CN103206819B - Gas-liquid separator and vehicle air conditioner - Google Patents
Gas-liquid separator and vehicle air conditioner Download PDFInfo
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- CN103206819B CN103206819B CN201210546515.2A CN201210546515A CN103206819B CN 103206819 B CN103206819 B CN 103206819B CN 201210546515 A CN201210546515 A CN 201210546515A CN 103206819 B CN103206819 B CN 103206819B
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Abstract
The invention provides a gas-liquid separator which can separate a refrigerant into a liquid and a gas refrigerant, store them, and selectively supply the refrigerants to an expansion valve and a compressor. The gas-liquid separator (9) comprises: a liquid storage chamber (24) used for storing a refrigerant, a refrigerant inlet (25a) used for enabling the refrigerant to flow into the liquid storage chamber (24), a first opening part (27) opened at a lower part of the liquid storage chamber (24), a second opening part (29) opened at an upper part of the liquid storage chamber (24), a first refrigerant outlet (30) used for guiding the refrigerant to the expansion valve (7), a second refrigerant outlet (31) used for guiding the refrigerant to the compressor (3), a flow path switching valve (34) which can be switched into a first switching position enabling communication of the first opening part (27) and the first refrigerant outlet (30), and a second switching position enabling communication of the second opening part (29) and the second refrigerant outlet (31).
Description
Technical field
The present invention relates to the gas-liquid separator being located at steam compression type refrigerating circulation and the air conditioner for motor vehicle with this gas-liquid separator.
Background technology
Such as in electric automobile, almost can not the heating of Btu utilization in compartment in the future self-driven source.Therefore, the various cold-producing medium of compression-type refrigeration cycle operation that makes is proposed as refrigeration source or that air conditioner for motor vehicle (such as with reference to patent document 1 and patent document 2) as heating source.
The compression-type refrigeration circulation of this air conditioner for motor vehicle comprises: compressor, and it is for compressed refrigerant; Indoor condenser, it adds hot-air for making through carrying out heat exchange between the compressed cold-producing medium of compressor and the air being supplied in compartment; Outdoor heat exchanger, it is for carrying out heat exchange between the air outside cold-producing medium and compartment; Decompression member, it reduces pressure for making cold-producing medium; Indoor evaporator, it carries out heat exchange and cooling-air for making the cold-producing medium that reduced pressure through above-mentioned decompression member and being supplied between the air in compartment.Further, need to make outdoor heat exchanger play function as condenser, or make outdoor heat exchanger play function as evaporimeter.Therefore, in the past, be configured with in the downstream of outdoor heat exchanger cold-producing medium guided via path from liquid tank to expansion valve, make cold-producing medium walk around indoor evaporator to guide via path from reservoir to compressor and be used for the stream switching part in these paths.
Patent document 1: Japanese Unexamined Patent Publication 2000 – No. 203249 publications (Japanese Patent No. 4341093 publication)
Patent document 2: Japanese Unexamined Patent Publication 10 – No. 287125 publications (Japanese Patent No. 3799732 publication)
Thus, the air conditioner for motor vehicle of previous example, because its cost increases, weight increases, and required installation space increases, and expects to cut down part number of packages so urgent.In addition, because needs arrange pipe-fitting joint between each constitution equipment, so also there is the worry connecting the number of working processes and increase.
Summary of the invention
Therefore, the present invention makes to solve the problem, and object is to provide a kind of and cold-producing medium can be separated into liquid refrigerant and gaseous refrigerant and stores and optionally supply the gas-liquid separator of each cold-producing medium to expansion valve and compressor and have the air conditioner for motor vehicle of this gas-liquid separator.
The feature of gas-liquid separator of the present invention is, comprising: fluid reservoir, and it is for store refrigerant; Refrigerant inlet, it flows into above-mentioned fluid reservoir for making cold-producing medium; 1st opening portion, it is in the lower openings of above-mentioned fluid reservoir; 2nd opening portion, it is at the upper opening of above-mentioned fluid reservoir; 1st refrigerant outlet, cold-producing medium is directed to decompression member by it; 2nd refrigerant outlet, cold-producing medium is directed to compressor by it; Flow path reversal valve, it can switch to the 1st switching position that makes to be communicated with between above-mentioned 1st opening portion with above-mentioned 1st refrigerant outlet and make the 2nd switching position that is communicated with between above-mentioned 2nd opening portion with above-mentioned 2nd refrigerant outlet.
Preferably, the interference of the cold-producing medium be arranged in the prominent part of for stirring swirling flow along the vertical direction in the bottom of above-mentioned fluid reservoir is dashed forward wall, the bottom of above-mentioned fluid reservoir, above-mentioned 1st opening portion of configuration, assigned position that above-mentioned interference is dashed forward beyond wall.
Preferably, the access will be communicated with between above-mentioned 2nd opening with above-mentioned 2nd refrigerant outlet is formed as the crow flies.
The feature of air conditioner for motor vehicle of the present invention is, comprising: compressor, and it is for compressed refrigerant; Indoor condenser, it adds hot-air for making through carrying out heat exchange between the compressed cold-producing medium of above-mentioned compressor and the air being supplied in compartment; Outdoor heat exchanger, it carries out heat exchange for making between air outside cold-producing medium and compartment; Decompression member, it reduces pressure for making cold-producing medium; Indoor evaporator, it carries out heat exchange and cooling-air for making the cold-producing medium that reduced pressure through above-mentioned decompression member and being supplied between the air in compartment; And gas-liquid separator, it is configured between above-mentioned outdoor heat exchanger and above-mentioned decompression member, has: fluid reservoir, for store refrigerant; Refrigerant inlet, it flows into above-mentioned fluid reservoir for making cold-producing medium; 1st opening portion, it is in the lower openings of above-mentioned fluid reservoir; 2nd opening portion, it is at the upper opening of above-mentioned fluid reservoir; 1st refrigerant outlet, it is for being directed to decompression member by cold-producing medium; 2nd refrigerant outlet, it is for being directed to compressor by cold-producing medium; Flow path reversal valve, it can switch to the 1st switching position that makes to be communicated with between above-mentioned 1st opening portion with above-mentioned 1st refrigerant outlet and make the 2nd switching position that is communicated with between above-mentioned 2nd opening portion with above-mentioned 2nd refrigerant outlet.
Adopt the present invention, the cold-producing medium flowed into from refrigerant inlet can be separated into liquid refrigerant and gaseous refrigerant by fluid reservoir and store, and suitably (in time) flow path reversal valve can be switched, liquid refrigerant is directed to expansion valve via the 1st opening portion of the bottom being located at fluid reservoir from the 1st refrigerant outlet, and gaseous refrigerant is directed to compressor via the 2nd opening portion on the top being located at fluid reservoir from the 2nd refrigerant outlet.Thus, gas-liquid separator has the function of storing liquid cold-producing medium and gaseous refrigerant respectively by cold-producing medium separation, with liquid refrigerant is optionally supplied to decompression member, gaseous refrigerant is optionally supplied to the function of compressor, so the quantity of constitution equipment can be reduced, compared with there is independently the situation of multiple constitution equipment as in the past, cost, weight and installation space can be cut down.In addition, the pipe-fitting joint of not pattern of wants equipment room, so can reduce pipe arrangement to connect the number of working processes.
Accompanying drawing explanation
Fig. 1 represents one embodiment of the present invention, is the structure chart of air conditioner for motor vehicle.
Fig. 2 represents one embodiment of the present invention, is the stereogram of gas-liquid separator.
Fig. 3 represents one embodiment of the present invention, is the top view unloaded after fluid reservoir of gas-liquid separator.
Fig. 4 represents one embodiment of the present invention, be flow path reversal valve when the 1st switching position, the A – A sectional view of Fig. 2 of gas-liquid separator.
Fig. 5 represents one embodiment of the present invention, be flow path reversal valve when the 2nd switching position, the B – B sectional view of Fig. 2 of gas-liquid separator.
Fig. 6 represents one embodiment of the present invention, is the key diagram of the swirling flow of the cold-producing medium produced in fluid reservoir.
Fig. 7 represents one embodiment of the present invention, is the D – D sectional view of Fig. 6.
Fig. 8 represents one embodiment of the present invention, is the figure of refrigerant path when representing Inner eycle heat absorption heating running.
Fig. 9 represents one embodiment of the present invention, is the figure of refrigerant path when representing outer circulation heat absorption heating running.
Figure 10 represents one embodiment of the present invention, is the figure of refrigerant path when heating (dehumidifying heating) running after representing refrigeration again.
Figure 11 represents one embodiment of the present invention, is the sectional view of the variation of the position arranging the 2nd refrigerant outlet.
Figure 12 represents one embodiment of the present invention, is the stereogram of the variation of the position arranging the 2nd refrigerant outlet.
Detailed description of the invention
Below, with reference to the accompanying drawings embodiments of the present invention are described.
one embodiment
As shown in Figure 1, air conditioner for motor vehicle 1 has steam compression type refrigerating circulation 2.Steam compression type refrigerating circulation 2 comprises: compressor 3, and it is for compressed refrigerant; Indoor condenser 4, it adds hot-air for making through carrying out heat exchange between the compressed cold-producing medium of compressor 3 and the air being supplied in compartment; Pressure adjusting parts 5, it is configured in the downstream of indoor condenser 4; Outdoor heat exchanger 6, it is configured in the downstream of pressure adjusting parts 5; Expansion valve 7, it is configured in the downstream of outdoor heat exchanger 6, is the decompression member for making cold-producing medium reduce pressure; Indoor evaporator 8, it is configured in the downstream of expansion valve 7; Gas-liquid separator 9, it is configured between outdoor heat exchanger 6 and expansion valve 7, and these parts above-mentioned are coupled together by each refrigerant piping 10.
In addition, steam compression type refrigerating circulation 2 comprises: triple valve 11, between its condenser 4 disposed in the interior and pressure adjusting parts 5; 1st bypass 12, it walks around outdoor heat exchanger 6, and is connected with this triple valve 11; 2nd bypass 13, it walks around expansion valve 7 and indoor evaporator 8, and is connected with gas-liquid separator 9.
Compressor 3 is such as blade-tape compressor, controls On/Off and the rotating speed of this compressor 3 according to the instruction from control assembly 14.
Indoor condenser 4 to be configured in air-conditioning box 15 and to be positioned at the downstream of indoor evaporator 8.Indoor condenser 4 for make through the cold-producing medium of the compressed HTHP of compressor 3 and in air-conditioning box 15 through air (being supplied to the air in compartment) carry out heat exchange.Indoor condenser 4 utilizes the exothermic effects of cold-producing medium to add hot-air.
Pressure adjusting parts 5 are made up of flow controller 5a and bypass 5c, and this bypass 5c is in parallel with flow controller 5a, and this bypass 5c is configured with open and close valve 5b.By making open and close valve 5b be positioned at open position, cold-producing medium can be made not reduce pressure and flow with original state.By making open and close valve 5b be positioned at closed position, cold-producing medium can be made to flow with reducing pressure because of flow controller 5a.Open and close valve 5b is controlled by control assembly 14.
Outdoor heat exchanger 6 is such as configured in enging cabin.Outdoor heat exchanger 6 carries out heat exchange for making to have passed between the air outside the cold-producing medium of indoor condenser 4 and compartment.
Expansion valve 7 has the temperature sensing tube portion (not shown) of the outlet side being located at indoor evaporator 8, and the valve opening of adjustment expansion valve 7, is maintained setting with the refrigerant superheat degree (overheated) of the outlet side by indoor evaporator 8 automatically.
Indoor evaporator 8 to be configured in air-conditioning box 15 and to be positioned at the upstream of indoor condenser 4.Indoor evaporator 8 for make the cold-producing medium that reduced pressure through expansion valve 7 and in air-conditioning box 15 through air (being supplied to the air in compartment) carry out heat exchange.Indoor evaporator 8 utilizes the heat-absorbing action cooling-air of cold-producing medium, dehumidifies.
As Fig. 2 to Fig. 5 in detail shown in, gas-liquid separator 9 has the shell 23 be made up of gas-liquid separation main body 21 and lower case 22.Gas-liquid separation main body 21 is drum, upper end closed, and lower end is uncovered.Be formed in the inside of gas-liquid separation main body 21 and cold-producing medium be separated into liquid refrigerant and gaseous refrigerant and the fluid reservoir 24 stored.
Run through the inflow pipe 25 having and guide the cold-producing medium transported via outdoor heat exchanger 6 or the 1st bypass 12 in the upper end of gas-liquid separation main body 21, cold-producing medium flows into fluid reservoir 24 from refrigerant inlet 25a.Immediately below refrigerant inlet 25a, be configured with swirling flow form component 26.
Swirling flow forms component 26 and has mulitpath, flows along convolution direction in order to the cold-producing medium flowed down from refrigerant inlet 25a.It is discoideus that swirling flow forms component 26.The peripheral part 26a that swirling flow forms component 26 is set as the size smaller than the inner peripheral surface of fluid reservoir 24.Thus, swirling flow formed to be formed with complete cycle between the peripheral part 26a of component 26 and the inner peripheral surface of fluid reservoir 24 can gap under confession flow of refrigerant.
The lower end of gas-liquid separation main body 21 is installed on the upper end 22a of lower case 22, utilizes the upper end 22a of this lower case 22 to form the bottom of fluid reservoir 24.That is, the upper end 22a of lower case 22 and gas-liquid separation main body 21 is utilized to form fluid reservoir 24.
In the bottom of fluid reservoir 24, namely the upper end 22a of lower case 22 be provided with the 1st opening portion 27 for being discharged from fluid reservoir 24 by liquid refrigerant.To hold up along the axis direction of fluid reservoir 24 at the central part of fluid reservoir 24 and be provided with pipe 28.The upper end open of this pipe 28 is configured to the 2nd opening portion 29 for discharging gaseous refrigerant from fluid reservoir 24.2nd central opening of opening portion 29 on the top of fluid reservoir 24.The lower end of pipe 28 is connected with the 2nd access 33.
Lower case 22 comprises: the 1st refrigerant outlet 30, and liquid refrigerant is directed to expansion valve 7 by it; 2nd refrigerant outlet 31, gaseous refrigerant is directed to compressor 3 by it; Flow path reversal valve 34, it can switch to the 2nd switching position making by the 1st access 32 the 1st switching position that is communicated with between the 1st opening portion 27 with the 1st refrigerant outlet 30 and make by the 2nd access 33 to be communicated with between the 2nd opening portion 29 with the 2nd refrigerant outlet 31.
Be arranged in the prominent part of at the upper end 22a of lower case 22 and interfere prominent wall 35, this interference wall 35 of dashing forward is stirring promotion divisions of the cold-producing medium stirring swirling flow along the vertical direction.Interfere prominent wall 35 to be trapezoidal prominent wall along the cross section that the radial direction of fluid reservoir 24 extends, interfere the circumferencial direction of wall 35 along fluid reservoir 24 of dashing forward with the configuration at equal intervals of 180 degree.
1st opening portion 27 is configured in the assigned position of interfering beyond prominent wall 35.Specifically, as shown in Figure 6 and Figure 7,1st opening portion 27 is configured in the outer circumferential side of the bottom of fluid reservoir 24 and is configured in scope B, above-mentioned scope B is 3/4 scope from the 1st position P1 to the scope A of the 2nd position P2, above-mentioned 1st position P 1 is to be positioned at the rear of this upper end 35a apart from the mode of the upper end 35a predetermined distance of interfering prominent wall 35, above-mentioned 2nd position P2 is positioned at the front of this upper end 35a to interfere the mode of the upper end 35a predetermined distance of prominent wall 35 apart from next.Here, the lower end position of inclined plane 35b when the 1st position P 1 is the inclined plane 35b inclination 45 degree of interference prominent wall 35, equally, the lower end position of inclined plane 35b when the 2nd position P2 is the inclined plane 35b inclination 45 degree of next interference prominent wall 35.
Flow path reversal valve 34 is housed in lower case 22 in revolvable mode, and flow path reversal valve 34 has utilization rotation and can change the spherical spool 41 of switching position, and spool 41 is driven by the driver 42 of the below being arranged on lower case 22.Driver 42 is controlled to drive by control assembly 14.
Spool 41 has the through hole 43 extended along the direction orthogonal with the rotating shaft direction of spool 41.Spool 41 can switch to the two-port of through hole 43 in the 1st switching position of the 1st access 32 split shed and the two-port of through hole 43 the 2nd switching position at the 2nd access 33 split shed.
1st refrigerant outlet 30 of lower case 22 is located at the 1st joint the 51,1st joint 51 and is installed on lower case 22.The rubber seal 52 in the gap between closed 1st joint 51 and lower case 22 is installed in the end by spool 41 side of the 1st joint 51.In addition, the 2nd refrigerant outlet 31 is located at the 2nd joint the 53,2nd joint 53 and is installed on lower case 22.The seal washer 54 in the gap between closed spool 41 and lower case 22, gap between spool 41 and the 2nd joint 53 is installed in the both sides of spool 41.
When adding heat run again after gas-liquid separator 9 carries out Inner eycle heat absorption heating running and refrigeration, as shown in Figure 4, spool 41 switches to and makes by the 1st access 32 the 1st switching position that is communicated with between the 1st opening portion 27 with the 1st refrigerant outlet 30.On the other hand, when carrying out outer circulation heat absorption heating running, as shown in Figure 5, spool 41 switches to and makes by the 2nd access 33 the 2nd switching position that is communicated with between the 2nd opening portion 29 with the 2nd refrigerant outlet 31.
In addition, the upstream side (left side of Fig. 1) of air-conditioning box 15 be provided with air blast, the air imported outside compartment outer circulation introducing port, import the Inner eycle introducing port of air in compartment and the inlet valve of the above-mentioned outer circulation introducing port of opening and closing and Inner eycle introducing port, these parts above-mentioned all omit diagram in FIG.The air blender door 16 to being adjusted by the air-supply of indoor condenser 4 and the mixed proportion of air-supply of walking around indoor condenser 4 is provided with in air-conditioning box 15.Be provided with foot's blow-off outlet, frost removal blow-off outlet and ventilation blow-off outlet in the position than this air blender door 16 downstream, these parts all omit diagram.
Control assembly 14 is utilized to switch the flow path reversal valve 34 of pressure adjusting parts 5, triple valve 11 and gas-liquid separator 9 respectively.Specifically, during circulation heat absorption heating running outside, as shown in Figure 9, the refrigerant path making to be turned back to compressor 3 by indoor condenser 4, triple valve 11, flow controller 5a, outdoor heat exchanger 6, gas-liquid separator 9 and the 2nd bypass 13 through the compressed cold-producing medium of compressor 3 is switched to.Flow controller 5a makes cold-producing medium reduce pressure, and outdoor heat exchanger 6 plays function as evaporimeter.When Inner eycle heat absorption heating running, as shown in Figure 8, the refrigerant path making to be turned back to compressor 3 by indoor condenser 4, triple valve 11, the 1st bypass 12, gas-liquid separator 9, expansion valve 7 and indoor evaporator 8 through the compressed cold-producing medium of compressor 3 is switched to.Cold-producing medium reduces pressure by expansion valve 7.When adding heat run again after refrigeration, as shown in Figure 10, the refrigerant path making to be turned back to compressor 3 by indoor condenser 4, bypass 5c, open and close valve 5b, outdoor heat exchanger 6, gas-liquid separator 9, expansion valve 7 and indoor evaporator 8 through the compressed cold-producing medium of compressor 3 is switched to.Pressure adjusting parts 5 do not make cold-producing medium reduce pressure, and outdoor heat exchanger 6 plays function as condenser.
Next, the action of air conditioner for motor vehicle 1 is described.When adding heat run again after refrigeration, as shown in Figure 10, triple valve 11 switches to and cold-producing medium is moved to outdoor heat exchanger 6 effluent, and open and close valve 5b switches to open mode, and the flow path reversal valve 34 of gas-liquid separator 9 switches to the 1st switching position.The cold-producing medium compressed through compressor 3 circulates in the refrigerant path by indoor condenser 4, triple valve 11, bypass 5c, open and close valve 5b, outdoor heat exchanger 6, gas-liquid separator 9, expansion valve 7 and indoor evaporator 8.Cold-producing medium through the compressed HTHP of compressor 3 dispels the heat to air at indoor condenser 4 and outdoor heat exchanger 6 place.Along with heat radiation, temperature declines cold-producing medium, and forms low pressure under the effect of expansion valve 7, and then this cold-producing medium absorbs heat from air in indoor evaporator 8.Thus, the air-supply of passing in air-conditioning box 15 is cooled in indoor evaporator 8, and part or all of this air-supply is reheated at indoor condenser 4 place.Thus, the air passed in air-conditioning box 15 is controlled the cold wind for preferred temperature.
When Inner eycle heat absorption heating running, as shown in Figure 8, triple valve 11 switches to and cold-producing medium is moved to the 1st bypass 12 effluent, and the flow path reversal valve 34 of gas-liquid separator 9 switches to the 1st switching position.Air blender door 16 switches to such as fully open position.Circulate in the refrigerant path by indoor condenser 4, triple valve 11, the 1st bypass 12, gas-liquid separator 9, expansion valve 7 and indoor evaporator 8 through the compressed cold-producing medium of compressor 3.Cold-producing medium through the compressed HTHP of compressor 3 dispels the heat to air in indoor condenser 4.Along with heat radiation, temperature declines, and the cold-producing medium becoming low pressure under the effect of expansion valve 7 absorbs heat from air in indoor evaporator 8.Thus, the air-supply of passing in air-conditioning box 15 is cooled in indoor evaporator 8, and the whole of this air-supply are reheated at indoor condenser 4 place.Thus, the air passed in air-conditioning box 15 is controlled the hot blast for preferred temperature.
During circulation heat absorption heating running outside, as shown in Figure 9, triple valve 11 switches to and cold-producing medium is moved to outdoor heat exchanger 6 effluent, and open and close valve 5b switches to closed condition, and the flow path reversal valve 34 of gas-liquid separator 9 switches to the 2nd switching position.Air blender door 16 switches to such as fully open position.Circulate in the refrigerant path by indoor condenser 4, triple valve 11, flow controller 5a, outdoor heat exchanger 6, gas-liquid separator 9 and the 2nd bypass 13 through the compressed cold-producing medium of compressor 3.Cold-producing medium through the compressed HTHP of compressor 3 dispels the heat to air at indoor condenser 4 place.Along with heat radiation, temperature declines cold-producing medium, and becomes low pressure along with the flow controller 5a by pressure adjusting parts 5, and then cold-producing medium absorbs heat from air at outdoor heat exchanger 6 place.Thus, the air-supply of passing in air-conditioning box 15 just have passed through this indoor evaporator 8 without the cooling at indoor evaporator 8 place, is heated at indoor condenser 4 place.Thus, the air passed in air-conditioning box 15 is controlled the hot blast for preferred temperature.During circulation heat absorption heating running outside, do not play the heat-absorbing action of cold-producing medium at indoor evaporator 8 place, not cooling-air, so the heating performance operating strong than Inner eycle heat absorption heating can be obtained.
Next, the action of the gas-liquid separator 9 in above-mentioned operation process is described in detail.The cold-producing medium transported via outdoor heat exchanger 6 or the 1st bypass 12 is directed into fluid reservoir 24 from refrigerant inlet 25a.The flow of refrigerant flow in fluid reservoir 24 is formed on component 26 through swirling flow, is formed as spiral flow and flows downward from the gap between peripheral part 26a and the inner peripheral surface of fluid reservoir 24.
As shown by the arrow in fig. 6, spiral flow is formed as the swirling flow of cold-producing medium in the bottom of fluid reservoir 24.The swirling flow of cold-producing medium, when with when interfering the lopsidedness face 35b of prominent wall 35 to contact, is climbed along inclined plane 35b, then passes through from interfering above the upper end 35a of prominent wall 35.When the time comes, heavy liquid refrigerant is easily interfering leaning in part C(Fig. 7 of 35b side, lopsidedness face on prominent wall 35 to represent) precipitation.Further, after the swirling flow of this cold-producing medium passes through the upper end 35a of the prominent wall 35 of interference, the gaseous refrigerant that proportion is little is in floating state, and the inclined plane 35b decline of the opposite side of wall 35 of dashing forward is interfered on the liquid refrigerant edge containing lubricating oil.Utilize the flowing of the above-below direction of this cold-producing medium to change and forcibly stir cold-producing medium along the vertical direction.Utilize this stirring to make gaseous refrigerant be deposited in the top of fluid reservoir 24, make the liquid refrigerant being mixed into lubricating oil be deposited in the bottom of fluid reservoir 24.When flow path reversal valve 34 is positioned at the 1st switching position, the liquid refrigerant being mixed into lubricating oil enters from the 1st opening portion 27, after the 1st access 32, flows out from the 1st refrigerant outlet 30.On the other hand, when flow path reversal valve 34 is positioned at the 2nd switching position, gaseous refrigerant enters from the 2nd opening portion 29, after the 2nd access 33, flows out from the 2nd refrigerant outlet 31.
As mentioned above, gas-liquid separator of the present invention comprises: fluid reservoir 24, and it is for store refrigerant; Refrigerant inlet 25a, it flows into fluid reservoir 24 for making cold-producing medium; 1st opening portion 27, it is in the lower openings of fluid reservoir 24; 2nd opening portion 29, it is at the upper opening of fluid reservoir 24; 1st refrigerant outlet 30, it is for being directed to expansion valve 7 by cold-producing medium; 2nd refrigerant outlet 31, it is for being directed to compressor 3 by cold-producing medium; Flow path reversal valve 34, it can switch to the 1st switching position that makes to be communicated with between the 1st opening portion 27 with the 1st refrigerant outlet 30 and make the 2nd switching position that is communicated with between the 2nd opening portion 29 with the 2nd refrigerant outlet 31.
Thus, the cold-producing medium flowed into from refrigerant inlet 25a can be separated into liquid refrigerant and gaseous refrigerant and store in fluid reservoir 24, and suitably switch flow path reversal valve 34, via the 1st opening portion 27 of the bottom being located at fluid reservoir 24, liquid refrigerant can be directed to expansion valve 7 from the 1st refrigerant outlet 30, and via the 2nd opening portion 29 on the top being located at fluid reservoir 24, gaseous refrigerant be directed to compressor 3 from the 2nd refrigerant outlet 31.Thus, gas-liquid separator 9 has the function being separated cold-producing medium and distinguishing storing liquid cold-producing medium and gaseous refrigerant, expansion valve 7 is optionally supplied to by liquid refrigerant, and gaseous refrigerant is optionally supplied to the function of compressor 3, so the quantity of constitution equipment can be reduced, compared with there is independently the situation of multiple constitution equipment as in the past, cost, weight and installation space can be cut down.In addition, the pipe-fitting joint to connecting between constitution equipment need not be set, so pipe arrangement can be reduced connect the number of working processes.
In the present embodiment, flow path reversal valve 34, by having along with rotating the spherical spool 41 that can change switching position, can reduce the installation space of spool 41, so can realize the densification of flow path reversal valve 34.
In the present embodiment, after have passed in the swirling flow of cold-producing medium the upper end 35a interfering prominent wall 35, the liquid refrigerant containing lubricating oil in swirling flow declines along interfering the inclined plane 35b of prominent wall 35, so by configuring the 1st opening portion 27 in scope B, lubricating oil can be reclaimed more and to conveying such as compressor 3 grade, above-mentioned scope B is 3/4 of the scope A from the 1st position P 1 to the 2 position P2, above-mentioned 1st position P1 is to be positioned at the rear of this upper end 35a apart from the mode of the upper end 35a predetermined distance of interfering prominent wall 35, above-mentioned 2nd position P2 is positioned at the front of this upper end 35a to interfere the mode of the upper end 35a predetermined distance of prominent wall 35 apart from next.In addition, when the swirling flow of cold-producing medium contacts with the inclined plane 35b of the side of interfering prominent wall 35, the part C precipitation of liquid refrigerant easily on front side of the root of the inclined plane 35b of side, not easily reclaim the lubricating oil in this part C, so be limited in scope B by the position of the 1st opening portion 27, avoid the position the 1st opening portion 27 being configured in above-mentioned part C.In addition, the swirling flow of the cold-producing medium in the fluid reservoir 24 and lubricating oil contained by liquid refrigerant is easily trapped in the outer circumferential side of the bottom of fluid reservoir 24 under the influence of centrifugal force, so more the 1st opening portion 27 of the outer circumferential side of lubricating oil self-configuring in the bottom of fluid reservoir 24 can be directed to the 1st refrigerant outlet 30.
the variation of the bottom of fluid reservoir
In the above-described embodiment, exemplified with in the bottom of fluid reservoir 24, namely the upper end 22a of lower case 22 interference of stirring the cold-producing medium of swirling flow be along the vertical direction set dash forward the situation of wall 35, but also can not arrange and interfere prominent wall and the bottom that is formed flatly fluid reservoir.In this case, the tap hole that the outer circumferential side configuration in the bottom of fluid reservoir is flowed out for the cold-producing medium in fluid reservoir.
the variation of the position of the 2nd refrigerant outlet
In the above-described embodiment, exemplified with the layout in order to improve constitution equipment, vehicle-mounted assembleability, and the driver 42 that spool 41 is rotated is configured in the situation of the below of lower case 22, but as is illustrated by figs. 11 and 12, also driver 42 can be configured in the side of lower case 22, and the 2nd refrigerant outlet 31 is arranged on the downside of lower case 22, thus can be formed as the crow flies and make the 2nd opening portion 29 of pipe 28 upper end and the access 61 be communicated with between the 2nd refrigerant outlet 31.Thus, compared with situation about bending halfway with access, the pressure loss of cold-producing medium in above-mentioned access 61 can be reduced.
description of reference numerals
1, air conditioner for motor vehicle; 2, steam compression type refrigerating circulation; 3, compressor; 4, indoor condenser; 6, outdoor heat exchanger; 7, expansion valve (decompression member); 8, indoor evaporator; 9, gas-liquid separator; 24, fluid reservoir; 25a, refrigerant inlet; 27, the 1st opening portion; 29, the 2nd opening portion; 30, the 1st refrigerant outlet; 31, the 2nd refrigerant outlet; 34, flow path reversal valve; 35, prominent wall is interfered; 61, access.
Claims (4)
1. a gas-liquid separator, is characterized in that,
This gas-liquid separator (9) comprising:
Fluid reservoir (24), it is for store refrigerant;
Refrigerant inlet (25a), it flows into above-mentioned fluid reservoir (24) for making cold-producing medium;
1st opening portion (27), it is in the lower openings of above-mentioned fluid reservoir (24);
2nd opening portion (29), it is at the upper opening of above-mentioned fluid reservoir (24);
1st refrigerant outlet (30), it is for being directed to decompression member (7) by cold-producing medium;
2nd refrigerant outlet (31), it is for being directed to compressor (3) by cold-producing medium;
Flow path reversal valve (34), it can switch to the 1st switching position that makes to be communicated with between above-mentioned 1st opening portion (27) with above-mentioned 1st refrigerant outlet (30) and make the 2nd switching position that is communicated with between above-mentioned 2nd opening portion (29) with above-mentioned 2nd refrigerant outlet (31).
2. gas-liquid separator according to claim 1 (9), is characterized in that,
Projecting in the bottom of above-mentioned fluid reservoir (24) have the interference of the cold-producing medium stirring swirling flow along the vertical direction to dash forward wall (35), above-mentioned 1st opening portion (27) of configuration, assigned position beyond the above-mentioned interference of the bottom of above-mentioned fluid reservoir (24) dashes forward wall (35).
3. gas-liquid separator according to claim 1 and 2 (9), is characterized in that,
Form the access (61) will be communicated with between above-mentioned 2nd opening portion (29) with above-mentioned 2nd refrigerant outlet (31) as the crow flies.
4. an air conditioner for motor vehicle, is characterized in that,
This air conditioner for motor vehicle (1) comprising:
Compressor (3), it is for compressed refrigerant;
Indoor condenser (4), it adds hot-air for making through carrying out heat exchange between the compressed cold-producing medium of above-mentioned compressor (3) and the air being supplied in compartment;
Outdoor heat exchanger (6), it carries out heat exchange for making between air outside cold-producing medium and compartment;
Decompression member (7), it is for reducing pressure to cold-producing medium;
Indoor evaporator (8), it carries out heat exchange and cooling-air for making the cold-producing medium that reduced pressure through above-mentioned decompression member (7) and being supplied between the air in compartment; And
Gas-liquid separator (9);
This gas-liquid separator (9) its be configured between above-mentioned outdoor heat exchanger (6) and above-mentioned decompression member (7), have: fluid reservoir (24), for store refrigerant;
Refrigerant inlet (25a), it flows into above-mentioned fluid reservoir (24) for making cold-producing medium;
1st opening portion (27), it is in the lower openings of above-mentioned fluid reservoir (24);
2nd opening portion (29), it is at the upper opening of above-mentioned fluid reservoir (24);
1st refrigerant outlet (30), it is for being directed to decompression member (7) by cold-producing medium;
2nd refrigerant outlet (31), it is for being directed to compressor (3) by cold-producing medium;
Flow path reversal valve (34), it can switch to the 1st switching position that makes to be communicated with between above-mentioned 1st opening portion (27) with above-mentioned 1st refrigerant outlet (30) and make the 2nd switching position that is communicated with between above-mentioned 2nd opening portion (29) with above-mentioned 2nd refrigerant outlet (31).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-006805 | 2012-01-17 | ||
| JP2012006805A JP5911728B2 (en) | 2012-01-17 | 2012-01-17 | Gas-liquid separator and vehicle air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103206819A CN103206819A (en) | 2013-07-17 |
| CN103206819B true CN103206819B (en) | 2015-04-08 |
Family
ID=48754123
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210546515.2A Expired - Fee Related CN103206819B (en) | 2012-01-17 | 2012-12-14 | Gas-liquid separator and vehicle air conditioner |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5911728B2 (en) |
| CN (1) | CN103206819B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6432339B2 (en) * | 2014-12-25 | 2018-12-05 | 株式会社デンソー | Refrigeration cycle equipment |
| JP6191642B2 (en) | 2015-03-25 | 2017-09-06 | コニカミノルタ株式会社 | Optional equipment for electrical equipment |
| JP6430465B2 (en) * | 2016-12-01 | 2018-11-28 | カルソニックカンセイ株式会社 | Gas-liquid separator |
| JP6606052B2 (en) | 2016-12-01 | 2019-11-13 | マレリ株式会社 | Air conditioner |
| JP6496434B1 (en) * | 2017-10-02 | 2019-04-03 | カルソニックカンセイ株式会社 | Air conditioner |
| WO2019069666A1 (en) * | 2017-10-02 | 2019-04-11 | カルソニックカンセイ株式会社 | Air conditioning device |
| JP6606254B2 (en) * | 2018-10-31 | 2019-11-13 | マレリ株式会社 | Gas-liquid separator |
| JP6606253B2 (en) * | 2018-10-31 | 2019-11-13 | マレリ株式会社 | Gas-liquid separator |
| JP7439658B2 (en) | 2020-06-30 | 2024-02-28 | 株式会社デンソー | Refrigeration cycle equipment |
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| US5184480A (en) * | 1991-12-23 | 1993-02-09 | Ford Motor Company | Accumulator for vehicle air conditioning system |
| JP2000009366A (en) * | 1998-04-24 | 2000-01-14 | Daiyu:Kk | Flow path switching device for working medium in cooling-heating device and accumulator provided therewith |
| US6035653A (en) * | 1997-04-17 | 2000-03-14 | Denso Corporation | Air conditioner |
| JP2000203249A (en) * | 1999-01-13 | 2000-07-25 | Denso Corp | Air conditioner |
| JP2011225174A (en) * | 2010-04-22 | 2011-11-10 | Calsonic Kansei Corp | Vehicular air conditioner |
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| JPH03260556A (en) * | 1990-03-08 | 1991-11-20 | Mitsubishi Electric Corp | Equipment for refrigeration cycle |
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| JP3794121B2 (en) * | 1997-02-28 | 2006-07-05 | 株式会社デンソー | Air conditioner for vehicles |
| JPH1123106A (en) * | 1997-07-02 | 1999-01-26 | Daiyu:Kk | Accumulator equipped with passage switching mechanism |
| JPH1130445A (en) * | 1997-07-10 | 1999-02-02 | Denso Corp | Refrigerating cycle device |
| JPH1194401A (en) * | 1997-07-24 | 1999-04-09 | Hitachi Ltd | Refrigerating and air-conditioning equipment |
| JPH11223407A (en) * | 1998-02-05 | 1999-08-17 | Nippon Soken Inc | Heat pump type air conditioner |
| JP2001330343A (en) * | 2000-05-19 | 2001-11-30 | Fujitsu General Ltd | Accumulator for compressor |
| JP3780834B2 (en) * | 2000-09-08 | 2006-05-31 | 株式会社日立製作所 | Air conditioner |
| JP2002307054A (en) * | 2001-04-12 | 2002-10-22 | Daikin Ind Ltd | Ozone water producing apparatus and gas-liquid separator thereof |
| JP2003074992A (en) * | 2001-08-31 | 2003-03-12 | Nippon Soken Inc | Refrigeration cycle apparatus |
| JP4776438B2 (en) * | 2006-05-26 | 2011-09-21 | サンデン株式会社 | Refrigeration cycle |
| JP2009198060A (en) * | 2008-02-20 | 2009-09-03 | Calsonic Kansei Corp | Air-conditioning system |
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2012
- 2012-01-17 JP JP2012006805A patent/JP5911728B2/en not_active Expired - Fee Related
- 2012-12-14 CN CN201210546515.2A patent/CN103206819B/en not_active Expired - Fee Related
Patent Citations (5)
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| US5184480A (en) * | 1991-12-23 | 1993-02-09 | Ford Motor Company | Accumulator for vehicle air conditioning system |
| US6035653A (en) * | 1997-04-17 | 2000-03-14 | Denso Corporation | Air conditioner |
| JP2000009366A (en) * | 1998-04-24 | 2000-01-14 | Daiyu:Kk | Flow path switching device for working medium in cooling-heating device and accumulator provided therewith |
| JP2000203249A (en) * | 1999-01-13 | 2000-07-25 | Denso Corp | Air conditioner |
| JP2011225174A (en) * | 2010-04-22 | 2011-11-10 | Calsonic Kansei Corp | Vehicular air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5911728B2 (en) | 2016-04-27 |
| CN103206819A (en) | 2013-07-17 |
| JP2013148229A (en) | 2013-08-01 |
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Granted publication date: 20150408 Termination date: 20201214 |