CN103373193A - Air conditioning system of automobile - Google Patents
Air conditioning system of automobile Download PDFInfo
- Publication number
- CN103373193A CN103373193A CN2012101163863A CN201210116386A CN103373193A CN 103373193 A CN103373193 A CN 103373193A CN 2012101163863 A CN2012101163863 A CN 2012101163863A CN 201210116386 A CN201210116386 A CN 201210116386A CN 103373193 A CN103373193 A CN 103373193A
- Authority
- CN
- China
- Prior art keywords
- refrigerant
- heat exchanger
- intermediate heat
- exchanger
- pipeline
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Air-Conditioning For Vehicles (AREA)
Abstract
The invention discloses an air conditioning system of an automobile. The air conditioning system comprises a refrigerant circulating system and a coolant circulating system. The refrigerant circulating system can provide a cold source for the coolant circulating system and comprises a compressor, a vapor-liquid separator, an interior condenser, an exterior heat exchanger and an interior evaporator, the vapor-liquid separator is arranged in front of an air inlet of the compressor, and the interior condenser is connected with an outlet of the compressor; a second throttling element, a bypass flow path and an intermediate heat exchanger are arranged between the interior condenser and the exterior heat exchanger, and at least two throttling elements are respectively arranged in pipelines which run from the exterior heat exchanger to the interior evaporator and the intermediate heat exchanger respectively, so that refrigerants which are condensed by the exterior heat exchanger can be throttled by the throttling elements and then can flow to the interior evaporator and the intermediate heat exchanger when the refrigerant circulating system is in a refrigerating mode. The air conditioning system has the advantages that batteries can be cooled, heat can be absorbed from low-temperature heat sources in a heat pump manner and is used for heating, accordingly, the efficiency is improved, and power consumption is reduced.
Description
Technical field
The present invention relates to the automobile air conditioning technology field, particularly the automotive air-conditioning system of a kind of electric automobile air-conditioning system or hybrid power.
Background technology
Development along with low-carbon economy, energy-saving and emission-reduction have been proposed stricter requirement, countries in the world are all the strategic direction of new-energy automobile as automobile industry development, and electronlmobil or hybrid vehicle become from now on one of development of automobile aspect because energy-conserving and environment-protective are arranged.But electronlmobil is owing to use battery as power resources, and battery is as core component, and its cost and capacity/weight are restricting the development of new-energy automobile; Its a/c system equally also is different from original automotive air-conditioning system.Traditional internal combustion engine type automobile can utilize the waste heat of combustion engine and the heat of engine exhaust to come vehicle cabin, and the power of electronlmobil mainly comes from motor, and the heat that has lacked driving engine can utilize.In addition, in orthodox car, blowing engine and condensation motor be air conditioning for automobiles main use power supply, and on electronlmobil/hybrid vehicle electricity consumption be hybrid power not merely just, this contradiction will be more outstanding.At first, compressor does not have the driving of driving engine, relies on electric energy fully; Its two, same do not have the waste heat of driving engine to use when heating because there has not been driving engine, will rely on electric energy fully yet.So how to improve the degree of utilization of electric energy, become the subject matter of electronlmobil or hybrid power automobile air conditioner.
Summary of the invention
The technical problem to be solved in the present invention provides a kind of automotive air-conditioning system, adopt heat pump that the compartment is carried out temperature control, and also provide cold to cool off by automotive air-conditioning system to battery, it is available that the cooling of battery is had a various ways, system can be according to the mode of operation of ambient temperature and battery itself, select the most energy-conservation mode of operation, and then improve the efficiency of automotive air-conditioning system.For this reason, the present invention is by the following technical solutions:
A kind of automotive air-conditioning system is included as that passenger accommodation provides the refrigerant-cycle systems of low-temperature receiver and thermal source and according to the coolant circulation system of thermal load control battery temperature, refrigerant-cycle systems can be coolant circulation system low-temperature receiver is provided; Described refrigerant-cycle systems belongs to heat pump, comprises at least: refrigeration mode, heating mode; Described refrigerant-cycle systems comprises compressor, be positioned at the vapour liquid separator before the compressor inlet, the car inner condenser that is connected with the outlet of compressor, and the compartment external environment carry out compartment outer heat-exchanger, the car evaporator of interchange of heat; Be provided with the second section fluid element in the pipeline between described car inner condenser and the compartment outer heat-exchanger, the second section fluid element is provided with a bypass flow path; Refrigerant-cycle systems also comprises and can be the Intermediate Heat Exchanger that coolant circulation system provides low-temperature receiver; From leading to the pipeline of evaporator in the car, Intermediate Heat Exchanger, described compartment outer heat-exchanger is provided with at least one throttle unit, make refrigerant-cycle systems when refrigeration mode, after the throttle unit throttling, can lead to evaporator in the car, Intermediate Heat Exchanger through the refrigerant of compartment outer heat-exchanger condensation; Described coolant circulation system comprises: passive refrigerating mode, and the active cooling pattern, coolant circulation system absorbs cold to be used for the cooling to battery from described Intermediate Heat Exchanger when passive refrigerating mode.
Preferably, the pipeline after the described compartment outer heat-exchanger is divided into two streams: wherein the first loop directly is connected to described vapour liquid separator by pipeline, and second servo loop leads to evaporator and described Intermediate Heat Exchanger in the described car; The conducting when heating mode of the first loop, second servo loop conducting when refrigeration mode; Described refrigerant-cycle systems is provided with the break-make in triple valve or two these two loops of solenoid control.
Alternatively, described compartment outer heat-exchanger leads in the pipeline of evaporator in the described car, described Intermediate Heat Exchanger and respectively is provided with a throttle unit: described compartment outer heat-exchanger leads to the first throttle element of evaporator in the described car, the 3rd throttle unit that described compartment outer heat-exchanger leads to the refrigerant section of described Intermediate Heat Exchanger, when refrigeration mode, refrigerant is divided into two streams after condensing by described compartment outer heat-exchanger, and wherein the first stream flows to evaporator in the described car after the throttling of first throttle element; The second stream flows to the refrigerant section of described Intermediate Heat Exchanger after the 3rd throttle unit throttling.In this sample car evaporator and the temperature of the refrigerant section of Intermediate Heat Exchanger just distinguish controllable, with the needs of the energy-conservation and traveling comfort that satisfies system.
Alternatively, be respectively arranged with shutoff valve or electromagnetic valve or with the flow-controlling gate of cutoff function in described two streams.
Alternatively, described compartment outer heat-exchanger leads to and is provided with a throttle unit in the pipeline of evaporator in the described car, described Intermediate Heat Exchanger: main throttle unit, when refrigeration mode, refrigerant by the outer heat-exchanger condensation of described compartment after by second servo loop, by being divided into again two streams after the described main throttle unit throttling: flow to evaporator in the described car the first stream, flow to the second stream of the refrigerant section of described Intermediate Heat Exchanger.System unit is relatively less like this, can save manufacturing cost.
Alternatively, at least one stream is provided with the flow-controlling gate of cutoff function or is provided with shutoff valve and the combination of flow-controlling gate in described two streams.
Preferably, described refrigerant-cycle systems comprises the second Intermediate Heat Exchanger, the 4th throttle unit, the second Intermediate Heat Exchanger comprises first part and the second part, the second part of the second Intermediate Heat Exchanger is arranged in the outlet and the pipeline between described the 3rd throttle unit of described car inner condenser, first part one end of the second Intermediate Heat Exchanger connects the 4th throttle unit, and the other end is connected to the import of described vapour liquid separator by the pipeline valve member; The other end of described the 4th throttle unit is connected to the outlet of described car inner condenser by pipeline fitting; The first part of described the 4th throttle unit, the second Intermediate Heat Exchanger is series connection setting.By the second Intermediate Heat Exchanger is set, the operating range of this heat pump increases, and efficient improves, thereby has enlarged the range of use of electronlmobil.
Preferably, described the second Intermediate Heat Exchanger is the dual channel H Exch, is provided with shutoff valve or electromagnetic valve in the first part place pipeline of described the 4th throttle unit, the second Intermediate Heat Exchanger; When heating mode, shutoff valve or electromagnetic valve in the first part place pipeline of described the 4th throttle unit, the second Intermediate Heat Exchanger are opened, make the refrigerant behind the car inner condenser of flowing through to be split into two parts: the second part of first's refrigerant flow direction Intermediate Heat Exchanger, second portion refrigerant elder generation is through the throttling of the 4th throttle unit, become the refrigerant of low-temp low-pressure, and then flow through the first part of Intermediate Heat Exchanger, and absorb the heat of refrigerant in the second part of Intermediate Heat Exchanger.
Preferably, described coolant circulation system comprises: the liquid section of the refrigerant fluid stream of water pump, transfer valve, described battery, low temperature water tank, Intermediate Heat Exchanger; The water pump setting of connecting with the refrigerant fluid stream of described battery, the outlet of described transfer valve can switch to realize according to system condition the switching of the multiple-working mode of coolant circulation system: a outlet of wherein said transfer valve is connected to the liquid section of described Intermediate Heat Exchanger, the liquid section of Intermediate Heat Exchanger then is connected to an end communication port of the refrigerant fluid stream of battery by pipeline, realize the passive refrigerating mode of system during a outlet conducting; The b outlet of described transfer valve is connected to low temperature water tank, and the other end of low temperature water tank then is connected to an end communication port of the refrigerant fluid stream of battery by pipeline, realizes the active cooling pattern of system during b outlet conducting.
Preferably, described coolant circulation system also comprises self-loopa pattern, heating mode, also be provided with the second electric heater in the coolant circuit of described coolant circulation system to realize heating mode, described transfer valve also is provided with the c outlet, and the c outlet is connected to an end communication port of the refrigerant fluid stream of battery by pipeline.Heating mode is set can avoids battery working under the low temperature very much, thus travelled distance and the service life that can improve battery.And the energy consumption that the self-loopa pattern can further be saved system is set, improve system effectiveness.
Compared with prior art, the present invention has the following advantages: automotive air-conditioning system of the present invention adopts heat pump techniques, comes to raise the efficiency brownout be used to heating from the low-temperature heat source absorbing heat; To the water cooled cooling of battery, have multiple-working mode simultaneously: passive refrigerating mode, the active cooling pattern, the most energy-conservation mode of operation can according to the mode of operation of ambient temperature and battery itself, be selected by system; And then save further electric energy, and raise the efficiency, increase the travelled distance of car load.
Description of drawings
Fig. 1 is the pipeline connection diagram of refrigerant-cycle systems when refrigeration mode of the first specific embodiment of the present invention;
Fig. 2 is the pipeline connection diagram of the first specific embodiment refrigerant-cycle systems of the present invention when heating mode;
Fig. 3 is the pipeline connection diagram of the first specific embodiment refrigerant-cycle systems of the present invention when deice mode;
Fig. 4 is the pipeline connection diagram of the first specific embodiment coolant circulation system of the present invention when passive refrigerating mode;
Fig. 5 is the pipeline connection diagram of the first specific embodiment coolant circulation system of the present invention when the active cooling pattern;
Fig. 6 is the pipeline connection diagram of the first specific embodiment coolant circulation system of the present invention when the self-loopa pattern;
Fig. 7 is the pipeline connection diagram of the second specific embodiment of the present invention;
Fig. 8 is the scheme drawing that the pipeline of a/c system refrigerant-cycle systems shown in Figure 7 when heating mode connects;
Fig. 9 is the pipeline connection diagram of the third specific embodiment of the present invention;
Figure 10 is the pipeline connection diagram of the 4th kind of specific embodiment of the present invention.
The specific embodiment
For above-mentioned purpose of the present invention, feature and advantage can be become apparent more, below in conjunction with accompanying drawing the specific embodiment of the present invention is described in detail.
Automotive air-conditioning system of the present invention comprises refrigerant-cycle systems and coolant circulation system: refrigerant-cycle systems provides low-temperature receiver and thermal source for passenger accommodation, can be simultaneously coolant circulation system low-temperature receiver is provided; Coolant circulation system can be selected best mode of operation according to the needs of thermal load, is in better service conditions with the temperature of controlling battery.Refrigerant-cycle systems belongs to heat pump, comprising: refrigeration mode, heating mode, deice mode etc.The first specific embodiment of the present invention such as Fig. 1-shown in Figure 6, wherein Fig. 1 is the pipeline connection diagram of the first specific embodiment of the present invention, its refrigerant-cycle systems is when refrigeration mode; Fig. 2 is the pipeline connection diagram of refrigerant-cycle systems when heating mode; Fig. 3 is the pipeline connection diagram of refrigerant-cycle systems when deice mode; Fig. 4 is the pipeline connection diagram of coolant circulation system when passive refrigerating mode; Fig. 5 is the pipeline connection diagram of coolant circulation system when the active cooling pattern; Fig. 6 is the pipeline connection diagram of coolant circulation system when the self-loopa pattern; Wherein pipeline is represented by dotted lines this place's pipeline and is cut off obstructed among the figure.
As shown in the figure, refrigerant-cycle systems of the present invention comprises compressor 1, be positioned at vapour liquid separator 14 before the compressor inlet, carry out compartment outer heat-exchanger 6, first throttle element 10, the 3rd throttle unit 8, air-conditioning box 100, the second section fluid element 5 of interchange of heat, the refrigerant section 91 of Intermediate Heat Exchanger 9 with the compartment external environment, and connects to form complete heat pump type air conditioning system by corresponding pipeline.Wherein the first air-conditioning box 100 be used for regulating in the compartment temperature with or humidity, the first air-conditioning box 100 comprises evaporator 101, car inner condenser 102, temperature damper 105, electric heater 103, grid and air channel 109 in cycle throttle 106, interior circulating air opening 107, fresh wind port 108, the first blower fan 104, the car, for passenger accommodation provides comfortable environment; Also be provided with the 3rd shutoff valve 13 in the pipeline in car before the evaporator 101, first throttle element 10 is arranged in the pipeline between compartment outer heat-exchanger 6 and the 3rd shutoff valve 13, be provided with second section fluid element 5 in the pipeline after the car inner condenser 102, be arranged in parallel bypass flow path with second section fluid element 5, whether be provided with conducting that the first shutoff valve 3 controls bypass flow path in the bypass flow path.After second section fluid element 5 or its bypass flow path, be provided with compartment outer heat-exchanger 6 and reach the second blower fan 15 that wind regime is provided to compartment outer heat-exchanger 6, from compartment outer heat-exchanger 6 pipeline out, be provided with triple valve 7, the import of triple valve 7 is connected with the outlet of compartment outer heat-exchanger 6, and the first outlet 71 of triple valve 7 is connected to first throttle element 10 and the 3rd throttle unit 8; The another port of first throttle element 10 is connected with the 3rd shutoff valve 13.And be connected with the refrigerant section 91 of Intermediate Heat Exchanger 9 in the pipeline after the 3rd throttle unit 8, after being connected with the outlet of the second shutoff valve 12, the second shutoff valves 12 and evaporator 101 refrigerant out converges in car, the another port of refrigerant section 91 gets back to vapour liquid separator 14.And the second outlet 72 of triple valve 7 directly is connected to vapour liquid separator 14 by pipeline.Intermediate Heat Exchanger 9 can be divided into two parts: refrigerant section 91, liquid section 92, and the Fluid Flow in A between refrigerant section 91 and the liquid section 92 is independently, but can carry out interchange of heat between the two; And the concrete form of Intermediate Heat Exchanger 9 can be the relatively low and small volume of the such manufacturing cost of shell and tube exchanger, also can adopt plate type heat exchanger in addition; Can also be the form of water tank in addition: the liquid section 92 such as Intermediate Heat Exchanger 9 be a water tank, and there is refrigerant fluid inside, and the refrigerant section 91 of Intermediate Heat Exchanger 9 then by the liquid section 92 of refrigerant fluid is housed, so equally also can realize the purpose of interchange of heat between the two.Evaporator 101, car inner condenser 102 are selected to carry out heat supply, cooling or demist to described compartment according to the operating mode demand in the compartment in the described car, specifically can be arranged in the compartment, also can be arranged at outside the compartment and blow in the compartment by air supply duct.
Coolant circulation system comprises: the liquid section 92 of the refrigerant fluid stream of water pump 20, transfer valve 21, battery 22, low temperature water tank 23, Intermediate Heat Exchanger 9 etc.The import of transfer valve 21 is connected with water pump 20 pipelines, transfer valve 21 total a, b, three available switchings in exit position of c, thereby determine three flow directions of refrigerant fluid, be three circulation patterns of coolant circulation system: wherein a outlet is connected to the liquid section 92 of Intermediate Heat Exchanger 9,92 water route imports of getting back to battery 22 by the pipeline connection of the liquid section of Intermediate Heat Exchanger 9; The b outlet is connected to low temperature water tank 23, and the other end of low temperature water tank 23 connects the water route import of getting back to battery 22 by pipeline; The water route import of battery 22 is directly got back in the c outlet by pipeline.
When needed to freeze in the compartment summer, the a/c system of refrigerant-cycle systems switched to refrigeration mode, and at this moment battery 22 also cools off simultaneously.Under refrigeration mode, the first shutoff valve 3, the second shutoff valve 12, the 3rd shutoff valve 13 are opened; Triple valve 7 leads to the first outlet 71 conductings of first throttle element 10, the 3rd throttle unit 8, and the second outlet that triple valve 2 leads to vapour liquid separator 14 72 is closed.Under refrigeration mode, compressor 1 consumes certain electric energy, and the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure, and then the car inner condenser 102 of flowing through flows to compartment outer heat-exchanger 6 by the first shutoff valve 3.The refrigerant of High Temperature High Pressure in compartment outer heat-exchanger 6 under the cooling condensation of cooling-air stream B, emit heat by and be discharged in the ambient air and go, itself undergo phase transition and be condensed into liquid state.Liquid refrigerant from compartment outer heat-exchanger 6 out after, flow through triple valve 7, can be divided into two-way: first via liquid refrigerant makes refrigerant step-down cooling through 10 throttlings of first throttle element; The liquid refrigerant of low-temp low-pressure arrives evaporator 101 in the cars by the 3rd shutoff valve 13, the heat in car among the liquid refrigerant absorbing air of the evaporator 101 low-temp low-pressures stream A, itself undergo phase transition and flash to gaseous state and in the car evaporator 101 flow out.Another road liquid refrigerant is through 8 throttlings of the 3rd throttle unit, make refrigerant step-down cooling, then the liquid refrigerant that arrives low-temp low-pressure arrives the refrigerant section 91 of Intermediate Heat Exchanger 9, the heat of the liquid dielectrics such as refrigerant fluid such as water in the liquid refrigerant absorption liquid body 92 of refrigerant section 91 low-temp low-pressures, itself undergo phase transition and flash to gaseous state, then out also pass through the second shutoff valve 12 from refrigerant section 91, converge with out gaseous refrigerant the evaporator in car 101, separation through vapour liquid separator 14, liquid refrigerant (if any) be stored in the vapour liquid separator 14, the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure again by compressor 1, so periodical duty.104 couples of air stream A of the first blower fan play the conveying effect.By cool-down dehumidification, through grid and air channel 109, it is indoor to send into car by evaporator 101 in the car for air stream A, reduces the indoor temperature of car, and comfortable by bus environment is provided.
In addition, the control of air stream A temperature can also be achieved in that can be as required, by the opening angle of temperature damper 105 determine the to flow through ratio of car inner condenser 102, and the flow through air stream of car inner condenser 102 of heating, mix with original air stream again, and reach required temperature.Wherein, air stream A is the mixing wind of interior circulating air opening 107 and fresh wind port 108 of flowing through, and blending ratio can by system according to the traveling comfort requirement, be controlled by cycle throttle 106.And circulated air can further be saved power consumption in introducing.And when temperature is higher, can closing temperature air door 105, make air stream A not carry out interchange of heat with car inner condenser 102; And in temperature when not being very high, at this moment battery needs cooling, and the air stream A that is transported to does not then need too low temperature in the compartment in, then can suitably open temperature damper 105, thereby controls the leaving air temp of air stream A.At this moment, the liquid refrigerant of low-temp low-pressure evaporates and absorbing heat in the refrigerant section 91 of Intermediate Heat Exchanger 9, the cooling of the refrigerant fluid of the liquid section 92 of the Intermediate Heat Exchanger 9 of flowing through, for the cooling fluid circulation, make battery 22 be operated in suitable temperature, to keep its work period of service and life-span.
Under the pattern described above, freeze simultaneously in battery and the compartment.In addition, in the present embodiment in the car evaporator 101 and Intermediate Heat Exchanger 9 can work independently, specifically can be achieved by the control to the second shutoff valve 12 and the 3rd shutoff valve 13, thereby can be separately provide low-temperature receiver for passenger accommodation or battery.As when not needing cold wind in the compartment or when battery needs rapid cooling, the 3rd shutoff valve 13 can be closed, the second shutoff valve 12 is opened, and the flow through refrigerant section 91 of Intermediate Heat Exchanger of refrigerant is only arranged.The 3rd shutoff valve 13 and the second shutoff valve 12 concrete preferential electromagnetic valves that adopt control to realize the automatically needs of control; In addition, in order further to improve the efficiency of refrigerant-cycle systems, the 3rd shutoff valve 13 and the second shutoff valve 12 can be used instead with the flow-controlling gate of cutoff function and control with the distribution of carrying out flow, control the flow by the refrigerant of this two-way, to cut the waste, improve system energy efficiency.
When external temperature further reduces, at this moment the compartment need to heat to improve temperature, and battery 22 temperature when travelling at the beginning is lower, and need suitably cooling when driving to that certain fare register battery can generate heat, here the operation of refrigerant-cycle systems as shown in Figure 2, Fig. 2 is the pipeline connection diagram of the first specific embodiment refrigerant-cycle systems of the present invention when heating mode; Under heating mode, the first shutoff valve 3 is closed, and simultaneously the second shutoff valve 12,13 is closed, and the first outlet 71 that triple valve 7 leads to first throttle element 10, the 3rd throttle unit 8 is closed, and triple valve 2 leads to the second outlet 72 conductings of vapour liquid separator 14.Compressor 1 consumes certain electric energy, and the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure, and the car inner condenser 102 of flowing through under the cooling condensation of Cryogenic air stream A, itself undergoes phase transition and is condensed into liquid state.Liquid refrigerant becomes the liquid refrigerant of low-temp low-pressure through the throttling of second section fluid element 5.The liquid refrigerant of low-temp low-pressure flows to compartment outer heat-exchanger 6, B carries out interchange of heat with Cryogenic air stream, absorb its heat of vaporization and become the gaseous refrigerant of low-temp low-pressure, cool off simultaneously low temperature water tank 23, at this moment, to the cooling of battery can by with the low temperature liquid medium circulation of low temperature water tank 23 to battery to cool off.Like this, this system can be from the low temperature environment of lower temperature absorbing heat, realize the function of heat pump.Absorbing heat undergoes phase transition and the low-temperature low-pressure refrigerant that evaporates flows through triple valve 7, and flows to vapour liquid separator 14 from the second outlet 72 of triple valve 7; Through the separation of vapour liquid separator 14, liquid refrigerant is stored in the vapour liquid separator 14, and the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure again by compressor 1, so periodical duty.104 couples of air stream A of the first blower fan play the conveying effect, and air stream A is heated by car inner condenser 102, and through grid and air channel 109, it is indoor to send into car, increase the indoor temperature of car, and comfortable by bus environment is provided.Wherein, air stream A is the mixing wind of interior circulating air opening 107 and fresh wind port 108 of flowing through, but the blending ratio system is controlled by cycle throttle 106 according to the traveling comfort requirement.And the ratio of interior circulated air is not to cause that vehicle window knot mist is as target.And circulated air can further be saved power consumption in introducing.If ambient temperature is too low, the heating properties of heat pump is not enough, or causes heat pump efficiency lower, or even when causing heat pump to work, can come auxiliary heating with electric heater 103, realize heating function with heat pump.Like this, the operating range of this system further strengthens, thereby has enlarged the range of use of electronlmobil, particularly in the low cold zone of low temperature.
Not allow refrigerant pass through evaporator 101 in the car when heating in the refrigerant-cycle systems during above-mentioned Implementation Modes, the wind that blows out of blower fan 104 carries out interchange of heat by not carrying out interchange of heat during evaporator 101 in the car and directly arrive the high car inner condenser of refrigerant temperature 102 like this.
In addition when winter, the outer temperature of some regional car is lower, when external temperature is lower than zero degree or during near zero degree, because during heating mode, compartment outer heat-exchanger 6 is for cold scattering, after the heating mode work-hours is long, make 6 frostings of compartment outer heat-exchanger or freeze easily like this, and then affect the efficiency of operation of heat pump even lose heat dispersion, so, need to regularly or according to running condition start deicing (or claiming to defrost) pattern.Particularly, refrigerant-cycle systems of the present invention when deice mode running condition as shown in Figure 3, Fig. 3 is the pipeline connection diagram of the first specific embodiment refrigerant-cycle systems of the present invention when deice mode.At this moment, the first shutoff valve 3, the 3rd shutoff valve 13 are opened, and the second shutoff valve 12 is closed, and triple valve 7 leads to the first outlet 71 conductings of first throttle element 10, and the second outlet 72 that triple valve 2 leads to vapour liquid separator 14 is closed.Compressor 1 consumes certain electric energy, the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure, the car inner condenser 102 of flowing through, at this moment, blower fan 104 can not worked, so there is not air stream A, this moment, the gaseous refrigerant of High Temperature High Pressure flowed to compartment outer heat-exchanger 6 by the first shutoff valve 3, emit heat, the ice (frost) on compartment outer heat-exchanger 6 surfaces is removed rapidly, recover heating performance.Refrigerant itself undergoes phase transition and is condensed into liquid state (or part).Refrigerant makes refrigerant step-down cooling when flowing through first throttle element 10, the refrigerant of low-temp low-pressure evaporator 101 in car does not have interchange of heat.The refrigerant of low-temp low-pressure, through the separation of vapour liquid separator 14, liquid refrigerant is stored in the vapour liquid separator 14, and the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure again by compressor 1, and so periodical duty carries out deicing.Like this, the operating range of this system further strengthens, thereby has enlarged the range of use of electronlmobil, particularly in the low cold zone of low temperature.
Just begun deicing when deicing finishes at deice mode, the pressure-enthalpy chart of its refrigerant is the process of a dynamic change, when deice mode just begins, refrigerant by the gas-liquid two-phase before the vapour liquid separator 14, separation through vapour liquid separator 14, the refrigerant that leads to compressor 1 air suctiton inlet is saturated gaseous refrigerant, liquid refrigerant stays storage at the refrigerant liquid storage space of vapour liquid separator 14, so the capacity requirement of the refrigerant liquid storage space of vapour liquid separator 14, can guarantee like this that by the refrigerant behind the vapour liquid separator 14 be gaseous refrigerant at the 30-60% of described heat pump refrigerant charge; When deicing was in stable condition, its discharge state reached super heat at leisure, thereby can not cause the wet compression of compressor 1.
In addition, also can select whether to carry out interchange of heat at car inner condenser 102 during deice mode, as wanting quick deicing namely can not allow car inner condenser 102 carry out interchange of heat, the temperature that arrives like this refrigerant of compartment outer heat-exchanger 6 can be higher, and the time of deicing or frost just can be shorter.Usually, the time of deice mode operation is all relatively short, generally about 3-4 minute.By the time after deicing finishes, mode of operation can be returned to the heating mode operation.
Throttle unit can be selected throttle pipe, heating power expansion valve or electric expansion valve in the embodiment that the above introduces, and in order to ensure the efficiency of refrigerant-cycle systems, throttle unit is preferentially selected electric expansion valve.
The above has introduced the refrigerant-cycle systems of the first embodiment of the present invention, and the below introduces the coolant circulation system of the first embodiment of the present invention, and coolant circulation system comprises two kinds of mode of operations: passive refrigerating mode, active cooling pattern.
Passive refrigerating mode refers to that refrigerant-cycle systems need to provide low-temperature receiver to coolant circulation system, and passive refrigerating mode is applicable to the occasion that thermal load is larger or external temperature is higher of battery 22.At this moment, transfer valve 21 is operated in a exit position, that is: position a exit conducting, and position b, the c exit disconnects.Water pump 20 coolant pump to transfer valve 21, by the liquid section 92 of a outlet pump to Intermediate Heat Exchanger 9, cooled off by the low-temperature low-pressure refrigerant in the refrigerant section 91 of Intermediate Heat Exchanger 9, become the lower refrigerant fluid of temperature, return in the refrigerant fluid pipeline of battery 22, absorb the heat that battery 22 sheds, become the higher refrigerant fluid of temperature, get back to water pump 20, so finish a circulation.So circulation is for battery 22 dispels the heat.Under this pattern, the heat that battery 22 sends relies on refrigerant circulation to shed fully.Preferably, be controlled between 0-10 ℃ from the temperature of liquid section 92 liquid medium out of middle heat exchanger 9, thereby the operating temperature of guaranteeing battery 22 is between 25-35 ℃.Passive refrigerating mode generally cooperates the refrigeration mode result of use of refrigerant-cycle systems better.
The active cooling pattern refers to that refrigerant-cycle systems need not to provide low-temperature receiver to coolant circulation system, and the low-temperature receiver that coolant circulation system uses is the product of paying of refrigerant-cycle systems, can not bring load to refrigerant-cycle systems.The thermal load that the active cooling pattern is applicable to battery is not large especially, and external temperature is not extra high occasion.At this moment, transfer valve 21 is operated in the b exit position, that is: position b exit conducting, and position a, the c exit disconnects.Water pump 20 to transfer valve 21, exports pump to coolant pump to low temperature water tank 23 by b.In coolant storage tank 23, the refrigerant fluid that temperature is higher is under the cooling of air stream B, become the lower refrigerant fluid of temperature, be back to again in the liquid pipeline of battery 22, absorb the heat that battery 22 sheds, become the higher refrigerant fluid of temperature, get back to water pump 20, so finish a circulation.At this moment, the second blower fan 15 is worked, or directly utilizes the wind surface in the running car, and the heat that battery 22 is produced directly is dispersed in the external environment.So circulation is for battery 22 dispels the heat.Under this pattern, the heat that battery 22 sends does not rely on refrigerant circulation to shed, but relies on the wind surface in the second blower fan 15 or the running car directly to shed, and saves the electric energy of car load, raises the efficiency, and increases the travelled distance of car load.Usually, the active cooling pattern can cooperate the heating mode of refrigerant-cycle systems, also can cool off when refrigerant-cycle systems does not move.
In addition, in order further to reduce the power consumption of car load, coolant circulation system also is provided with the self-loopa pattern in the present embodiment.The self-loopa pattern is applicable in the very little situation of the thermal load of battery, and at this moment, transfer valve 21 is operated in the c exit position, that is: position c exit conducting, and position b, the c exit disconnects.Water pump 20 to transfer valve 21, in the liquid pipeline by the direct blowback battery 22 of c outlet pump, absorbs the heat that battery 22 sheds to coolant pump, becomes the slightly high refrigerant fluid of temperature, gets back to water pump 20, so finishes a circulation.So circulation is for battery 22 dispels the heat.This pattern is applicable to the smaller occasion of thermal load of battery.Can follow after passive refrigerating mode or active cooling pattern and be used, also can use separately.Utilize the larger characteristic of specific heat of water, by the circulation of refrigerant fluid self, make the interior temperature distribution of battery 22 comparatively even.Save the electric energy of car load, raise the efficiency, increase the travelled distance of car load.
Can find out from above, will be in the car in the first embodiment the refrigerant of evaporator 101 and the refrigerant section 91 of Intermediate Heat Exchanger 9 carry out throttling by first throttle element 10 and the 3rd throttle unit 8 respectively, the cold of these two parts can control to adjust respectively like this, thereby satisfies the different demands of these two parts.
The below introduces the second specific embodiment of the present invention, such as Fig. 7, shown in Figure 8, wherein Fig. 7 is the pipeline connection diagram of the second specific embodiment of the present invention, and Fig. 8 is the scheme drawing that the pipeline of a/c system refrigerant circulation shown in Figure 7 when heating mode connects.Present embodiment with above introduce the first embodiment difference be that refrigerant circulation is different when heating mode, particularly, increased by the second Intermediate Heat Exchanger 4 in the present embodiment, the 4th throttle unit 2, the 5th shutoff valve 15, the second Intermediate Heat Exchanger 4 is the dual channel H Exch, it comprises first part 41 and the second part 42, the second part 42 of the second Intermediate Heat Exchanger 4 is arranged in the outlet and the pipeline between the second section fluid element 5 of car inner condenser 102, first part 41 1 ends of the second Intermediate Heat Exchanger 4 connect the 4th throttle unit 2, the other end connects the 5th shutoff valve 15, i.e. the 4th throttle unit 2, the first part 41 of the second Intermediate Heat Exchanger 4, the 5th shutoff valve 15 is series connection setting, the other end of the 4th throttle unit 2 connects the outlet of car inner condenser 102, and the other end that the 5th shutoff valve 15 connects then is connected to the import of vapour liquid separator 14; The first part 41 of other the second Intermediate Heat Exchanger 4 and the sequence of erection of the 5th shutoff valve 15 can exchange, and are about to can realize too before the first part 41 that the 5th shutoff valve 15 is arranged on the second Intermediate Heat Exchanger 4.
The refrigerant-cycle systems of present embodiment the 5th shutoff valve 15 when refrigeration mode and deice mode is closed, and concrete operational mode is with reference to top the first embodiment.And when heating mode, the 5th shutoff valve 15 is opened, and the first shutoff valve 3 is closed, and the second shutoff valve 12,13 is closed simultaneously, the first outlet that triple valve 7 leads to first throttle element 10, the 3rd throttle unit 8 71 is closed, and triple valve 2 leads to the second outlet 72 conductings of vapour liquid separator 14.Under heating mode, compressor 1 consumes certain electric energy, the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure, the car inner condenser 102 of flowing through, under the cooling condensation of Cryogenic air stream A, itself undergo phase transition and be condensed into liquid state, then, refrigerant can be split into two parts: the second part 42 of first's refrigerant flow direction Intermediate Heat Exchanger 4, second portion refrigerant elder generation is through the throttling of the 4th throttle unit 2, become the liquid refrigerant of low-temp low-pressure, and then flow through the first part 41 of Intermediate Heat Exchanger, and and absorb the heat of refrigerant in the second part 42 of Intermediate Heat Exchanger 4, itself undergo phase transition and flash to gaseous state, through shutoff valve 15, flow to vapour liquid separator 14; And refrigerant further was cooled into the refrigerant of cold (or colder) in the second part 42 of Intermediate Heat Exchanger 4, make its step-down cooling through second section fluid element 5, flow to compartment outer heat-exchanger 6, carry out interchange of heat with Cryogenic air stream B, absorb its heat of vaporization and become the gaseous refrigerant of low-temp low-pressure.Like this, by the second Intermediate Heat Exchanger 4 is set, the temperature of the refrigerant that arrives compartment outer heat-exchanger 6 is further reduced, thereby the refrigerant in the raising compartment outer heat-exchanger 6 and the temperature difference of external environment, thereby make refrigerant can absorb the heat of how outside low temperature environment, namely this system can be from the low temperature environment of lower temperature absorbing heat, improve the function of heat pump.Absorbing heat undergoes phase transition and the low-temperature low-pressure refrigerant that evaporates flows through triple valve 7, by the second outlet 72 of triple valve 7, and converges with the second part 42 low-temperature low-pressure refrigerants of coming from the second Intermediate Heat Exchanger 4 and to flow to vapour liquid separator 14.Through the separation of vapour liquid separator 14, liquid refrigerant is stored in the vapour liquid separator 14, and the gaseous refrigerant of low-temp low-pressure is compressed into the gaseous refrigerant of High Temperature High Pressure again by compressor 1, so periodical duty.By the second Intermediate Heat Exchanger 4 is set, the operating range of this heat pump further increases, and efficient also can correspondingly improve, and particularly can enlarge the serviceability temperature scope of electronlmobil, particularly in the low cold zone of low temperature.Other operational processs of present embodiment can with reference to top the first embodiment, just be not described in detail here.
The below introduces the third embodiment of the present invention, as shown in Figure 9, the difference of present embodiment and the first embodiment of introducing above is that the refrigerant of evaporator 101 and the refrigerant section 91 of Intermediate Heat Exchanger 9 is not to carry out throttling by first throttle element 10 and the 3rd throttle unit 8 respectively in the car for leading to, but control by main throttle unit 16, the second shutoff valve 12 of this two-way break-make of the control that will originally arrange in addition, the 3rd shutoff valve 13 changes two into the flow-controlling gate of cutoff function, perhaps adds the mode of a flow-controlling gate by each shutoff valve is set respectively; The refrigerant that leads to evaporator 101 and the refrigerant section 91 of Intermediate Heat Exchanger 9 in the car is led to the refrigerant of evaporator 101 and the refrigerant section 91 of Intermediate Heat Exchanger 9 in the car by flow-controlling gate control, to guarantee in the compartment temperature with battery.Other operational modes of the present invention can with reference to top the first embodiment, be not described in detail here.
The below introduces the 4th kind of specific embodiment of the present invention, as shown in figure 10, the difference of this embodiment and top the third embodiment is also to be provided with the second electric heater 11 in the cooling-liquid cycle loop, when winter, temperature was very low, if battery moves under very low temperature, travelled distance and life-span in the time of can shortening equally its use, so can optionally drive the refrigerant fluid in the loop of the second electric heater 11 heating and cooling fluid circulations, be used for heating to battery, because the heating-up temperature of electric heater is controllable, so just be easy to make battery operated at suitable range of temperatures, thereby improve its travelled distance and service life, at this moment can between self-loopa pattern and heating mode, change for the temperature control mode of battery and carry out, to guarantee the operating temperature of battery 22.Other operational mode can be with reference to embodiment described above.In addition, the second electric heater can also be arranged on other positions in the loop of self-loopa pattern.
In addition, in several embodiments that the above introduces, be to carry out the control of the type of flow of refrigerant by triple valve 7 by the refrigerant behind the compartment outer heat-exchanger 6, triple valve 7 specifically can adopt the control of electromagnetism switching mode, make its an outlet conducting, another port closing; But the present invention is not limited to this, can also adopt other modes to control, as adopt two electromagnetic valves to control respectively too and can realize the object of the invention, namely control respectively the refrigerant flow path that out leads to afterwards vapour liquid separator 14 from compartment outer heat-exchanger 6 with two electromagnetic valves, lead to Intermediate Heat Exchanger 9, the refrigerant flow path of evaporator 101 directions in the car, wherein these two electromagnetic valves optionally conducting one of them, can realize purpose of the present invention equally like this, operational mode can with reference to top embodiment, no longer be repeated here particularly.Several enforcement embodiments of introducing above in addition can also mutually make up or substitute, and this should be to be easy to just can realize those skilled in the art, so also introduce no longer in detail.
The above only is preferred embodiment of the present invention, is not the present invention is done any pro forma restriction.Although the present invention discloses as above with preferred embodiment, yet is not to limit the present invention.Any those of ordinary skill in the art, do not breaking away from the technical solution of the present invention scope situation, all can utilize method and the technology contents of above-mentioned announcement that technical solution of the present invention is made many possible changes and modification, or be revised as the equivalent embodiment of equivalent variations.Therefore, every content that does not break away from technical solution of the present invention according to any simple modification, equivalent variations and the modification that technical spirit of the present invention is done above embodiment, all still belongs in the scope of technical solution of the present invention protection.
Claims (10)
1. automotive air-conditioning system is included as that passenger accommodation provides the refrigerant-cycle systems of low-temperature receiver and thermal source and according to the coolant circulation system of thermal load control battery temperature, refrigerant-cycle systems can be coolant circulation system low-temperature receiver is provided; Described refrigerant-cycle systems belongs to heat pump, comprises at least: refrigeration mode, heating mode; Described refrigerant-cycle systems comprises compressor, be positioned at the vapour liquid separator before the compressor inlet, the car inner condenser that is connected with the outlet of compressor, and the compartment external environment carry out compartment outer heat-exchanger, the car evaporator of interchange of heat; Be provided with the second section fluid element in the pipeline between described car inner condenser and the compartment outer heat-exchanger, the second section fluid element is provided with a bypass flow path; Refrigerant-cycle systems also comprises and can be the Intermediate Heat Exchanger that coolant circulation system provides low-temperature receiver; From leading to the pipeline of evaporator in the car, Intermediate Heat Exchanger, described compartment outer heat-exchanger is provided with at least one throttle unit, make refrigerant-cycle systems when refrigeration mode, after the throttle unit throttling, can lead to evaporator in the car, Intermediate Heat Exchanger through the refrigerant of compartment outer heat-exchanger condensation; Described coolant circulation system comprises: passive refrigerating mode, and the active cooling pattern, coolant circulation system absorbs cold to be used for the cooling to battery from described Intermediate Heat Exchanger when passive refrigerating mode.
2. automotive air-conditioning system according to claim 1, it is characterized in that, pipeline after the described compartment outer heat-exchanger is divided into two streams: wherein the first loop directly is connected to described vapour liquid separator by pipeline, and second servo loop leads to evaporator and described Intermediate Heat Exchanger in the described car; The conducting when heating mode of the first loop, second servo loop conducting when refrigeration mode; Described refrigerant-cycle systems is provided with the break-make in triple valve or two these two loops of solenoid control.
3. automotive air-conditioning system according to claim 2, it is characterized in that, described compartment outer heat-exchanger leads to evaporator in the described car, respectively be provided with a throttle unit in the pipeline of described Intermediate Heat Exchanger: described compartment outer heat-exchanger leads to the first throttle element of evaporator in the described car, described compartment outer heat-exchanger leads to the 3rd throttle unit of the refrigerant section of described Intermediate Heat Exchanger, when refrigeration mode, refrigerant is divided into two streams after condensing by described compartment outer heat-exchanger, and wherein the first stream flows to evaporator in the described car after the throttling of first throttle element; The second stream flows to the refrigerant section of described Intermediate Heat Exchanger after the 3rd throttle unit throttling.
4. automotive air-conditioning system according to claim 3 is characterized in that, is respectively arranged with shutoff valve or electromagnetic valve in described two streams or with the flow-controlling gate of cutoff function.
5. automotive air-conditioning system according to claim 2, it is characterized in that, described compartment outer heat-exchanger leads to and is provided with a throttle unit in the pipeline of evaporator in the described car, described Intermediate Heat Exchanger: main throttle unit, when refrigeration mode, refrigerant by the outer heat-exchanger condensation of described compartment after by second servo loop, by being divided into again two streams after the described main throttle unit throttling: flow to evaporator in the described car the first stream, flow to the second stream of the refrigerant section of described Intermediate Heat Exchanger.
6. automotive air-conditioning system according to claim 5 is characterized in that, at least one stream is provided with the flow-controlling gate of cutoff function or is provided with shutoff valve and the combination of flow-controlling gate in described two streams.
7. arbitrary described automotive air-conditioning system wherein according to claim 1-6, it is characterized in that, described refrigerant-cycle systems comprises the second Intermediate Heat Exchanger, the 4th throttle unit, the second Intermediate Heat Exchanger comprises first part and the second part, the second part of the second Intermediate Heat Exchanger is arranged in the outlet and the pipeline between described the 3rd throttle unit of described car inner condenser, first part one end of the second Intermediate Heat Exchanger connects the 4th throttle unit, and the other end is connected to the import of described vapour liquid separator by the pipeline valve member; The other end of described the 4th throttle unit is connected to the outlet of described car inner condenser by pipeline fitting; The first part of described the 4th throttle unit, the second Intermediate Heat Exchanger is series connection setting.
8. automotive air-conditioning system according to claim 7 is characterized in that, described the second Intermediate Heat Exchanger is the dual channel H Exch, is provided with shutoff valve or electromagnetic valve in the first part place pipeline of described the 4th throttle unit, the second Intermediate Heat Exchanger; When heating mode, shutoff valve or electromagnetic valve in the first part place pipeline of described the 4th throttle unit, the second Intermediate Heat Exchanger are opened, make the refrigerant behind the car inner condenser of flowing through to be split into two parts: the second part of first's refrigerant flow direction Intermediate Heat Exchanger, second portion refrigerant elder generation is through the throttling of the 4th throttle unit, become the refrigerant of low-temp low-pressure, and then flow through the first part of Intermediate Heat Exchanger, and absorb the heat of refrigerant in the second part of Intermediate Heat Exchanger.
9. according to the arbitrary described automotive air-conditioning system of the claims, it is characterized in that described coolant circulation system comprises: the liquid section of the refrigerant fluid stream of water pump, transfer valve, described battery, low temperature water tank, Intermediate Heat Exchanger; The water pump setting of connecting with the refrigerant fluid stream of described battery, the outlet of described transfer valve can switch to realize according to system condition the switching of the multiple-working mode of coolant circulation system: a outlet of wherein said transfer valve is connected to the liquid section of described Intermediate Heat Exchanger, the liquid section of Intermediate Heat Exchanger then is connected to an end communication port of the refrigerant fluid stream of battery by pipeline, realize the passive refrigerating mode of system during a outlet conducting; The b outlet of described transfer valve is connected to low temperature water tank, and the other end of low temperature water tank then is connected to an end communication port of the refrigerant fluid stream of battery by pipeline, realizes the active cooling pattern of system during b outlet conducting.
10. automotive air-conditioning system according to claim 9, it is characterized in that, described coolant circulation system also comprises self-loopa pattern, heating mode, also be provided with the second electric heater in the coolant circuit of described coolant circulation system to realize heating mode, described transfer valve also is provided with the c outlet, and the c outlet is connected to an end communication port of the refrigerant fluid stream of battery by pipeline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210116386.3A CN103373193B (en) | 2012-04-20 | 2012-04-20 | A kind of automotive air-conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210116386.3A CN103373193B (en) | 2012-04-20 | 2012-04-20 | A kind of automotive air-conditioning system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103373193A true CN103373193A (en) | 2013-10-30 |
| CN103373193B CN103373193B (en) | 2016-05-04 |
Family
ID=49459260
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210116386.3A Active CN103373193B (en) | 2012-04-20 | 2012-04-20 | A kind of automotive air-conditioning system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103373193B (en) |
Cited By (31)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103644617A (en) * | 2013-12-30 | 2014-03-19 | 安徽江淮汽车股份有限公司 | Double-evaporator air-conditioning system for pure electric vehicle and control method of system |
| CN105020816A (en) * | 2014-04-30 | 2015-11-04 | 杭州三花研究院有限公司 | Air conditioning system |
| CN105398308A (en) * | 2015-12-09 | 2016-03-16 | 北京新能源汽车股份有限公司 | Air conditioning system of electric vehicle |
| CN106183842A (en) * | 2015-05-26 | 2016-12-07 | 福特全球技术公司 | Management is for the refrigerating mode of the high-tension battery of vehicle |
| CN107394311A (en) * | 2017-08-02 | 2017-11-24 | 上海加冷松芝汽车空调股份有限公司 | The cooling of electric automobile power battery and heating system |
| CN109037853A (en) * | 2018-10-29 | 2018-12-18 | 重庆科技学院 | Electric automobile power battery temperature management system |
| CN109291761A (en) * | 2018-11-09 | 2019-02-01 | 上海加冷松芝汽车空调股份有限公司 | A kind of electric automobile heat-pump air-conditioning system |
| WO2019029218A1 (en) * | 2017-08-08 | 2019-02-14 | 杭州三花研究院有限公司 | Automotive air conditioning system |
| CN109353185A (en) * | 2018-11-21 | 2019-02-19 | 珠海格力电器股份有限公司 | Combined type heat manages system and its control method, electric car |
| CN109720165A (en) * | 2017-10-27 | 2019-05-07 | 翰昂汽车零部件有限公司 | Vehicle heat pump system |
| CN109760484A (en) * | 2018-12-29 | 2019-05-17 | 中国科学院广州能源研究所 | A kind of thermal management system of electric automobile |
| EP3453989A4 (en) * | 2016-05-10 | 2019-05-22 | BYD Company Limited | Heat pump air conditioning system and electric automobile |
| CN109849617A (en) * | 2019-03-11 | 2019-06-07 | 中国科学院广州能源研究所 | A kind of heat management system for electric car |
| CN110195940A (en) * | 2019-05-10 | 2019-09-03 | 江苏敏安电动汽车有限公司 | A kind of air conditioning for automobiles heat pump system of integrated heat exchanger |
| CN110375463A (en) * | 2018-04-12 | 2019-10-25 | 杭州三花研究院有限公司 | Hot pump in low temp system |
| CN110641242A (en) * | 2019-09-05 | 2020-01-03 | 珠海格力电器股份有限公司 | Defrosting control method and device for heat pump air conditioner of electric vehicle and computer readable storage medium |
| CN110953699A (en) * | 2018-09-26 | 2020-04-03 | 杭州三花研究院有限公司 | Air conditioning system and control method thereof |
| WO2020134371A1 (en) * | 2018-12-28 | 2020-07-02 | 杭州三花研究院有限公司 | Heat pump system |
| CN111923683A (en) * | 2019-05-13 | 2020-11-13 | 艾卡尔科技股份有限公司 | Vehicle thermodynamic method and system |
| CN112092566A (en) * | 2019-06-17 | 2020-12-18 | 杭州三花研究院有限公司 | Thermal management system |
| CN112140831A (en) * | 2019-06-28 | 2020-12-29 | 杭州三花研究院有限公司 | Thermal management system |
| CN109774409B (en) * | 2018-12-26 | 2021-01-19 | 爱驰汽车有限公司 | Automobile heat management system |
| CN112339521A (en) * | 2019-08-08 | 2021-02-09 | 杭州三花研究院有限公司 | Thermal management system and control method thereof |
| CN113173050A (en) * | 2021-02-26 | 2021-07-27 | 三花控股集团有限公司 | Thermal management system |
| CN113335026A (en) * | 2021-07-23 | 2021-09-03 | 曼德电子电器有限公司 | Cooling circulation system for electric vehicle motor battery cooling and heat pump and operation method |
| CN113370748A (en) * | 2021-07-14 | 2021-09-10 | 珠海格力电器股份有限公司 | Thermal management system and electric automobile |
| CN113725519A (en) * | 2021-08-31 | 2021-11-30 | 远景能源有限公司 | Liquid cooling system with dehumidification function |
| WO2022179593A1 (en) * | 2021-02-26 | 2022-09-01 | 三花控股集团有限公司 | Heat management system |
| EP3984794A4 (en) * | 2019-09-19 | 2022-10-19 | Hangzhou Sanhua Research Institute Co., Ltd. | Thermal management system |
| WO2022246968A1 (en) * | 2021-05-27 | 2022-12-01 | 深圳昂湃技术有限公司 | Heat pump air conditioning device and implementation method thereof |
| US11828507B2 (en) | 2018-09-25 | 2023-11-28 | Hangzhou Sanhua Research Institute Co., Ltd. | Air conditioning system and control method therefor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060063048A1 (en) * | 2004-09-23 | 2006-03-23 | Kolodziej Jason R | Optimal temperature tracking for necessary and accurate thermal control of a fuel cell system |
| JP2007294305A (en) * | 2006-04-26 | 2007-11-08 | Nissan Motor Co Ltd | Cooling system of fuel cell |
| CN101551174A (en) * | 2008-04-04 | 2009-10-07 | 通用汽车环球科技运作公司 | Vehicle HVAC and battery thermal management |
| CN102050007A (en) * | 2010-12-13 | 2011-05-11 | 法雷奥汽车空调湖北有限公司 | Control system for heat management of electric vehicle |
| CN102104181A (en) * | 2009-12-18 | 2011-06-22 | 上海汽车集团股份有限公司 | Power accumulator heat management system and vehicle |
-
2012
- 2012-04-20 CN CN201210116386.3A patent/CN103373193B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060063048A1 (en) * | 2004-09-23 | 2006-03-23 | Kolodziej Jason R | Optimal temperature tracking for necessary and accurate thermal control of a fuel cell system |
| JP2007294305A (en) * | 2006-04-26 | 2007-11-08 | Nissan Motor Co Ltd | Cooling system of fuel cell |
| CN101551174A (en) * | 2008-04-04 | 2009-10-07 | 通用汽车环球科技运作公司 | Vehicle HVAC and battery thermal management |
| CN102104181A (en) * | 2009-12-18 | 2011-06-22 | 上海汽车集团股份有限公司 | Power accumulator heat management system and vehicle |
| CN102050007A (en) * | 2010-12-13 | 2011-05-11 | 法雷奥汽车空调湖北有限公司 | Control system for heat management of electric vehicle |
Cited By (47)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103644617A (en) * | 2013-12-30 | 2014-03-19 | 安徽江淮汽车股份有限公司 | Double-evaporator air-conditioning system for pure electric vehicle and control method of system |
| CN103644617B (en) * | 2013-12-30 | 2016-08-10 | 安徽江淮汽车股份有限公司 | The control method of pure electric automobile double evaporators air conditioning system |
| CN105020816A (en) * | 2014-04-30 | 2015-11-04 | 杭州三花研究院有限公司 | Air conditioning system |
| CN105020816B (en) * | 2014-04-30 | 2019-06-28 | 杭州三花研究院有限公司 | Air-conditioning system |
| CN106183842A (en) * | 2015-05-26 | 2016-12-07 | 福特全球技术公司 | Management is for the refrigerating mode of the high-tension battery of vehicle |
| CN105398308A (en) * | 2015-12-09 | 2016-03-16 | 北京新能源汽车股份有限公司 | Air conditioning system of electric vehicle |
| CN105398308B (en) * | 2015-12-09 | 2019-04-12 | 北京新能源汽车股份有限公司 | The air-conditioning system of electric car |
| EP3453989A4 (en) * | 2016-05-10 | 2019-05-22 | BYD Company Limited | Heat pump air conditioning system and electric automobile |
| CN107394311A (en) * | 2017-08-02 | 2017-11-24 | 上海加冷松芝汽车空调股份有限公司 | The cooling of electric automobile power battery and heating system |
| CN107394311B (en) * | 2017-08-02 | 2023-07-14 | 上海加冷松芝汽车空调股份有限公司 | Cooling and heating system of electric automobile power battery |
| US11358438B2 (en) | 2017-08-08 | 2022-06-14 | Hangzhou Sanhua Research Institute Co., Ltd. | Automotive air conditioning system |
| WO2019029218A1 (en) * | 2017-08-08 | 2019-02-14 | 杭州三花研究院有限公司 | Automotive air conditioning system |
| CN109720165A (en) * | 2017-10-27 | 2019-05-07 | 翰昂汽车零部件有限公司 | Vehicle heat pump system |
| CN114459171A (en) * | 2018-04-12 | 2022-05-10 | 杭州三花研究院有限公司 | Low-temperature heat pump system |
| CN110375463B (en) * | 2018-04-12 | 2022-02-01 | 杭州三花研究院有限公司 | Low-temperature heat pump system |
| CN110375463A (en) * | 2018-04-12 | 2019-10-25 | 杭州三花研究院有限公司 | Hot pump in low temp system |
| US11828507B2 (en) | 2018-09-25 | 2023-11-28 | Hangzhou Sanhua Research Institute Co., Ltd. | Air conditioning system and control method therefor |
| CN110953699A (en) * | 2018-09-26 | 2020-04-03 | 杭州三花研究院有限公司 | Air conditioning system and control method thereof |
| CN109037853A (en) * | 2018-10-29 | 2018-12-18 | 重庆科技学院 | Electric automobile power battery temperature management system |
| CN109037853B (en) * | 2018-10-29 | 2023-04-21 | 重庆科技学院 | Temperature management system for power battery of electric automobile |
| CN109291761A (en) * | 2018-11-09 | 2019-02-01 | 上海加冷松芝汽车空调股份有限公司 | A kind of electric automobile heat-pump air-conditioning system |
| CN109291761B (en) * | 2018-11-09 | 2023-09-12 | 上海加冷松芝汽车空调股份有限公司 | Heat pump air conditioning system of electric automobile |
| CN109353185A (en) * | 2018-11-21 | 2019-02-19 | 珠海格力电器股份有限公司 | Combined type heat manages system and its control method, electric car |
| CN109353185B (en) * | 2018-11-21 | 2023-08-29 | 珠海格力电器股份有限公司 | Combined type thermal management system, control method thereof and electric automobile |
| CN109774409B (en) * | 2018-12-26 | 2021-01-19 | 爱驰汽车有限公司 | Automobile heat management system |
| WO2020134371A1 (en) * | 2018-12-28 | 2020-07-02 | 杭州三花研究院有限公司 | Heat pump system |
| CN109760484B (en) * | 2018-12-29 | 2021-01-05 | 中国科学院广州能源研究所 | Electric automobile thermal management system |
| CN109760484A (en) * | 2018-12-29 | 2019-05-17 | 中国科学院广州能源研究所 | A kind of thermal management system of electric automobile |
| CN109849617B (en) * | 2019-03-11 | 2022-02-01 | 中国科学院广州能源研究所 | Thermal management system for electric automobile |
| CN109849617A (en) * | 2019-03-11 | 2019-06-07 | 中国科学院广州能源研究所 | A kind of heat management system for electric car |
| CN110195940A (en) * | 2019-05-10 | 2019-09-03 | 江苏敏安电动汽车有限公司 | A kind of air conditioning for automobiles heat pump system of integrated heat exchanger |
| CN111923683A (en) * | 2019-05-13 | 2020-11-13 | 艾卡尔科技股份有限公司 | Vehicle thermodynamic method and system |
| CN112092566B (en) * | 2019-06-17 | 2024-04-05 | 杭州三花研究院有限公司 | Thermal management system |
| CN112092566A (en) * | 2019-06-17 | 2020-12-18 | 杭州三花研究院有限公司 | Thermal management system |
| CN112140831A (en) * | 2019-06-28 | 2020-12-29 | 杭州三花研究院有限公司 | Thermal management system |
| CN112339521A (en) * | 2019-08-08 | 2021-02-09 | 杭州三花研究院有限公司 | Thermal management system and control method thereof |
| CN110641242B (en) * | 2019-09-05 | 2024-04-19 | 珠海格力电器股份有限公司 | Defrosting control method and device for heat pump air conditioner of electric automobile and computer readable storage medium |
| CN110641242A (en) * | 2019-09-05 | 2020-01-03 | 珠海格力电器股份有限公司 | Defrosting control method and device for heat pump air conditioner of electric vehicle and computer readable storage medium |
| EP3984794A4 (en) * | 2019-09-19 | 2022-10-19 | Hangzhou Sanhua Research Institute Co., Ltd. | Thermal management system |
| CN113173050A (en) * | 2021-02-26 | 2021-07-27 | 三花控股集团有限公司 | Thermal management system |
| WO2022179593A1 (en) * | 2021-02-26 | 2022-09-01 | 三花控股集团有限公司 | Heat management system |
| WO2022246968A1 (en) * | 2021-05-27 | 2022-12-01 | 深圳昂湃技术有限公司 | Heat pump air conditioning device and implementation method thereof |
| CN113370748B (en) * | 2021-07-14 | 2023-09-29 | 珠海格力电器股份有限公司 | Thermal management system and electric automobile |
| CN113370748A (en) * | 2021-07-14 | 2021-09-10 | 珠海格力电器股份有限公司 | Thermal management system and electric automobile |
| CN113335026B (en) * | 2021-07-23 | 2022-06-17 | 曼德电子电器有限公司 | Cooling circulation system for electric vehicle motor battery cooling and heat pump and operation method |
| CN113335026A (en) * | 2021-07-23 | 2021-09-03 | 曼德电子电器有限公司 | Cooling circulation system for electric vehicle motor battery cooling and heat pump and operation method |
| CN113725519A (en) * | 2021-08-31 | 2021-11-30 | 远景能源有限公司 | Liquid cooling system with dehumidification function |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103373193B (en) | 2016-05-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103373193A (en) | Air conditioning system of automobile | |
| CN110525169B (en) | Integrated passenger cabin heat pump air conditioner and three-electric heating management system for pure electric vehicle | |
| CN103358851B (en) | A kind of automotive air-conditioning system | |
| CN104121724B (en) | A kind of air-conditioning system and a kind of heat exchanger | |
| CN103256746B (en) | A kind of automotive air-conditioning system | |
| CN108705915A (en) | A kind of heat management system for electric vehicle | |
| CN106938601B (en) | Electric automobile heat pump air conditioning system and control method thereof | |
| CN209274301U (en) | A kind of heat management system for electric vehicle | |
| CN103256747B (en) | A kind of automotive air-conditioning system | |
| CN103707736B (en) | A kind of automotive air-conditioning system | |
| CN108749517A (en) | A kind of heat management system of electric vehicle | |
| CN112248743B (en) | Dual-temperature-zone outdoor heat exchanger heat pump system | |
| CN103712277B (en) | A kind of automotive air-conditioning system | |
| CN103158486B (en) | A kind of automotive air-conditioning system | |
| CN103192675B (en) | A kind of automotive air-conditioning system | |
| CN103158487A (en) | Automobile air conditioning system | |
| CN106585323B (en) | Working mode of new energy automobile air conditioning system with quick defrosting and demisting functions | |
| CN113246686B (en) | Integrated thermal management system of pure electric vehicle and pure electric vehicle | |
| CN209079590U (en) | A kind of heat pump air conditioning system and automobile | |
| CN115675013A (en) | Multi-working-condition finished automobile thermal management system and method for new energy electric automobile | |
| CN103158490A (en) | Car air-conditioning system | |
| CN103162360B (en) | A kind of automotive air-conditioning system | |
| CN112477554A (en) | Battery thermal management system for electric vehicle heat pump | |
| CN103292510A (en) | Automobile air conditioning system | |
| CN103192676B (en) | A kind of automotive air-conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20171222 Address after: 312500 Xinchang County, Zhejiang Province under the streets of Liquan Village Patentee after: Sanhua Holding Group Co., Ltd. Address before: 310018, No. 12, No. 289, Hangzhou Economic Development Zone, Zhejiang Patentee before: Hangzhou Sanhua Institute Co., Ltd. |
|
| TR01 | Transfer of patent right |