figure 19 is the overall structure schematic diagram of the heat pump cycle 10 in defrost operation according to the present embodiment corresponding with Fig. 2 of the first embodiment.
Particularly, the difference of the present embodiment and the first embodiment is to increase and flows out flow control valve 84 with the outflow flow of the cold-producing medium regulating heat exchanger 16 outdoor and flow out.Flow out flow control valve 84 and there is the basic structure identical for the basic structure of the variable throttling device thereof 83 heated with the 8th embodiment, and therefore form one with the refrigerant outlet of outdoor heat converter 16.
In the present embodiment, air conditioning controller with function collects at heating operation, used heat the valve opening degree opened completely in operation and cooling down operation and flow out flow control valve 84, and collect to operate with heating operation, used heat and compare with cooling down operation, in defrost operation, reduce the valve opening degree flowing out flow control valve 84.Therefore, in defrost operation, compared with before being transformed into defrost operation, the inflow flow flowing into the cold-producing medium in outdoor heat converter 16 reduces.The structure of the structure of other parts of the present embodiment and operation and other parts of the first embodiment with operate identical.
In the vehicle air conditioner 1 of the present embodiment, the valve opening degree flowing out flow control valve 84 is reduced in defrost operation, make it possible to the inflow flow reducing to flow into the cold-producing medium in outdoor heat converter 16, thus the effect identical with the effect of the 8th embodiment can be provided.
Construct integratedly with the refrigerant outlet of outdoor heat converter 16 owing to flowing out flow control valve 84, therefore can reduce the volume from the discharge port of compressor 11 to the coolant channel of the entrance side of outflow flow control valve 84, thus reduce the flow of the cold-producing medium flow in outdoor heat converter 16 fast.
Tenth embodiment and the 11 embodiment
In above 3rd, the 8th and the 9th embodiment, in an illustrative manner, outdoor heat converter 16 shows heating efficiency to realize the heating to vehicle interior, does not stop the running of compressor 11 in defrost operation simultaneously.In the 9th embodiment, as shown in figure 20, in the housing 31 of ptc heater 85 air-conditioning unit 30 disposed in the interior, and be used as the heating element heater being produced heat by supply electric power.
The downstream of the air stream of ptc heater 85 condenser 12 disposed in the interior, and by producing heat from air conditioning controller with function supply electric power in defrost operation.Therefore, even if when air conditioning controller with function stops the running of compressor 11 during defrost operation, ptc heater 85 also can be used as the auxiliary heater adding hot-air, thus realizes the heating to vehicle interior.
In the 11 embodiment, as shown in figure 21, heater core 86 is configured to for as adding heat-shift between the engine coolant of hot fluid and air.Heater core 86 has the basic structure identical with the basic structure of the heater core 63 of the second embodiment.The downstream of the air stream of heater core 86 condenser 12 disposed in the interior enters wherein to allow flow of engine coolant during defrost operation.
Therefore, even if work as air conditioning controller with function during defrost operation to stop the operation of compressor 11, heater core 86 also can be used as the auxiliary heater adding hot-air, thus realizes the heating to vehicle interior.Be used as the hot fluid that adds adding the thermal source of hot-air at heater core 86 place and be not limited to engine coolant, but can be the cooling agent etc. for cooling the car-mounted device (such as, for the motor MG that advances or transverter) producing in operation heat.
Alternatively, ptc heater the 85 and the 11 embodiment of the tenth embodiment heater core 86 can condenser 12 disposed in the interior air stream downstream be used as auxiliary heater.Figure 20 and Figure 21 is respectively according to the overall structure figure of the heat pump cycle in defrost operation 10 of the 9th embodiment and the 11 embodiment, and corresponds to Fig. 2 of the first embodiment.
(other embodiment)
The present invention is not limited to above-described embodiment, but can carry out various amendment and change to above embodiment as follows when not deviating from protection scope of the present invention.
(1) in the embodiment above, in an illustrative manner, the car-mounted device (external heat source) of generation heat is the motor MG for advancing in operation, but external heat source is not limited to this.Such as, when heat pump cycle 10 is applied to vehicle air conditioner 1, engine or the electric device for the such as transverter supplying power to the motor MG for advancing can be used as external heat source.
At use engine as in external heat source, not only contained in engine coolant heat, and also in engine exhaust, contained heat may be used to defrost.Further, when heat pump cycle 10 being applied to still air adjuster, freezer, the cooling being used for automatic vending machine etc. and heater etc., other electric device of drive source of engine, motor and the compressor that is used as heat pump cycle 10 can be used as external heat source.
(2) in the embodiment above, adopt electric T-shaped valve 42 as carrying out the loop switch device switched in the cooling fluid circuit of coolant circulation circuit 40, but loop switch device is not limited to this.Such as, thermostatic valve can be used.Thermostatic valve is the cooling fluid temperature responsive valve be made up of mechanical mechanism, and described mechanical mechanism makes valve body displacement open and close cooling channels by using the temperature variant hot wax (heat sensitive member) of volume.Therefore, the use of thermostatic valve can also remove coolant temperature sensor 52.
(3) in the embodiment above, the refrigerant pipe 16a of outdoor heat converter 16, the cooling fluid pipe 43a of radiator 43 and outer fin 50 are formed by aluminium alloy (metal) and pass through together with soldered joint.Apparently, outer fin 50 can be formed by other material (such as, CNT etc.) with fabulous thermal conductivity, and these elements can be bonded together with other engagement device of such as adhesive.
(4) in the embodiment above, in normal heating operation, perform the switching be switched to for allowing cooling agent to walk around the cooling fluid circuit of radiator 43, thus the heat distributed from the motor MG being used for advancing is stored in cooling agent.Alternatively, or in addition, heat storage housing (heat storage device) for holding the heat storage medium of such as paraffin can be arranged in coolant circulation circuit 40, and the heat distributed from the motor MG for advancing in normal heating operation by this can be stored in heat storage housing.
Alternatively or in addition, the heating element heater (such as, ptc heater) being produced heat by supply electric power can be arranged in coolant circulation circuit 40, and the heat distributed from heating element heater in normal heating operation can be stored in cooling agent.Alternatively, from car-mounted device with produce at least one in the heating element heater of heat heat of distributing can be stored in cooling agent the operation of the motor MG for advancing etc.Now, the heat produced in heating element heater controls to increase with the reduction with external air temperature with being supposed to, thus avoids unnecessary power consumption.
(5) in above first embodiment, in an illustrative manner, when car speed is equal to or less than predetermined reference car speed (in the present embodiment, 20km/h) and the refrigerant temperature Te of the outlet side of outdoor heat converter 16 is equal to or less than 0 DEG C time, frosting determination portion is used for determining whether frost is formed in outdoor heat converter 16 place.But, for frosting really fixed condition be not limited to this.
Such as, the temperature detecting part of the temperature of the outer fin 50 for sensing chamber's outer heat-exchanger 16 can be set, and when the temperature detected by temperature detecting part is equal to or less than predetermined frosting reference temperature (such as ,-5 DEG C), can determine that frost is formed.
(6) in the embodiment above, in an illustrative manner, for the device of the running of the fan 17 that turns off the blast in defrost operation for reducing to flow into the volume of the extraneous air in heat-absorption air passage 16b and heat radiation air duct 43b.No matter be normal operating and defrost operation, when compressor 11 stops, the ability that blows of blower fan 17 can increase, until pass by the scheduled time.Therefore, when compressor 11 stops, the ability that blows of blower fan 17 can increase, and makes the temperature of outdoor heat converter 16 can rapidly increase to the level identical with external air temperature.
(7) more than, the structure described in each embodiment can be applied to other embodiment.Such as, in the vehicle chamber described in the 7th embodiment, coordinated signals can perform in the vehicle air conditioner of application second to the 5th and the 8th to the 11 heat pump cycle 10 of each in embodiment.
Such as, when the vehicle interior coordinated signals of the 7th embodiment is applied to the heat pump cycle 10 of the 3rd embodiment, air conditioning controller with function can change in control at air conditioning mode in rate-determining steps S200 when not stopping the running of compressor 11 opens open/closed valve 15c.When being applied to the 4th embodiment, open/closed valve 15a and open/closed valve 15c can change control by air conditioning mode and open in rate-determining steps S200.
Similarly, when being applied to the 8th embodiment, the valve opening degree for the variable throttling device thereof 83 heated can be reduced in rate-determining steps S200 in air conditioning mode change controls.When being applied to the 9th embodiment, the valve opening degree flowing out flow control valve 84 can be reduced in rate-determining steps S200 in air conditioning mode change controls.
(8) although in the embodiment above in an illustrative manner using common fluorine-based cold-producing medium as cold-producing medium, cold-producing medium is not limited to this.The natural refrigerant and hydrocarbon refrigerant etc. of such as carbon dioxide can be used.Further, heat pump cycle 10 can form the supercritical refrigeration cycle being equal to or higher than the critical pressure of cold-producing medium from the pressure of the cold-producing medium of compressor 11 discharge.

Claims (25)

1. a heat pump cycle, comprising:
The compressor (11) of compression and refrigerant emission;
User side heat exchanger (12), described user side heat exchanger is heat-shift between heat-exchange fluid and the cold-producing medium discharged from described compressor (11);
Decompressor (13,83), described decompressor reduces pressure to the cold-producing medium flowed out from described user side heat exchanger (12);
Outdoor heat converter (16), described outdoor heat converter makes by described decompressor (13,83) cold-producing medium reduced pressure and extraneous air heat-shift are to evaporate described cold-producing medium, and described heat pump cycle is suitable for performing the defrost operation being used for defrosting to described outdoor heat converter (16) when outdoor heat converter (16) frosting;
Indoor evaporator (20), for allowing the cold-producing medium in the downstream of described outdoor heat converter (16) and heat-exchange fluid heat-shift and evaporating described cold-producing medium;
Refrigerant flowpath switching device shifter, described refrigerant flowpath switching device shifter is configured to switch heating operation refrigerant flowpath and cooling down operation refrigerant flowpath, in heating operation refrigerant flowpath, the cold-producing medium discharged from described compressor (11) flow into described user side heat exchanger (12) with heat hot replacement fluids, in cooling down operation refrigerant flowpath, flow in described indoor evaporator (20) at the cold-producing medium of described outdoor heat converter (16) place distribute heat with heat of cooling replacement fluids;
Heat dissipation heat exchanger (43), described heat dissipation heat exchanger is arranged in cooling fluid closed circuit (40), described cooling fluid closed circuit (40) is circulated for making the cooling fluid of cooling external heat source (MG), and described heat dissipation heat exchanger (43) is suitable for heat-shift between described cooling fluid and extraneous air; With
Cooling fluid circuit switching device shifter (42), described cooling fluid circuit switching device shifter be formed at for allow cooling fluid flow into cooling fluid circuit in heat dissipation heat exchanger (43) and for allow described cooling fluid to walk around described heat dissipation heat exchanger (43) cooling fluid circuit between switch, wherein:
Described outdoor heat converter (16) comprises refrigerant pipe (16a), is flowed in described refrigerant pipe by the cold-producing medium that described decompressor (13,83) reduces pressure;
Formed around described refrigerant pipe (16a) for making the heat-absorption air passage (16b) of described flow of external air;
Described heat dissipation heat exchanger (43) comprises cooling fluid pipe (43a), and described cooling fluid flows in described cooling fluid pipe;
Formed around described cooling fluid pipe (43a) for making the heat radiation air duct (43b) of described flow of external air;
Described heat-absorption air passage (16b) and described heat radiation air duct (43b) are provided with outer fin (50), described outer fin can realize the heat trnasfer between described refrigerant pipe (16a) and described cooling fluid pipe (43a), promotes the heat exchange in described outdoor heat converter (16) and described heat dissipation heat exchanger (43) simultaneously;
Described cooling fluid circuit switching device shifter (42) at least performs the switching be switched to for making cooling fluid flow into the cooling fluid circuit in described heat dissipation heat exchanger (43) in defrost operation;
The flow direction flowing through the cold-producing medium of described refrigerant pipe (16a) in heating operation is identical with the flow direction of the cold-producing medium flowing through described refrigerant pipe (16a) in cooling down operation;
The heat exchange area of the refrigerant inlet side of described outdoor heat converter (16) is overlapping with the heat exchange area of the cooling fluid inlet side of described heat dissipation heat exchanger (43) on outside airflow direction;
Described outdoor heat converter (16) is constructed such that: in cooling down operation, the flow of refrigerant of relatively-high temperature is by the heat exchange area of the refrigerant inlet side of described outdoor heat converter (16), and in heating operation the flow of refrigerant of relative low temperature by the heat exchange area of the refrigerant inlet side of described outdoor heat converter (16); And
Described heat dissipation heat exchanger (43) is constructed such that: in cooling down operation and heating operation, and the cooling fluid of relatively-high temperature flows by the heat exchange area of the refrigerant inlet side of described heat dissipation heat exchanger (43).
2. heat pump cycle according to claim 1, wherein, in defrost operation, compared with before being transformed into defrost operation, the inflow flow flowing into the cold-producing medium in described outdoor heat converter (16) reduces.
3. heat pump cycle according to claim 1, wherein:
Described decompressor (83) is variable restriction mechanism, and in described variable restriction mechanism, throttling opening degree is variable; And
Compared with before being transformed into defrost operation, described decompressor (83) increases throttling opening degree in defrost operation.
4. heat pump cycle according to claim 1, also comprises:
Flow out flow control valve (84), described outflow flow control valve is configured to the outflow flow regulating the cold-producing medium flowed out from described outdoor heat converter (16),
Wherein compared with before being transformed into defrost operation, described outflow flow control valve (84) reduces the outflow flow of described cold-producing medium in defrost operation.
5. heat pump cycle according to claim 4, wherein, described outflow flow control valve (84) be configured to the cold-producing medium for described outdoor heat converter (16) go out interruption-forming one.
6. heat pump cycle according to claim 1, also comprises:
Outdoor blowers (17), described outdoor blowers blows extraneous air towards described outdoor heat converter (16) and heat dissipation heat exchanger (43),
Wherein compared with before the described compressor of stopping (11), when described compressor (11) stops, described outdoor blowers (17) increases blowability.
7. heat pump cycle according to claim 1, wherein, in defrost operation, compared with before being transformed into defrost operation, the heating efficiency for user side heat exchanger (12) of heat hot replacement fluids reduces.
8. heat pump cycle according to claim 1, wherein, described heat-absorption air passage (16b) and described heat radiation air duct (43b) are constructed such that the volume of the extraneous air flow in described heat-absorption air passage (16b) and described heat radiation air duct (43b) reduces in defrost operation.
9. heat pump cycle according to claim 1, also comprises:
Outdoor blowers (17), described outdoor blowers blows extraneous air towards described outdoor heat converter (16) and described heat dissipation heat exchanger (43),
Wherein said heat dissipation heat exchanger (43) is positioned at the windward side of the flow direction (X) of the extraneous air blowed by described outdoor blowers (17) relative to described outdoor heat converter (16).
10. the heat pump cycle according to any one of claim 1-9, wherein:
At least one in described refrigerant pipe (16a) is positioned between described cooling fluid pipe (43a);
At least one in described cooling fluid pipe (43a) is positioned between described refrigerant pipe (16a); And
At least one in described heat-absorption air passage (16b) and described heat radiation air duct (43b) is formed as an air duct.
11. heat pump cycles according to any one of claim 1-9, described heat pump cycle is applied to vehicle air conditioning, and described heat pump cycle also comprises:
Inside Air Temperature test section, described Inside Air Temperature test section is configured to the Inside Air Temperature detecting vehicle interior; With
Frosting determination portion, described frosting determination portion is configured to the frosting determining described outdoor heat converter (16), wherein:
Described heat-exchange fluid is the air being blown into described vehicle interior;
Described external heat source is the car-mounted device (MG) producing heat in operation;
Described cooling fluid is the cooling agent for cooling described car-mounted device (MG); And
When being determined by described frosting determination portion that frost is formed in described outdoor heat converter (16) place and the Inside Air Temperature of vehicle interior (Tr) is equal to or greater than predetermined reference Inside Air Temperature (KTr), the switching that the execution of described cooling fluid circuit switching device shifter (42) is switched to for making cooling fluid flow into the cooling fluid circuit in described heat dissipation heat exchanger (43).
12. heat pump cycles according to any one of claim 1-9, described heat pump cycle is applied to vehicle air conditioning, and described heat pump cycle also comprises:
For determining the frosting determination portion of the frosting of outdoor heat converter (16), wherein
Described heat-exchange fluid is the air being blown into described vehicle interior;
Described external heat source is the car-mounted device (MG) producing heat in operation;
Described cooling fluid is the cooling agent for cooling described car-mounted device (MG);
Described user side heat exchanger (12) is arranged in housing (31), forms air duct in described housing;
Will be introduced in the inner air in described housing (31) for change is arranged in housing (31) with the inner/outer air switching device shifter (33) of the introducing ratio of extraneous air, wherein:
When determining that frost is formed in described outdoor heat converter (16) place by described frosting determination portion, the execution of described cooling fluid circuit switching device shifter (42) is switched to for making cooling fluid flow to the switching of the cooling fluid circuit of described heat dissipation heat exchanger (43); And
When determining that frost is formed in described outdoor heat converter (16) place by described frosting determination portion, compared with before being transformed into defrost operation, described inner/outer air switching device shifter (33) increases the introducing ratio of inner air and extraneous air.
13. heat pump cycles according to any one of claim 1-9, described heat pump cycle is applied to vehicle air conditioning, and described heat pump cycle also comprises:
Be configured to the frosting determination portion of the frosting determining described outdoor heat converter (16), wherein:
Described heat-exchange fluid is the air being blown into described vehicle interior;
Described external heat source is the car-mounted device (MG) producing heat in operation;
Described cooling fluid is the cooling agent for cooling described car-mounted device (MG);
Described user side heat exchanger (12) is arranged in housing (31), forms air duct in described housing;
For being used for the air outlet slit mode-changeover device (37a-37c) that blow air carries out switching to the opening/closing state of the air outlet slit of described vehicle interior in air outlet slit pattern to be arranged in described housing (31) by changing;
At least foot's air outlet slit is set to air outlet slit, and described foot air outlet slit is used for the foot of blow air to passenger;
When determining that frost is formed in described outdoor heat converter (16) place by described frosting determination portion, cooling fluid circuit switching device shifter (42) performs and is switched to for making cooling fluid flow to the switching of the cooling fluid circuit in described heat dissipation heat exchanger (43); And
When determining that frost is formed in described outdoor heat converter (16) place by described frosting determination portion, the switching that the execution of described air outlet slit mode-changeover device (37a-37c) is switched to for the air outlet slit pattern from described foot air outlet slit blow air.
14. heat pump cycles according to any one of claim 1-9, described heat pump cycle is applied to vehicle air conditioning, and described heat pump cycle also comprises:
Be configured to the frosting determination portion of the frosting determining described outdoor heat converter (16), wherein:
Heat-exchange fluid is the air being blown into described vehicle interior;
Described external heat source is the car-mounted device (MG) producing heat in operation;
Described cooling fluid is the cooling agent for cooling described car-mounted device (MG);
Described user side heat exchanger (12) is arranged in housing (31), forms air duct in described housing;
Air blast (32) for being blowed towards described vehicle interior by air is arranged in described housing (31);
When determining that frost is formed in described outdoor heat converter (16) place by described frosting determination portion, the switching that the execution of described cooling fluid circuit switching device shifter (42) is switched to for making cooling fluid flow into the cooling fluid circuit in described heat dissipation heat exchanger (43); And
Compared with before determining frosting, described air blast (32) reduces blowability.
15. heat pump cycles according to any one of claim 1-9, described heat pump cycle is applied to vehicle air conditioning, and described heat pump cycle also comprises:
For determining the frosting determination portion of the frosting of described outdoor heat converter (16), wherein:
Heat-exchange fluid is the air being blown into described vehicle interior;
Described external heat source is the car-mounted device (MG) producing heat in operation;
Described cooling fluid is the cooling agent for cooling described car-mounted device (MG);
When car speed is equal to or less than predetermined reference speed, and when the temperature of the cold-producing medium of the outlet side of described outdoor heat converter (16) is equal to or less than 0 DEG C, described frosting determination portion determines that frost is formed in described outdoor heat converter (16) place; And
When determining that frost is formed in described outdoor heat converter (16) place by described frosting determination portion, the execution of described cooling fluid circuit switching device shifter (42) is switched to for making cooling fluid flow to the switching of the cooling fluid circuit in described heat dissipation heat exchanger (43).
16. heat pump cycles according to claim 15, wherein, when the speed of traveling vehicle is equal to or less than predetermined reference speed, and when the temperature of the cold-producing medium of the outlet side of described outdoor heat converter (16) is equal to or less than 0 DEG C, described frosting determination portion determines that frost is formed in described outdoor heat converter (16) place.
17. heat pump cycles according to claim 11, also comprise:
Be configured to the coolant temperature test section (52) that detection flow into the temperature of the cooling agent in car-mounted device (MG), wherein:
When the coolant temperature (Tw) detected by described coolant temperature test section (52) is equal to or greater than described predetermined reference temperature, the switching that the execution of described cooling fluid circuit switching device shifter (42) is switched to for making cooling fluid flow into the cooling fluid circuit in described heat dissipation heat exchanger (43).
18. heat pump cycles according to any one of claim 1-9, wherein, when the execution of described cooling fluid circuit switching device shifter (42) is switched to for making cooling fluid walk around the switching of the cooling fluid circuit of described heat dissipation heat exchanger (43), described cooling fluid closed circuit (40) is stored in the heat comprised in described external heat source within it.
19. heat pump cycles according to claim 18, described heat pump cycle is applied to vehicle air conditioning, wherein:
Described heat-exchange fluid is the air being blown into described vehicle interior;
Described external heat source is the car-mounted device (MG) producing heat in operation;
Described cooling fluid is the cooling agent for cooling described car-mounted device (MG); And
When cooling fluid circuit switching device shifter (42) execution is switched to for making cooling fluid walk around the switching of the cooling fluid circuit of described heat dissipation heat exchanger (43), the heat distributed from described car-mounted device (MG) is stored in cooling agent by described cooling fluid closed circuit (40).
20. heat pump cycles according to claim 18, described heat pump cycle is applied to vehicle air conditioning, wherein:
Described heat-exchange fluid is the air being blown into described vehicle interior;
Described external heat source is the heating element heater being produced heat by supply electric power;
Described cooling fluid is the cooling agent for cooling described heating element heater; And
When the execution of described cooling fluid circuit switching device shifter (42) is switched to for making cooling fluid walk around the switching of the cooling fluid circuit of described heat dissipation heat exchanger (43), the heat distributed from described heating element heater is stored in cooling agent by described cooling fluid closed circuit (40).
21. heat pump cycles according to claim 18, described heat pump cycle is applied to vehicle air conditioning, wherein:
Described heat-exchange fluid is the air being blown into described vehicle interior;
The car-mounted device (MG) of generation heat in operation and the heating element heater being produced heat by supply electric power are provided as external heat source;
Described cooling fluid is the cooling agent for cooling described heating element heater and described car-mounted device (MG); And
When the execution of described cooling fluid circuit switching device shifter (42) is switched to for allowing cooling fluid to walk around the switching of the cooling fluid circuit of described heat dissipation heat exchanger (43), described cooling fluid closed circuit (40) is stored in from least one heat distributed described car-mounted device (MG) and described heating element heater in cooling agent.
22. heat pump cycles according to claim 20 or 21, wherein, described heating element heater have from described heating element heater produce according to the controlled heat of external air temperature.
23. heat pump cycles according to any one of claim 1-9, also comprise:
Outdoor unit bypass passageways (64), described outdoor unit bypass passageways makes walked around described outdoor heat converter (16) by the cold-producing medium that described decompressor (13,83) reduces pressure and cold-producing medium be directed to the refrigerant outlet side of described outdoor heat converter (16); With
Outdoor unit bypass passageways switching device shifter (15c), described outdoor unit bypass passageways switching device shifter is formed at for will by described decompressor (13,83) refrigerant loop that the cold-producing medium reduced pressure is directed to described outdoor heat converter (16) with for will by described decompressor (13,83) switch between the refrigerant loop that the cold-producing medium reduced pressure guides towards described outdoor unit bypass passageways (64)
Wherein in defrost operation, the switching that the execution of described outdoor unit bypass passageways switching device shifter (15c) is switched to for the refrigerant loop will be directed to described outdoor unit bypass passageways (64) by the cold-producing medium that described decompressor (13,83) reduce pressure.
24. heat pump cycles according to any one of claim 1-9, also comprise:
Indoor evaporator (20), described indoor evaporator is heat-shift between the cold-producing medium in the downstream of heat-exchange fluid and described outdoor heat converter (16);
Evaporator bypass passage (20a), described evaporator bypass passage makes the cold-producing medium in the downstream of outdoor heat converter (16) walk around described indoor evaporator (20) and described cold-producing medium is directed to the refrigerant outlet of described indoor evaporator (20); With
Evaporator bypass channel switching device (15b), the described evaporator bypass channel switching device cold-producing medium be formed at for the downstream by described outdoor heat converter (16) is directed between the refrigerant loop of described indoor evaporator (20) and the refrigerant loop being directed to described evaporator bypass passage (20a) for the cold-producing medium in the downstream by described outdoor heat converter (16) and switches
Wherein in defrost operation, described evaporator bypass channel switching device (15b) the execution cold-producing medium be switched to for the downstream by described outdoor heat converter (16) is directed to the switching of the refrigerant loop of described indoor evaporator (20).
25. heat pump cycles according to any one of claim 1-9, described heat pump cycle is applied to vehicle air conditioning, wherein:
Described heat-exchange fluid is the air being blown into described vehicle interior;
Described user side heat exchanger (12) is arranged in housing (31), forms blast channel in described housing; And
Auxiliary heater is arranged in described housing (31), uses and is produced adding hot fluid and carrying out the air of heated blown to described vehicle interior by least one generation in the heating element heater (85) of heat of supply electric power as heating source of the car-mounted device heating of heat in operation.
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