CN102367975A - Overhead-type car-mounted air conditioner system - Google Patents
Overhead-type car-mounted air conditioner system Download PDFInfo
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- CN102367975A CN102367975A CN2011102729900A CN201110272990A CN102367975A CN 102367975 A CN102367975 A CN 102367975A CN 2011102729900 A CN2011102729900 A CN 2011102729900A CN 201110272990 A CN201110272990 A CN 201110272990A CN 102367975 A CN102367975 A CN 102367975A
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Abstract
The invention discloses an overhead-type car-mounted air conditioner system, which comprises an air conditioner housing, a condenser, a condensing blower, a compressor, an evaporator, an evaporating blower, an expansion valve, a refrigerant circulating pipeline, a control circuit, a compressor power supply circuit and refrigerant, wherein the refrigerant is R410A refrigerant. The compressor is arranged inside the housing and is a fully-closed horizontal-type compressor which is electrically driven; a connection structure between the refrigerant circulating pipeline and parts which are connected with the refrigerant circulating pipeline adopts a welding structure, and a high-pressure pipeline between the compressor and the condenser and a high-pressure pipeline between the condenser and the expansion valve adopts a thick-wall pipe. Refrigerating output of R410A refrigerant per unit mass is 11.2 percent more than the refrigerating output of R134a refrigerant, and gas volume of the R410A refrigerant per unit refrigerating output is 132 percent smaller than the gas volume of the R134a refrigerant per unit refrigerating output; and the pressure of the R410A refrigerant is improved by 50 percent compared to that of the R407C refrigerant, the refrigerating output of R410A refrigerant per unit mass is improved by 6.2 percent compared to that of R407C refrigerant, and the gas volume of per refrigerating output is reduced by 60 percent compared to that of R407C refrigerant. Therefore, when R410A refrigerant is used as the refrigerant of the overhead-type car-mounted air conditioner system, the system size can be reduced, and the energy-efficiency ratio can be improved.
Description
The application is that invention is divided an application, and the application number of this division application original bill is 201110044758.1, and the applying date is on February 24th, 2011, and denomination of invention is " a kind of overhead type on-board air conditioner system ".
[technical field]
The present invention relates to car air-conditioner, relate in particular to a kind of overhead type on-board air conditioner system.
[background technology]
The employed cold-producing medium R12 of automobile air conditioning refrigerating system because its ODP value and GWP value are excessive, has been classified as the CFC material of forbidding in the world at present, and R22 substitutes working medium very soon also with disabled as short-term.Along with going deep into of mixed working fluid research in recent years, the multiple mixed working fluid that is suitable as alternative refrigerant has appearred.Wherein R407C, R410A are respectively that three kinds and two kinds of formulated by a certain percentage ODP of pure HFC working medium are zero mixed working fluid.
R134a substitutes working medium as a kind of comparatively ideal long-term, in a lot of refrigeration plants, is used widely.But the normal boiling point of R134a is merely-26.7 ℃, has limited its application at low temperatures.The refrigerating effect per unit swept volume of R407C and pressure are all more approaching with R22.Therefore, system also is applicable to the R407C system as long as the design of simple Adjustment System just can make former R22.But, systematic energy efficiency ratio (COP) can reduce about 5% than original system.This is because with respect to other cold-producing mediums, R407C has the temperature drift up to 6 ℃.Therefore the R407c system can reduce heat transmission when onesize condenser and evaporimeter, and influences systematic energy efficiency ratio.
R410A is the accurate azeotrope refrigerant of binary that is formed by 1: 1 mixed by R32 and R125.Compare with R22, R410A has the heat transmission and the flow behavior of significant advantage, and still, under the uniform temp condition, the pressure of R410A is about 1.5 times of R22, leaks more easily than R22, has limited the use of R410A on on-board air conditioner.
What the condensation air intake of traditional on-board air conditioner system adopted is air intake from the condensation chamber both sides, behind the condenser of the left and right sides, is blown out by the condensation fan of centre, and this structure can't be utilized head-on the wind comes from of vehicle ', and power consumption is higher, and structure is compact inadequately.
[summary of the invention]
The technical problem that the present invention will solve provides a kind of compact conformation, the higher overhead type on-board air conditioner system of Energy Efficiency Ratio.
In order to solve the problems of the technologies described above; The technical scheme that the present invention adopts is; A kind of overhead type on-board air conditioner system; Comprise air conditioner casing, condenser, condensation fan, compressor, evaporimeter, evaporation fan, expansion valve, refrigerant circulation line, control circuit, compressor power supply circuits and cold-producing medium, described cold-producing medium is the R410A cold-producing medium.Described compressor is arranged in the casing, is that electricity drives totally enclosed horizontal compressor; Syndeton between described refrigerant circulation line and the parts that are connected with circulation line adopts Welding Structure, and the pressure duct between the pressure duct between compressor and the condenser, condenser and the expansion valve adopts thick-walled pipe; On the pressure duct between compressor and the condenser, comprise the high voltage protective switch, during the hypertonia of compressor output end output, the high voltage protective switch sends guard signal to control circuit, and control circuit cuts off the power supply circuits of compressor.
Above-described overhead type on-board air conditioner system, the wall thickness of said thick-walled pipe is not less than 1.2 millimeters.
Above-described overhead type on-board air conditioner system, described air conditioner casing is divided into ante-chamber, lumen and back cavity, between ante-chamber and the lumen, separate with dividing plate between lumen and the back cavity; Described condenser, condensation fan, compressor are arranged in the ante-chamber, and described evaporimeter and evaporation fan are arranged in the back cavity, and the main part of described control circuit and compressor power supply circuits is arranged in the lumen.
Above-described overhead type on-board air conditioner system, described condenser is arranged in the front end of air conditioner casing ante-chamber, described condensation fan is 2 to 4, lateral arrangement at the middle part of ante-chamber, the back of condenser, described compressor is arranged in the rear portion of ante-chamber; The front end of air conditioner casing comprises the air inlet of condenser, and the top of air conditioner casing comprises the air outlet of condensation fan.
Above-described overhead type on-board air conditioner system; Described condenser is a parallel-flow heat exchanger; Described parallel-flow heat exchanger comprises isocon, collecting pipe and complex root flat tube, and every flat tube comprises the micro channel of plurality of parallel, and described flat tube connects isocon and collecting pipe; Described isocon includes an inlet and an outlet, and has dividing plate that isocon is divided into first and second portion in the isocon, and described inlet is communicated with first, and described outlet is communicated with second portion; The quantity of the flat tube that directly is communicated with isocon first is greater than the quantity of the flat tube that directly is communicated with the isocon second portion.
Above-described overhead type on-board air conditioner system, the front end face of air conditioner casing is the inclined-plane of hypsokinesis, described condenser hypsokinesis arranges that back rake angle is 70 ° to 78 °.
Above-described overhead type on-board air conditioner system, the axis of described flat tube cross section major axis and the angle of air conditioner casing lower plane are 15 ° to 25 °.
More than in 9 the described overhead type on-board air conditioner of arbitrary claim system, the condenser heat exchange area is 0.31 to 0.35 with the ratio of evaporimeter heat exchange area.
The overhead type on-board air conditioner employing R410A of system of the present invention is as cold-producing medium, and the refrigerating capacity of R410A unit mass is higher by 11.2% than R134a, and the gas volume of specific refrigerating effect is littler by 132% than R134a; The pressure ratio R407C's of R410A is high by 50%, but the unit mass refrigerating capacity is higher by 6.2% than R407C, and the gas volume of specific refrigerating effect is littler by 60% than R407C.Therefore, use R410A can reduce system bulk, improve Energy Efficiency Ratio as cold-producing medium.
[description of drawings]
Below in conjunction with the accompanying drawing and the specific embodiment the present invention is done further detailed explanation.
Fig. 1 is the outline drawing of overhead type on-board air conditioner system embodiment of the present invention.
Fig. 2 is the vertical view of overhead type on-board air conditioner structure embodiment internal structure of the present invention.
Fig. 3 is that the A of Fig. 2 is to cutaway view.
Fig. 4 is the partial enlarged drawing at B position among Fig. 3.
Fig. 5 is an overhead type on-board air conditioner system embodiment structure of condenser schematic diagram of the present invention
[specific embodiment]
To overhead type on-board air conditioner system embodiment shown in Figure 5, overhead type on-board air conditioner system comprises air conditioner casing 10, condenser 1, condensation fan 2, compressor 3, evaporimeter 4, evaporation fan 5, expansion valve 6, refrigerant circulation line, control circuit and compressor power supply circuits at Fig. 1.The used cold-producing medium of system is the R410A cold-producing medium.
On the pressure duct between compressor 3 and the condenser 1, the high voltage protective switch is housed.On the pressure duct between compressor 3 and the condenser 1, the high voltage protective switch is housed.During the hypertonia of compressor output end output; The high voltage protective switch breaks off; Controller in control circuit sends the too high guard signal of Compressor Discharge Pressure; Controller cuts off the power supply circuits of compressor, effectively eliminates the hidden danger that the system condensing high pressure brings, and the system that guaranteed uses the security of R410A cold-producing medium.
The front end face 1002 of air conditioner casing 10 is the inclined-plane of hypsokinesis, and condenser 1 is arranged in the front end of condensation chamber, and condenser 1 hypsokinesis arranges that back rake angle is 76 °.Totally 3 of condensation fans 2,3 condensation fan 2 lateral arrangement at the middle part of condensation chamber, the back of condenser 1.Compressor 3 is arranged in the rear portion of ante-chamber.The front end face 1002 of air conditioner casing 10 has the air inlet 1003 of condenser, and the air outlet of condensation fan 2 is arranged at the top 1004 of air conditioner casing 10.
As shown in Figure 5, condenser 1 is a parallel-flow heat exchanger, helps improving the withstand voltage level of condenser.Parallel-flow heat exchanger comprises isocon 11, collecting pipe 12 and complex root flat tube 13, and every flat tube 13 has a plurality of parallel micro channels 1301, and flat tube 13 connects isocon and collecting pipe; The inlet 1101 that is connected with compressor 3 is arranged at isocon 11 tops; The outlet 1102 that is connected with expansion valve 6 is arranged at the bottom; Have dividing plate that isocon is divided into first and second portion in the isocon 11, inlet 1101 is communicated with first, exports 1102 and is communicated with second portion; Cold-producing medium is cooling gradually in condenser, and volume flow reduces, and the flat tube that directly is communicated with isocon first is more than the flat tube that directly is communicated with the isocon second portion.
As shown in Figure 4, in order to reduce the air intake resistance, the axis of the flat tube 13 cross section major axis not principal plane with condenser 3 is vertical; But the angle that tilts; Like this, in the present embodiment, the angle of the axis of flat tube 13 cross section major axis and air conditioner casing 10 lower planes is 19 °.
Compare other heat exchanger, the advantage that the parallel-flow heat exchanger in the present embodiment has is following: the air side front face area is little, has increased the heat transfer area of air side; Internal volume is little, and the coolant injection amount is little; In light weight; Heat transfer coefficient is high; Windage is little, thereby noise is low.
Air quantity through heat exchanger is big more, and the heat that then heat exchanger obtained is just big more.But go for big more air quantity, just must consume more power of fan, thereby be unfavorable for energy-conservation.Present embodiment condenser 1 is arranged in front end, condenser 1 hypsokinesis of air conditioner casing 10 and arranges; Consider that mainly vehicle at a high speed to overtake; The wind to vehicle is met in the formation that air in the environment is relative; Utilize leading with fan blade of head-on wind, under the situation that consumes identical power of fan, condenser 1 can obtain bigger air quantity.Obtained energy-conservation effect to a certain extent, blower fan also can obtain the preferable performance curve simultaneously, thereby realizes the energy-efficient of air-conditioning system.
The above embodiment of the present invention adopts R410A as cold-producing medium, and gas density and the pressure of R410A are higher than R22, and operating pressure exceeds 50%-60%.The result that high pressure and high gas density are brought is, not only can use the compressor of littler capacity, can also use the more pipeline and the valve of minor diameter.The hidden danger that the system condensing high pressure brings has been eliminated in the use of high voltage protective switch.The system that makes thick compressor housing stands higher operating pressure.Compressor is made to such an extent that more thick and heavyly also have a benefit, and promptly the running noises of R410A compressor is than low significantly 2-4 decibel of R22 compressor.
Compare with the R22 system, it is high by 35% that the R410A system has the heat of significant hot transmission advantage one evaporimeter to transmit, and condenser is high by 5%.And system's heat transfer coefficient of R134a and R407c all is lower than R22.Under the equal quality flow, the pressure drop of R410A is less, and it can be used than R22 or littler pipeline and the valve of other cold-producing mediums.This will reduce more material cost for making the R410A system, and in long pipe arrangement family expenses machine and many on-line systems, more have superiority.Certainly, have only design system again, just can give full play to heat transmission and the little advantage of pressure drop of R410A---for example can consider to take following optimisation technique: use coil pipe than minor diameter; Different fin structures and increase closed circuit length; Reduce the quantity of refrigerating circuit etc.Finally we can see, in the system after designing again to the R410A cold-producing medium, adopt the evaporimeter and the condenser of smaller size smaller, and cost is lower, and reaches as high as 30% refrigerant charging decrease.The minimizing of refrigerant charge except cost reduces, can also promote the reliability of whole system.In identical refrigerating capacity, in the system of identical condensation temperature, adopt the systematic energy efficiency ratio of R410A to exceed 6% than R22.This is that the pressure drop in the whole system is littler because the loss of compressor in compression process is lower, and evaporimeter and condenser have stronger heat transmitting.Heat transmission makes it under identical service condition with littler pressure drop efficiently, and condensation temperature is lower, and evaporating temperature is higher, and this makes compressor in power consumption still less, and efficient obtains a better range of operation than under the higher situation.
Condenser 1 heat exchange area is 0.31 to 0.35 with the ratio of evaporimeter heat exchange area.
The above embodiment of the present invention adopts thick-walled pipe and micro-channel heat exchanger, and it is withstand voltage to have improved system, through adopting totally-enclosed compressor and welding pipeline, resolution system leakage problem.Condenser 1 heat exchange area and the ratio of evaporimeter heat exchange area are being confirmed as under 0.33 the condition; When the operating mode of 4.2 ℃ of suction superheat, 25 ℃ of the exhaust degrees of superheat, 11.5 ℃ of degree of supercoolings, 7 ℃ of evaporating temperatures, 55 ℃ of condensation temperatures; Can obtain the Energy Efficiency Ratio of overhead type on-board air conditioner system 2.65, apparently higher than the Energy Efficiency Ratio of traditional overhead type on-board air conditioner system less than 2.5.
Claims (8)
1. overhead type on-board air conditioner system; Comprise air conditioner casing, condenser, condensation fan, compressor, evaporimeter, evaporation fan, expansion valve, refrigerant circulation line, control circuit, compressor power supply circuits and cold-producing medium; It is characterized in that described cold-producing medium is the R410A cold-producing medium; Described compressor is arranged in the casing, is that electricity drives totally enclosed horizontal compressor; Syndeton between described refrigerant circulation line and the parts that are connected with circulation line adopts Welding Structure, and the pressure duct between the pressure duct between compressor and the condenser, condenser and the expansion valve adopts thick-walled pipe; On the pressure duct between compressor and the condenser, comprise the high voltage protective switch, during the hypertonia of compressor output end output, the high voltage protective switch sends guard signal to control circuit, and control circuit cuts off the power supply circuits of compressor.
2. overhead type on-board air conditioner according to claim 1 system is characterized in that the wall thickness of said thick-walled pipe is not less than 1.2 millimeters.
3. overhead type on-board air conditioner according to claim 1 system is characterized in that described air conditioner casing is divided into ante-chamber, lumen and back cavity, between ante-chamber and the lumen, separate with dividing plate between lumen and the back cavity; Described condenser, condensation fan, compressor are arranged in the ante-chamber, and described evaporimeter and evaporation fan are arranged in the back cavity, and the main part of described control circuit and compressor power supply circuits is arranged in the lumen.
4. overhead type on-board air conditioner according to claim 3 system; It is characterized in that described condenser is arranged in the front end of air conditioner casing ante-chamber, described condensation fan is 2 to 4; Lateral arrangement at the middle part of ante-chamber, the back of condenser, described compressor is arranged in the rear portion of ante-chamber; The front end of air conditioner casing comprises the air inlet of condenser, and the top of air conditioner casing comprises the air outlet of condensation fan.
5. overhead type on-board air conditioner according to claim 4 system; It is characterized in that; Described condenser is a parallel-flow heat exchanger; Described parallel-flow heat exchanger comprises isocon, collecting pipe and complex root flat tube, and every flat tube comprises the micro channel of plurality of parallel, and described flat tube connects isocon and collecting pipe; Described isocon includes an inlet and an outlet, and has dividing plate that isocon is divided into first and second portion in the isocon, and described inlet is communicated with first, and described outlet is communicated with second portion; The quantity of the flat tube that directly is communicated with isocon first is greater than the quantity of the flat tube that directly is communicated with the isocon second portion.
6. overhead type on-board air conditioner according to claim 5 system is characterized in that the front end face of air conditioner casing is the inclined-plane of hypsokinesis, and described condenser hypsokinesis arranges that back rake angle is 70 ° to 78 °.
7. overhead type on-board air conditioner according to claim 6 system is characterized in that the axis of described flat tube cross section major axis and the angle of air conditioner casing lower plane are 15 ° to 25 °.
8. according to the described overhead type on-board air conditioner of arbitrary claim system in the claim 1 to 7, it is characterized in that the condenser heat exchange area is 0.31 to 0.35 with the ratio of evaporimeter heat exchange area.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102729900A CN102367975A (en) | 2011-02-24 | 2011-02-24 | Overhead-type car-mounted air conditioner system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102729900A CN102367975A (en) | 2011-02-24 | 2011-02-24 | Overhead-type car-mounted air conditioner system |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011100447581A Division CN102095226A (en) | 2011-02-24 | 2011-02-24 | Top-mounted on-vehicle air-conditioning system |
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| CN102367975A true CN102367975A (en) | 2012-03-07 |
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| CN2011102729900A Pending CN102367975A (en) | 2011-02-24 | 2011-02-24 | Overhead-type car-mounted air conditioner system |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105216582A (en) * | 2015-11-16 | 2016-01-06 | 珠海格力电器股份有限公司 | On-board air conditioner |
| CN105890207A (en) * | 2016-04-15 | 2016-08-24 | 马怡鑫 | Environment-friendly type oil cooling and temperature controlling device |
| CN106994879A (en) * | 2017-05-17 | 2017-08-01 | 江苏国凯汽车部件有限公司 | Compact type vehicle-mounted top-mounted air conditioner |
| CN109606067A (en) * | 2019-01-28 | 2019-04-12 | 常州悅龙新能源汽车空调有限公司 | The car air-conditioner of overhead condenser |
| CN109624655A (en) * | 2018-12-27 | 2019-04-16 | 苏州新同创汽车空调有限公司 | A kind of pure electric vehicle top set air-conditioning |
| CN111251810A (en) * | 2018-11-30 | 2020-06-09 | 比亚迪股份有限公司 | Thermal management system of vehicle and vehicle |
| CN113639436A (en) * | 2021-08-02 | 2021-11-12 | 海尔(深圳)研发有限责任公司 | Method and device for adjusting heat exchange quantity of air conditioner outdoor unit and air conditioner outdoor unit |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105216582A (en) * | 2015-11-16 | 2016-01-06 | 珠海格力电器股份有限公司 | On-board air conditioner |
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| CN111251810A (en) * | 2018-11-30 | 2020-06-09 | 比亚迪股份有限公司 | Thermal management system of vehicle and vehicle |
| CN111251810B (en) * | 2018-11-30 | 2022-08-09 | 比亚迪股份有限公司 | Thermal management system of vehicle and vehicle |
| CN109624655A (en) * | 2018-12-27 | 2019-04-16 | 苏州新同创汽车空调有限公司 | A kind of pure electric vehicle top set air-conditioning |
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| CN113639436A (en) * | 2021-08-02 | 2021-11-12 | 海尔(深圳)研发有限责任公司 | Method and device for adjusting heat exchange quantity of air conditioner outdoor unit and air conditioner outdoor unit |
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Application publication date: 20120307 |