CN103541900A - Rotary type compressor, refrigerant circulation system and control method thereof - Google Patents
Rotary type compressor, refrigerant circulation system and control method thereof Download PDFInfo
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- CN103541900A CN103541900A CN201210242109.7A CN201210242109A CN103541900A CN 103541900 A CN103541900 A CN 103541900A CN 201210242109 A CN201210242109 A CN 201210242109A CN 103541900 A CN103541900 A CN 103541900A
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Abstract
The invention discloses a rotary type compressor, a refrigerant circulation system and a control method thereof. The rotary type compressor comprises a shell, a first flange, a cylinder, a second flange and a cover plate, wherein an air suction opening and an air exhaust opening which are communicated with the inner cavity of the cylinder are formed in the cylinder; a bypass opening communicated with the inner cavity of the cylinder is formed in the end face, which is opposite to the second flange, of the cylinder; a bypass runner and a bypass valve component for opening and closing the bypass runner are arranged on the second flange; one end of the bypass runner is communicated with the bypass opening, and the other end of the bypass runner is communicated with a low-pressure air-suction-side pipeline of the compressor through a bypass pipe positioned outside the shell; a control valve for adjusting the opening and the closing of the bypass pipe is arranged on the bypass pipe. Part of a bypass circulation flow path is positioned outside the shell of the compressor, so that the temperature rising, caused by circulation in a machine body, of bypass air is avoided, and the problem of air suction overheat caused by a fact that air bypasses to the air suction opening is finally solved; therefore, the efficiency of bypass starting of the compressor can be improved.
Description
Technical field
The present invention relates to compressor, particularly relate to a kind of rotary compressor, there is the refrigerant-cycle systems of this rotary compressor, and the controlling method of refrigerant-cycle systems.
Background technique
In prior art, some compressors change the capacity of compressor by controlling the rotating speed of compressor, but this need to possess complicated frequency conversion system, so manufacturing expense is quite expensive.In order to reduce manufacture cost, some compressors utilize bypass valve assembly to change compressor capacity, and this adjustable bypass valve assembly can be needed Exhaust Gas auto bypass to low pressure one side, to maintain low evaporating pressure.
Figure 1 shows that wherein a kind of structural representation of capacity adjusting mechanism, this bypass valve assembly is mainly by the valve opening 35 being arranged on the second flange, insert slidably guiding valve in valve opening 35 and form for the valve spring 82 of elastic support guiding valve, wherein, guiding valve comprises the first pressure unit 81a, the second pressure unit 81b and linkage unit 81c, back pressure hole 83a is connected with the public side outlet 95c of switching valve assembly 91 through public connecting tube 94, the high pressure side entrance 95a of switching valve assembly 91 is connected with the relief opening of compressor through high-pressure connecting pipe 92, the low voltage side entrance 95b of switching valve assembly 91 is connected with the intakeport of compressor through low-pressure connection tube 93.In oepration at full load situation, the public side of switching valve assembly 91 outlet 95c is connected with low voltage side entrance 95b, and the spring of the switching valve spring 98 of pressure unit 81a moves to the left side of accompanying drawing, and the first pressure unit 81a closes high pressure side bypass hole 33.When high pressure side bypass hole 33 closures, compressor oepration at full load.On the contrary, in no-load running situation, the public side outlet 95c of switching valve assembly 91 is connected with high pressure side entrance 95a, the spring of the switching valve spring 98 of pressure unit 81a moves to the right side of accompanying drawing, the linkage unit 81c of guiding valve 81 is between high pressure side bypass hole 33 and low pressure side bypass hole 34, thereby by-pass hole 33 and 34 is connected to each other, the full no-load running of compressor.There is following defect in this capacity adjusting mechanism:
(1) bypass gases opens and closes by guiding valve, and gas is bypassed to low-pressure cavity from hyperbaric chamber, and bypass cyclic process all completes in compressor.Because the pump housing is immersed in the middle of compressor oil sump, oil temperature when body is worked in the condition of high temperature, gas bypass circulates all the time under hot environment, therefore the gas temperature that is bypassed to intakeport place is very high, thereby cause suction superheat, pump body finally can be equilibrated at a higher temperature range, lubricants performance declines, pump housing wearing and tearing aggravation, compressor overall performance declines obviously.
(2) for guaranteeing the normal mobile working of guiding valve, guiding valve Yu Fa road should be designed with certain gap width, and therefore the gas in hyperbaric chamber is inevitably revealed to low-pressure cavity direction by circular lance.High pressure gas leakage expands after low-pressure cavity, causes the minimizing of low-pressure cavity gettering quantity, thereby the working efficiency under its non-bypass state is also affected.
(3) sliding valve structure opening and closing for controlling by-pass port, need to control by the high displacement transducer of precision, could obtain accurate control.Control mode is complicated, and cost is high.
Summary of the invention
For above-mentioned prior art present situation, first technical problem to be solved by this invention is, provides a kind of discharge capacity variable rotary compressor, and its performance is high, simple in structure, reliability is high, feasibility is strong.
Second technical problem to be solved by this invention is, a kind of refrigerant-cycle systems with above-mentioned rotary compressor is provided.
The 3rd technical problem to be solved by this invention is, a kind of controlling method of above-mentioned refrigerant-cycle systems is provided.
The present invention solves the technological scheme that above-mentioned first technical problem adopts: a kind of rotary compressor, comprise housing, be arranged in turn the first flange in this housing, cylinder, the second flange and cover plate, on described cylinder, be provided with intakeport and relief opening with its intracavity inter-connection, at described cylinder in the face of being provided with the by-pass port with its intracavity inter-connection on the end face of described the second flange, on described the second flange, be provided with bypass flow channel and for opening and closing the bypass valve assembly of this bypass flow channel, one end of this bypass flow channel is connected with described by-pass port, the other end is through being positioned at the bypass tube of described outside and the low pressure air suction lateral line of compressor is connected, and on described bypass tube, be provided with the control valve for regulating bypass tube to open and close.
In an embodiment, described by-pass port is angular cut therein.
In an embodiment, described by-pass port and described relief opening are staggeredly arranged on the circumferencial direction of described cylinder therein.
In an embodiment, described by-pass port and described intakeport are 20 to 340 degree along the angle α of the sense of rotation of compressor therein.
Therein in an embodiment, described bypass flow channel comprises and is arranged at described the second flanged surface to the bypass cavity on the end face of described cover plate, be arranged at the by-pass hole of this bypass cavity of connection on described the second flange and described by-pass port and be disposed radially the bypass side opening that is communicated with this bypass cavity and described bypass tube on described the second flange vertically, and the opening of described bypass cavity is by described cover plate for sealing.
Therein in an embodiment, described bypass valve assembly comprises the bypass valve block being arranged in described bypass cavity, this bypass valve block has fixed end and free end, and the fixed end of bypass valve block is fixed on described the second flange, and the free end of bypass valve block covers on the aperture of described by-pass hole.
In an embodiment, described bypass valve assembly also comprises the baffle plate of opening amplitude for limiting described bypass valve block therein.
In an embodiment, the sealed width L of described bypass cavity is greater than or equal to 2mm therein.
Therein in an embodiment, on described the first flange, be provided with the exhaust port that is connected with described relief opening and for opening and closing the outlet valve of this exhaust port.
In an embodiment, described outlet valve comprises exhaust valve plate therein, and this exhaust valve plate has fixed end and free end, and the fixed end of exhaust valve plate is fixed on described the first flange, and the free end of exhaust valve plate covers on described exhaust port.
In an embodiment, the diameter R2 of described exhaust port is less than the diameter of described by-pass hole R1 therein.
In an embodiment, the thickness of described exhaust valve plate is greater than the thickness of described bypass valve block therein.
In an embodiment, the rigidity of described exhaust valve plate is greater than the rigidity of described bypass valve block therein.
The present invention solves the technological scheme that above-mentioned second technical problem adopt: a kind of refrigerant-cycle systems, comprise compressor, four-way valve, vaporizer, condenser and throttle element, and described compressor is above-mentioned rotary compressor.
Therein in an embodiment, described refrigerant-cycle systems also comprises liquor separator, the intakeport of this liquor separator is connected with described four-way valve, the air outlet of this liquor separator is connected with the intakeport of described cylinder, and the outlet end of described bypass tube is connected on the suction port and the pipeline between described four-way valve of this liquor separator.
The present invention solves above-mentioned the 3rd technological scheme that technical problem adopts: a kind of controlling method of refrigerant-cycle systems, comprise the steps, when the absolute value of the temperature T 1 of object to be regulated and the poor Δ T of setting temperature T2 is less than or equal to 20 °, open described control valve.
Compared with prior art, rotary compressor provided by the present invention, refrigerant-cycle systems and controlling method thereof, because the part of bypass circulation stream is positioned at compression case external body, the temperature rise of having avoided bypass gases to produce in internal body circulation, finally can avoid gas bypass to arrive the suction superheat problem at intakeport place, efficiency when compressor bypass is opened obtains and improves; And, bypass tube adopts control valve to control, need in the second flange, not design complicated sensor, do not need to control by point-device displacement yet, the unlatching of controlling control valve by temperature transducer can reach controls the object that bypass flow channel opens and closes, therefore have advantages of simple in structure, cost is low, structural reliability and feasibility higher.
Accompanying drawing explanation
Fig. 1 is the structural representation of capacity adjusting mechanism of the prior art;
Fig. 2 is the structural representation of the pump housing of the rotary compressor in one of them embodiment of the present invention;
Fig. 3 is the main TV structure schematic diagram of the cylinder in Fig. 2;
Fig. 4 is the main TV structure schematic diagram of the second flange in Fig. 2;
Fig. 5 is the structural representation of the bypass valve block in Fig. 2;
Fig. 6 is the structural representation of the bypass valve assembly in Fig. 2;
Fig. 7 is the main TV structure schematic diagram of the first flange in Fig. 2;
Fig. 8 is the schematic diagram with the refrigerant-cycle systems of rotary compressor shown in Fig. 2;
Fig. 9 is rotary compressor shown in Fig. 2 and the inhalation temperature variation diagram of the rotary compressor with capacity adjusting mechanism shown in Fig. 1 when bypass adjusting work;
Figure 10 is rotary compressor shown in Fig. 2 and the exhaust gas temperature change figure of the rotary compressor with capacity adjusting mechanism shown in Fig. 1 when bypass adjusting work;
Figure 11 is rotary compressor shown in Fig. 2 and the refrigerating capacity figure of the rotary compressor with capacity adjusting mechanism shown in Fig. 1 when by-pass hole is closed;
Figure 12 is rotary compressor shown in Fig. 2 and the COP test result figure with the rotary compressor of capacity adjusting mechanism shown in Fig. 1.
Above in each figure, 10-compressor, 11-bent axle, 12-the first flange, 121-exhaust port, 13-cylinder, 131-intakeport, 132-relief opening, 133-by-pass port, 14-roller, 15-the second flange, 151-bypass cavity, 152-by-pass hole, 153-bypass side opening, 16-slide plate, 17-cover plate, 18-bypass valve block, 181-fixed end, 182-free end, 19-baffle plate, 20-four-way valve, 30-vaporizer, 40-throttle element, 50-condenser, 60-liquor separator, 70-control valve, 80-bypass tube.
Embodiment
Below with reference to accompanying drawing, also the present invention is described in detail in conjunction with the embodiments.It should be noted that, in the situation that not conflicting, the feature in following embodiment and embodiment can combine mutually.
As shown in Figure 3, the cylinder 13 of the present embodiment except thering is the intakeport 131 and relief opening 132 that existing cylinder is identical, also at cylinder 13 in the face of being provided with the by-pass port 133 with its intracavity inter-connection on the end face of the second flange 15.Preferably, described by-pass port 133 is angular cut.Preferably, described by-pass port 133 and described relief opening 132 are staggeredly arranged on the circumferencial direction of described cylinder 13.Because if by-pass port 133 is identical with relief opening 132 positions, compressor 10 pump housings can only be fully loaded with and zero load between switching, can not embody the advantage of variable volume compressor.Preferably, described by-pass port 133 and described intakeport 131 are 20 to 340 degree along the angle α of the sense of rotation of compressor 10.According to bypass effect and different air conditioning condition variation analysis, obtain, for different model air-conditioning system when α be that 120 to 270 effects that obtain while spending are better.
As shown in Figure 4, on the second flange 15, be provided with bypass flow channel.Preferably, bypass flow channel comprises and is arranged at described the second flange 15 in the face of the bypass cavity 151 on the end face of described cover plate 17, be arranged at the by-pass hole 152 of this bypass cavity 151 of connection on described the second flange 15 and described by-pass port 133 and be disposed radially the bypass side opening 153 being connected with bypass cavity 151 on described the second flange 15 vertically, because the volume of bypass cavity 151 is when too small, during bypass gases circulation, produce the larger loss of holding back, therefore for reducing the loss of bypass cavity 151, its volume should be greater than the volume of cylinder bypass gases.Because the second flange of existing compressor is used for getting rid of pressurized gas, gas and pump housing pressure of ambient gas that the second flange is got rid of are high pressure, therefore not high to sealing requirements.And the bypass gases of the present embodiment is low pressure gas, have larger pressure reduction with pressurized gas in pump housing environment, so the second flange 15 in the present embodiment adopts recessed structure to coordinate with cover plate 17, make the best sealing effect of bypass cavity 151 acquisition, avoid gas leakage.Preferably, the sealed width L of bypass cavity 151 is greater than or equals 2mm.Described bypass side opening 153 is through being positioned at the bypass tube 80 of described outside and the low pressure air suction lateral line of compressor 10 is connected (as shown in Figure 8), and on described bypass tube 80, be provided with the control valve 70 for regulating bypass tube 80 to open and close, control valve 70 preferably adopts solenoid valve.During bypass adjusting work, a part of gas flows into the by-pass hole 152 of the second flange 15 from by-pass port 133, enters the bypass cavity 151 of the second flange 15, flows into the bypass side opening 153 of the second flange 15, by external bypass tube 80 tunnels, finally flows into liquor separator 60.Due to, the part of bypass circulation stream is positioned at compressor 10 outside, the temperature rise of avoiding bypass gases to produce in internal body circulation, finally can avoid gas bypass to arrive the suction superheat problem at intakeport 131 places, and efficiency when compressor 10 bypass are opened obtains and improves.And, bypass tube 80 adopts electromagnetic valve, compare with existing scheme, need to be at the complicated sensor of the interior design of the second flange 15, do not need to control by point-device displacement yet, the unlatching of controlling solenoid valve by temperature transducer can reach controls the object that bypass flow channel opens and closes, therefore have advantages of simple in structure, cost is low.
Bypass valve assembly is for controlling the switching of by-pass hole 152.As shown in Figure 5, Figure 6, the described bypass valve assembly of the present embodiment comprises the bypass valve block 18 being arranged in described bypass cavity 151, this bypass valve block 18 has fixed end 181 and free end 182, the fixed end 181 of bypass valve block 18 is fixed on described the second flange 15, and the free end 12 of bypass valve block 18 covers on the aperture of described by-pass hole 152.When the gas pressure at the aperture place of by-pass hole 152 is during higher than bypass valve block 18 back pressure, bypass valve block 18 is upspring, and bypass gases can the interior discharge of bypass cavity 151 to the second flange 15 by by-pass hole 152.Otherwise when by-pass hole 152 pressure are less than bypass valve block 18 back pressure, bypass valve block 18 cannot flick.By-pass hole 152 adopts the control program of elasticity bypass valve block 18, the leakage loss while avoiding non-bypass work.And because bypass valve block 18 is a kind of one-way valves, gas flows from cylinder 13 inside to bypass cavity 151 only, bypass valve block 18 free ends 12 can thoroughly solve gas backflow problem with the adequate closure in the aperture of by-pass hole 152.Preferably, described bypass valve assembly also comprises baffle plate 19, and baffle plate 19 and bypass valve block 18 are fixed on the second flange 15 places by rivet, and baffle plate 19 is for limiting the unlatching amplitude of bypass valve block 18, to prevent that excessive unlatching of bypass valve sheet 18 from causing part breaking.
The first flange 12 is for getting rid of pressurized gas.As shown in Figure 7, on the first flange 12, be provided with the exhaust port 121 that is connected with described relief opening 132 and for opening and closing the outlet valve (not shown on figure) of this exhaust port 121, described outlet valve comprises exhaust valve plate, this exhaust valve plate has fixed end and free end, the fixed end of exhaust valve plate is fixed on described the first flange, and the free end of exhaust valve plate covers on described exhaust port.For the situation of avoiding occurring that bypass valve block 18 and exhaust valve plate are opened simultaneously, the diameter R1 of described by-pass hole 152 is greater than the diameter R2 of described exhaust port 121.The bypass gases pressure suffered due to bypass valve block 18 is less, suffered impulsive load is little compared with exhaust valve plate, therefore for improving structural behaviour, reducing the bypass gases drag losses that bypass valve block 18 produces, the thickness of bypass valve block 18 is less than the thickness of exhaust valve plate, equally, the rigidity of described exhaust valve plate is greater than the rigidity of described bypass valve block 18.
In another embodiment of the present invention, a kind of refrigerant-cycle systems (as air-conditioning, heat pump water heater etc.) is provided, as shown in Figure 8, refrigerant-cycle systems comprises compressor 10, four-way valve 20, vaporizer 30, condenser 50 and throttle element 40, and described compressor 10 adopts the rotary compressor 10 of above-described embodiment.Compressor 10 also comprises liquor separator 60, and this liquor separator 60 has suction port and air outlet, and the air outlet of liquor separator 60 is connected with the intakeport 131 of described cylinder 13, and the outlet end of described bypass tube 80 is connected with the suction port of this liquor separator 60.
In another embodiment of the present invention, provide a kind of controlling method of above-mentioned refrigerant-cycle systems, when the temperature T 1 of object to be regulated, (when refrigerant-cycle systems is air-conditioning, T1 is indoor environment temperature; When refrigerant-cycle systems is heat pump water heater, T1 is the temperature of water to be heated in water tank) while being less than or equal to 20 ° with the absolute value of the poor Δ T of setting temperature T2, opening described control valve 70, thereby open bypass flow path.
The rotary compressor 10 (hereinafter to be referred as the present embodiment) that the embodiment of the present invention provides is compared with the existing rotary compressor (hereinafter to be referred as prior art) described in background technique, has following beneficial effect:
(1) contrast the present embodiment and the overheated variation that causes inhalation temperature of two kinds of technological scheme bypass gases of prior art, result as shown in Figure 9.As can be seen from the figure, the present embodiment causes air-breathing excess temperature much smaller than prior art, be therefore conducive to improve the pump housing service life (in figure, the temperature variation curve that square line is the present embodiment; Triangle line is the temperature variation curve of prior art; Temperature variation curve when rhombus line is normal operation).
(2) the Exhaust temperature rise amount that contrast the present embodiment and prior art two schemes suction superheat cause, result as shown in figure 10.As can be seen from the figure, the delivery temperature of the present embodiment is less than prior art, can reduce the temperature of compressor inner body environment, thus raising compressor electric motor reliability (in figure, the temperature variation curve that square line is the present embodiment; Triangle line is the temperature variation curve of prior art; Temperature variation curve when rhombus line is normal operation).
(3) as can be seen from Figure 11, because prior art scheme exists more serious leakage loss, and the present embodiment scheme performance when by-pass port is closed completes consistent with normal model machine substantially, show in refrigerating capacity when bypass valve cuts out higher than prior art scheme (in figure, count from left to right, to be the present embodiment close and refrigeration and heating capacity when valve opens at valve for first group and second group of bar chart, refrigeration and heating capacity that the 3rd group of bar chart is prior art when valve pass and valve are opened).
(4) final, as shown in figure 12, the COP of the present embodiment is better than prior art scheme, and (in figure, count from left to right, first and second cylinder represent the COP value of the present embodiment, and the 3rd cylinder represents the COP value of prior art.
As can be seen here, the rotary compressor that the embodiment of the present invention provides, has advantages of that performance is high, simple in structure, reliability is high, feasibility is strong.
The above embodiment has only expressed several mode of execution of the present invention, and it describes comparatively concrete and detailed, but can not therefore be interpreted as the restriction to the scope of the claims of the present invention.It should be pointed out that for the person of ordinary skill of the art, without departing from the inventive concept of the premise, can also make some distortion and improvement, these all belong to protection scope of the present invention.Therefore, the protection domain of patent of the present invention should be as the criterion with claims.
Claims (16)
1. a rotary compressor, comprise housing, be arranged in turn the first flange in this housing, cylinder, the second flange and cover plate, on described cylinder, be provided with intakeport and relief opening with its intracavity inter-connection, it is characterized in that, at described cylinder in the face of being provided with the by-pass port with its intracavity inter-connection on the end face of described the second flange, on described the second flange, be provided with bypass flow channel and for opening and closing the bypass valve assembly of this bypass flow channel, one end of this bypass flow channel is connected with described by-pass port, the other end is through being positioned at the bypass tube of described outside and the low pressure air suction lateral line of compressor is connected, and on described bypass tube, be provided with the control valve for regulating bypass tube to open and close.
2. rotary compressor according to claim 1, is characterized in that, described by-pass port is angular cut.
3. rotary compressor according to claim 1, is characterized in that, described by-pass port and described relief opening are staggeredly arranged on the circumferencial direction of described cylinder.
4. rotary compressor according to claim 3, is characterized in that, described by-pass port and described intakeport are 20 to 340 degree along the angle α of the sense of rotation of compressor.
5. according to the rotary compressor described in any one in claim 1 to 4, it is characterized in that, described bypass flow channel comprises and is arranged at described the second flanged surface to the bypass cavity on the end face of described cover plate, be arranged at the by-pass hole of this bypass cavity of connection on described the second flange and described by-pass port and be disposed radially the bypass side opening that is communicated with this bypass cavity and described bypass tube on described the second flange vertically, and the opening of described bypass cavity is by described cover plate for sealing.
6. rotary compressor according to claim 5, it is characterized in that, described bypass valve assembly comprises the bypass valve block being arranged in described bypass cavity, this bypass valve block has fixed end and free end, the fixed end of bypass valve block is fixed on described the second flange, and the free end of bypass valve block covers on the aperture of described by-pass hole.
7. rotary compressor according to claim 6, is characterized in that, described bypass valve assembly also comprises the baffle plate of opening amplitude for limiting described bypass valve block.
8. rotary compressor according to claim 5, is characterized in that, the sealed width L of described bypass cavity is greater than or equal to 2mm.
9. rotary compressor according to claim 5, is characterized in that, is provided with the exhaust port that is connected with described relief opening and for opening and closing the outlet valve of this exhaust port on described the first flange.
10. rotary compressor according to claim 9, it is characterized in that, described outlet valve comprises exhaust valve plate, and this exhaust valve plate has fixed end and free end, the fixed end of exhaust valve plate is fixed on described the first flange, and the free end of exhaust valve plate covers on described exhaust port.
11. rotary compressors according to claim 10, is characterized in that, the diameter R2 of described exhaust port is less than the diameter of described by-pass hole R1.
12. rotary compressors according to claim 10, is characterized in that, the thickness of described exhaust valve plate is greater than the thickness of described bypass valve block.
13. rotary compressors according to claim 10, is characterized in that, the rigidity of described exhaust valve plate is greater than the rigidity of described bypass valve block.
14. 1 kinds of refrigerant-cycle systems, comprise compressor, four-way valve, vaporizer, condenser and throttle element, it is characterized in that, described compressor is the rotary compressor as described in any one in claim 1 to 13.
15. refrigerant-cycle systems according to claim 14, it is characterized in that, also comprise liquor separator, the intakeport of this liquor separator is connected with described four-way valve, the air outlet of this liquor separator is connected with the intakeport of described cylinder, and the outlet end of described bypass tube is connected on the suction port and the pipeline between described four-way valve of this liquor separator.
The controlling method of 16. 1 kinds of refrigerant-cycle systems as claimed in claim 14, is characterized in that, comprises the steps, when the absolute value of the temperature T 1 of object to be regulated and the poor Δ T of setting temperature T2 is less than or equal to 20 °, opens described control valve.
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| CN201210242109.7A CN103541900B (en) | 2012-07-12 | 2012-07-12 | Rotary Compressor, refrigerant-cycle systems and control method thereof |
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| CN201210242109.7A CN103541900B (en) | 2012-07-12 | 2012-07-12 | Rotary Compressor, refrigerant-cycle systems and control method thereof |
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| CN103541900B CN103541900B (en) | 2016-11-23 |
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Cited By (5)
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| CN104976128A (en) * | 2015-07-15 | 2015-10-14 | 广东美芝制冷设备有限公司 | Rotary compressor and compression assembly thereof |
| CN105091464A (en) * | 2015-08-18 | 2015-11-25 | 合肥华凌股份有限公司 | Refrigerating system of refrigerator |
| CN106705299A (en) * | 2016-12-30 | 2017-05-24 | 广东申菱环境系统股份有限公司 | Subway station deep well cooling direct expansion air conditioner and control method thereof |
| CN107355563A (en) * | 2016-05-09 | 2017-11-17 | 浙江三花制冷集团有限公司 | Reversal valve and there is its refrigeration system |
| WO2024198315A1 (en) * | 2023-03-29 | 2024-10-03 | 约克广州空调冷冻设备有限公司 | Heat pump system |
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| CN103541900B (en) | 2016-11-23 |
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