CN102748289A - Double-cylinder rotary compressor - Google Patents
Double-cylinder rotary compressor Download PDFInfo
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- CN102748289A CN102748289A CN2011100983790A CN201110098379A CN102748289A CN 102748289 A CN102748289 A CN 102748289A CN 2011100983790 A CN2011100983790 A CN 2011100983790A CN 201110098379 A CN201110098379 A CN 201110098379A CN 102748289 A CN102748289 A CN 102748289A
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Abstract
The invention discloses a double-cylinder rotary compressor. The double-cylinder rotary compressor is characterized in that a motor portion and a compressing mechanism are arranged in a sealed housing; the compressing mechanism comprises a first cylinder with a first compression cavity, a second cylinder with a second compression cavity, and a middle division plate which is arranged between the first cylinder and the second cylinder and is provided with a centre hole; a first piston and a first slip sheet are arranged in the first compression cavity; a second piston and a second slip sheet are arranged in the second compression cavity; the first piston and the second piston are driven simultaneously by a crankshaft; a main bearing and a supplementary bearing for supporting the crankshaft are arranged respectively at sides of the first cylinder and the second cylinder; the middle division plate comprises at least a first flat plate and a second flat plate connected to the first flat plate; one or more exhaust valves are arranged in the first flat plate or/and the second flat plate; and the first flat plate and the second flat plate are connected together at least around the centre hole. The double-cylinder rotary compressor has the advantages of simple and reasonable structure, flexible operation, high energy efficiency ratio, long service life and wide application scope.
Description
Technical field
The present invention relates to a kind of rotary compressor, particularly a kind of twin-tub rotation-type compressor.
Background technique
Pressure in the muffler chamber in the central diaphragm that is made up of two flat-shaped parts is high pressure; When be positioned at central diaphragm above the first cylinder compression chamber or below the pressure of the second cylinder compression chamber when changing; Pressure difference between the pressure in the pressure in the muffler chamber and the first cylinder compression chamber or the second cylinder compression chamber also changes thereupon, and central diaphragm expands distortion according to the pressure difference that changes.The central diaphragm of this dilatancy makes the gap smaller between the face that slides up and down of piston and slide plate in first cylinder or second cylinder, causes the piston sintering easily or causes the slippage loss increase and then compressor efficiency reduces.
Patent documentation 1: Japanese Patent Laid is driven the 1998-213087 rotary compressor.
Patent documentation 2: Chinese patent publication number CN1761817A rotary closed type compressor and refrigerating circulatory device.
Patent documentation 3: Japanese Patent Laid is opened the 2008-128231 volume variable rotating compressor.
Summary of the invention
The object of the invention aims to provide a kind of simple and reasonable, flexible operation, Energy Efficiency Ratio height, long service life, twin-tub rotation-type compressor applied widely, to overcome deficiency of the prior art.
A kind of twin-tub rotation-type compressor by this purpose design; Be provided with motor section and compressing mechanism in the housing of sealing; Compressing mechanism comprise first cylinder that has first compression chamber, have second cylinder of second compression chamber and be folded in first cylinder and second cylinder between and have a central diaphragm of center hole; Be provided with the first piston and first slide plate in first compression chamber; Be provided with second piston and second slide plate in second compression chamber, bent axle drives the first piston and second piston simultaneously, is used to support the main bearing of bent axle and the side that supplementary bearing is separately positioned on first cylinder and second cylinder; Its structure characteristic is that central diaphragm comprises first dull and stereotyped and second flat board that links together at least, is provided with outlet valve in first flat board and/or second flat board.
Said first flat board and second flat board being joined together around center hole at least.
The layout of the groove that is provided with on the convexity that any in said first dull and stereotyped and second flat board goes up setting and the another one is consistent, is joined together at the inside of this groove first flat board and second flat board.
Said convexity comprises the annular protrusion in the outside that is arranged on the center hole on second flat board, and the arranged outside of this annular protrusion has the conic convex more than two.
Said groove comprises the circular groove in the outside that is arranged on the center hole on first flat board, and the arranged outside of this circular groove has the circular trough more than two.
Said central diaphragm adopts sintered alloy machine shaping.
The present invention will be through constituting first dull and stereotyped and second flat board the linking into an integrated entity at center hole of central diaphragm on every side; Make the rigidity of central diaphragm improve greatly; Therefore, the dilatancy of taking in the muffler chamber of exhaust valve component can diminish, can effectively avoid in first cylinder or second cylinder piston and slide plate slide up and down the gap smaller between the face; Reduce the sliding friction loss, improve the working efficiency of compressor and the working life that prolongs compressor.
The present invention is not only applicable to twin-tub rotation-type compressor, and is applicable to three cylinder rotary compressors, and it has simple and reasonable, flexible operation, Energy Efficiency Ratio height, long service life, advantage of wide range of application.
Description of drawings
Fig. 1 is the broken section structural representation of embodiments of the invention 1.
Fig. 2 is the broken section structure for amplifying schematic representation of the compressing mechanism among the embodiment 1.
Fig. 3 is the main TV structure schematic representation of the central diaphragm among the embodiment 1.
Fig. 4 is that A-A among Fig. 3 is to the sectional structure schematic representation.
Fig. 5 is the dull and stereotyped main TV structure schematic representation of first among the embodiment 1.
Fig. 6 is that Y-Y among Fig. 5 is to the sectional structure schematic representation.
Fig. 7 is the dull and stereotyped main TV structure schematic representation of second among the embodiment 1.
Fig. 8 is that Z-Z among Fig. 7 is to the sectional structure schematic representation.
Fig. 9 is the main TV structure schematic representation of the outlet valve among the embodiment 1.
Figure 10 is the main TV structure schematic representation of the limited valve among the embodiment 1.
Figure 11 is the structural representation of the exhaust valve component among the embodiment 1.
Figure 12 is the dull and stereotyped and broken section structure for amplifying schematic representation of second flat board before assembling of first among the embodiment 1.
Figure 13 is the dull and stereotyped and broken section structure for amplifying schematic representation of second flat board after assembling of first among the embodiment 1.
Figure 14 is that X-X among Fig. 2 is to the broken section structural representation.
Figure 15 is the cross-sectional view of the active force that produces of the muffler chamber of the central diaphragm among the embodiment 1.
Figure 16 is the structural representation of embodiment 2 central diaphragm.
Figure 17 is that B-B among Figure 16 is to the broken section structural representation.
Among the figure: R is a rotary compressor, and 2 is housing, and 4 is compressing mechanism, and 5 is motor section, and 13a is first cylinder, and 13b is second cylinder, and 14a is first compression chamber; 14b is second compression chamber, and 17a is a first piston, and 17b is second piston, and 18a is first slide plate, and 18b is second slide plate, and 21 is bent axle; 25 is main bearing, and 26 is supplementary bearing, and 31 is first venting gas appliance, and 32 is second venting gas appliance, and 35 is bottom silencer, and 100 is central diaphragm; 101 is center hole, and 102 is muffler chamber, and 110 is first flat board, and 112 is circular groove, and 113 are the exhaust valve pool, and 114 is locking groove; 115 is exhaust port, and 116 is the cylinder screw hole, and 117 is screw, and 118 is exhaust passageway, and 119 is circular trough, and 120 is second flat board; 122 is annular protrusion, and 123 is conic convex, and 124 is the valve screw hole, and 130 is exhaust valve component, and 131 is outlet valve, and 132 is limited valve; 132a is a stop protrusion, and 134 is the valve screw, and 135 is the valve fixed hole, and S is spot welding, and H is a hyperbaric chamber, and L is a low pressure chamber.
Embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is further described.
Embodiment 1
Referring to twin-tub rotation-type compressor R shown in Figure 1, motor section 5 of taking in the housing 2 by sealing and the compressing mechanism 4 that disposes below it are formed.Compressing mechanism 4 is made up of the first cylinder 13a and two cylinders of the second cylinder 13b, the central diaphragm 100 of separating them, bent axle 21, main bearing 25 and supplementary bearing 26 etc.The periphery of the main bearing 25 of compressing mechanism 4 is fixed on the inwall of housing 2.
Referring to Fig. 2, shown the detailed structure of compressing mechanism 4.Compressing mechanism 4 disposes: in the first compression chamber 14a that the central authorities of the first cylinder 13a and the second cylinder 13b constitute respectively and second compression chamber, make the first piston 17a of eccentric operating and the reciprocating first slide plate 18a and the second slide plate 18b of periphery butt of the second piston 17b and these pistons.The bent axle 21 that drives these two pistons is through main bearing 25 and supplementary bearing 26 sliding supports.
Since the height of the first cylinder 13a greater than with the height of the second cylinder 13b, so the discharge capacity of the first compression chamber 14a than the second compression chamber 14b greatly.Main bearing 25 is taken in first venting gas appliance 31 of discharging the gas in the first compression chamber 14a; Supplementary bearing 26 is taken in second venting gas appliance 32 of discharging the gas in the second compression chamber 14b, and central diaphragm 100 is taken in the exhaust valve component 130 of discharging the gas in the first compression chamber 14a.Therefore, two exhaust passages forming by first venting gas appliance 31 and exhaust valve component 130 of the first compression chamber 14a.
The pressurized gas of the first compression chamber 14a are through two exhaust passages; (1) is discharged to the inside of housing 2 from first venting gas appliance 31; (2) exhaust valve components 130 that are equipped with from central diaphragm 100 inside and muffler chamber 102 are discharged in the housing 2 from main bearing 25 via exhaust passageway 118.The pressurized gas of the second compression chamber 14b via the bottom silencer 35 that is arranged on the supplementary bearing 26, are discharged to the inside of housing 2 from second venting gas appliance 32 from the top of main bearing 25.Wherein, exhaust passageway 118 is arranged in central diaphragm 100, the first cylinder 13a and the main bearing 25.
Referring to Fig. 3-Fig. 4, the formation of central diaphragm 100 is described.Central diaphragm 100 is made up of first dull and stereotyped 110 and second dull and stereotyped 120 these two flat-shaped parts, in the muffler chamber 102 that is surrounded jointly by first dull and stereotyped 110 and second flat board 120, has taken in exhaust valve component 130.
First dull and stereotyped 110 and second dull and stereotyped 120 is joined together around center hole 101 at least.The layout of the groove that is provided with on the convexity of setting and the another one on any in first dull and stereotyped 110 and second dull and stereotyped 120 is consistent, is joined together in the inside of this groove.
Said first dull and stereotyped 110 and second dull and stereotyped 120 is joined together around center hole 101 at least.Be provided with the cylinder screw hole 116 more than two around first dull and stereotyped 110 the center hole 101 with around second dull and stereotyped 120 the center hole 101, just can first dull and stereotyped 110 and second flat board 120 be linked together through screw.
Said convexity comprises the annular protrusion 122 in the outside that is arranged on the center hole 101 on second dull and stereotyped 120, and the arranged outside of this annular protrusion 122 has the conic convex 123 more than two; Said groove comprises the circular groove 112 in the outside that is arranged on the center hole 101 on first dull and stereotyped 110, and the arranged outside of this circular groove 112 has the circular trough 119 more than two.
First dull and stereotyped 110 and second dull and stereotyped 120 through method moulding such as sintered alloy and punching presses, partly appended machining.After first flat board 110 has been taken in exhaust valve component 130, be connected with second dull and stereotyped 120 in the position of regulation.
Be described below, connect annular protrusion 122 and six conic convex 123 of the second dull and stereotyped periphery configuration of the outside configuration of second dull and stereotyped 120 center hole 101 through projection welding, accomplish the connection operation.
Referring to Fig. 5-Fig. 6, be first dull and stereotyped 110 detailed structure.The first circular dull and stereotyped 110 process sintered alloy machine shapings; First dull and stereotyped 110 center portion is provided with center hole 101; Be provided with exhaust valve pool 113 and exhaust port 115 in the muffler chamber 102; Exhaust passageway 118 is communicated with muffler chamber 102, and the arranged outside of center hole 101 has the periphery of circular groove 112, the first dull and stereotyped 110 to be provided with six circular troughs 119 and five cylinder screw holes 116.
Referring to Fig. 7-second flat board 120 shown in Figure 8; Be provided with exhaust passageway 118 and five cylinder screw holes 116 of being communicated with muffler chamber 102; The arranged outside that is positioned at the center hole 101 of second dull and stereotyped 120 central part has annular protrusion 122, and the periphery of annular protrusion 122 is provided with six conic convex 123.They are configured in consistent location with passage, hole, the groove of first flat board 110 that is connected in pairs.The center of the screw 117 on the valve screw hole 124 and first dull and stereotyped 110 is consistent.
Certainly, the groove that is arranged on first flat board being exchanged with the convexity that is arranged on second flat board, also is to realize the object of the invention,
Referring to Fig. 9-Figure 11, shown the formation and the erection drawing of exhaust valve component 130.Exhaust valve component 130, assembling is accomplished in the S position of the S position of spot welding outlet valve 131 and limited valve 132 like a cork.Spot welding can not only ensure long running, can also transfer cores to outlet valve 131 and limited valve 132, state after exhaust valve component 130 is fixed to first dull and stereotyped 110 on become easy.
The exhaust valve component 130 that assembling is accomplished is configured in the inside like first dull and stereotyped 110 the exhaust valve pool 113 of Fig. 5-shown in Figure 6.At this moment, because the locking groove of the stop protrusion 132a of exhaust valve component 130 and exhaust valve pool 113 114 cooperates, exhaust valve component 130 correctly and can not be incorporated in the locking groove 114 owing to vibration is moved.In addition, valve screw 134 has been fixed exhaust valve part 130 when the final operation of manufacturing of exhaust valve component 130.
Between first dull and stereotyped 110 and second dull and stereotyped 120, assembling under the state of exhaust valve component 130; Annular protrusion 122 second dull and stereotyped 120 is consistent with conic convex 123; Under the consistent state of first dull and stereotyped 110 circular groove 112 and circular trough 119, first flat board and second flat board are carried out projection welding.The result is that first dull and stereotyped 110 and second dull and stereotyped 120 in periphery and firm the welding together of center hole.
Shown in the details of the welding portion 12-13 with the aid of pictures.Shown in Figure 12 is before welding, and shown in Figure 13 is after welding.The projection length of conic convex 123, the degree of depth of relative circular trough 119, the setting of welding surplus is longer.Therefore, because the welding of the bottom of the tip of conic convex 123 and circular trough 119, the surface of contact to first dull and stereotyped 110 and second dull and stereotyped 120 does not have harmful effect, can guarantee closely to be fixed together.Because this effect, can not only prevent from muffler chamber 102 to center hole 101 gas leakage, the precision in the time of can also maintaining next grinding process improves.
Next, the central diaphragm 100 that take in exhaust valve component 130, accomplish to connect in order to improve the plane precision of two fixing on the plane with the first cylinder 13a and second cylinder 13b faces, has appended grinding process.As a result, guaranteed the precision of the outer side plane of central diaphragm 100.
, from exhaust port 115 inject cleaning solution, clean exhaust valve component 130 and muffler chamber 102, remove the grinding powder thereafter.Cleaning solution is recovered from exhaust passageway 118.At this moment,, have some spaces to turn round up and down not by the exhaust valve component 130 of screw, thus can clean exhaust valve component around.
After washing process is accomplished, insert valve screws 134, be fixed on exhaust valve part 130 117 li of the screws of configuration on first dull and stereotyped 110 from the valve screw hole 124 of second dull and stereotyped 120 configurations.Assembling to this central diaphragm 100 is all accomplished.At this moment, exhaust valve part 130 has been fixed the position by locking groove 114, so can automatically be fixed on correct position by valve screw 134.
The full periderm in first dull and stereotyped 110 and second dull and stereotyped 120 and center hole 101 outsides of the central diaphragm 100 that is linked and packed like this fuses, and central diaphragm 100 can be regarded a structure as.Therefore rigidity is very high, is not easy distortion.
Figure 14 is that X-X among Fig. 2 is to the cross section.Be separated into low pressure chamber L and hyperbaric chamber H to the second compression chamber 14b with the slide plate 18b of the second piston 17b reciprocating operation of eccentric operating.The capacity of low pressure chamber L is that slide plate is maximum to lower dead center (when the slide plate path increment is zero), and at this moment, the pressure of whole compression chamber is low-pressure lateral pressure Ps.The first piston 17a of eccentric operating in the first compression chamber 14a of the first cylinder 13a with respect to the second piston 17b, is usually located at the phase angle that differs 180 degree.
Referring to Figure 15, rotary compressor R is on-stream, the first compression chamber 14a and the second compression chamber 14b and and be configured in the pressure dependence of muffler chamber 102 therebetween.The pressure of muffler chamber 102 be usually with the interior the same or high some high side pressure Pd of pressure of pressure of housing 2.The pressure of the first compression chamber 14a and the second compression chamber 14b alternately repeats to change high side pressure Pd and low-pressure lateral pressure Ps.
When the pressure of arbitrary compression chamber becomes low-pressure lateral pressure Ps, and the pressure difference Δ P between the pressure P d of muffler chamber 102 is maximum, has produced simultaneously from maximum force Fa or the Fb of muffler chamber 102 to this compression chamber.This maximum force Fa or Fb among bent axle 21 turns around, in the first compression chamber 14a and the second compression chamber 14b, respectively alternately produce once in twin-tub rotation-type compressor.
This maximum force Fa or Fb become makes central diaphragm 100 distortion, to the crooked active force of compression chamber, and is the stopping power to the piston of on central diaphragm 100, doing to slide.But, the incorporate central diaphragm 100 among the aforesaid embodiment 1, rigidity is fully high, can prevent trouble before it happens.
In addition, according to the announcement technology of patent documentation 1, the first dull and stereotyped and second dull and stereotyped not joint.In such occasion, because the existence of directed force F a and Fb, first flat board is to the distortion of first compression chamber, one side, and second platen surface is out of shape to the second compression chamber 14b, one side.At this moment, between two central diaphragms of center hole part, the gap occurred, muffler chamber is expanded as expanding.
Present embodiment 1 and patent documentation 1 connecting first dull and stereotyped 110 and second dull and stereotyped 120 adopt unconnected first flat board and the second dull and stereotyped design proposal to make comparisons, and its rigidity difference is with respect to the former, and it is 1/8 that the latter's design is estimated.That is to say be divided into two flat boards to central diaphragm after, dull and stereotyped separately rigidity descends significantly, the latter's amount of deformation increases greatly.Therefore, just produced following problems.
The face that slides up and down of piston respectively and the gap between bearing plane and the central diaphragm be set at usually depth pistion 0.05～0.1% between, just be piston slide up and down length between the face 0.05～0.1% between.For example, if the height of piston is 20mm, the gap is 10～20 μ m, and this gap is the total of two side clearances of piston.
The first dull and stereotyped perhaps amount of deformation of second flat board according to active force; If surpassed the value of above-mentioned two side clearances; The glade plane space of the face that slides up and down of piston has not just had, and piston not only can not turn round, and also can cause the sintering wearing and tearing between piston and bearing plane or the central diaphragm.And, even amount of deformation when the value of two above-mentioned side clearances is following, if the value of amount of deformation is bigger, because the frictional loss of piston and central diaphragm, the efficient of compressor will descend.
In addition, the capacity controlled rotary compressor shown in patent documentation 2 or patent documentation 3, static through the slide plate that makes reciprocating operation in second cylinder, be fixed on lower dead center, thereby make the idle running of second piston.Therefore, stopped the compression of second cylinder.
At this moment, second piston dallies in second compression chamber, and irrelevant with the running of second piston, second compression chamber is generally low voltage side Ps.At this moment, muffler chamber is maximum to the directed force F b of second compression chamber.So, central diaphragm dull and stereotyped like first in the patent documentation 1 and that second flat board does not have to engage is applied in the design of above-mentioned capacity controlled rotary compressor, the running clearance of the face that slides up and down of piston can be strict more value.
In embodiment 1, being connected of the conic convex 123 that disposes about the annular protrusion 122 and the periphery of the outside of center hole 101 configuration, in the assembling of compressing mechanism, the periphery of central diaphragm is fixed between the first cylinder 13a and the second cylinder 13b.Therefore, even omitted the connection of this periphery, very big influence can not arranged to the rigidity of central diaphragm 100 yet.But, at this moment just be necessary to confirm the precision of central diaphragm 100 at grinding process.
In order to improve the rigidity of central diaphragm 100, do not connect first dull and stereotyped 110 and second dull and stereotypedly 120, though the means that increase their thickness are arranged, the thickness increase of central diaphragm 100 will increase the size between the upper end of lower end and supplementary bearing 26 of main bearing 25.
Along with the increase of size, the axle base that drives the bent axle 21 of two pistons will be elongated, will take place because the rigidity of bent axle 21 descends, and the amplitude of running becomes big problem.Therefore, the thickness of central diaphragm 100 is that relation according to the rigidity of central diaphragm and bent axle 21 is limited in certain limit.Therefore, in embodiment 1, in the thickness of restriction first dull and stereotyped 110 and second dull and stereotyped 120, they are connected is best.
In addition, in embodiment 1, first dull and stereotyped 110 and the second dull and stereotyped 120 usefulness projection weldings are engaged, still, as substitute technology, for example, if use laser bonding, it is possible using still less heat input to weld, and necessary convexity and groove can also omit projection welding the time.Therefore, the technology that discloses during the present invention is not only above-mentioned constitutes, and in the scope of main idea of the present invention, can implement various distortion.
Referring to Figure 16-Figure 17, in the present embodiment, when reducing to be provided with first dull and stereotyped 110 thickness of exhaust port 115 and outlet valve 131, the thickness thickening second dull and stereotyped 120, formation limited valve 132 on second dull and stereotyped 120 then.Then this first flat board is connected as the method among the embodiment 1 with second flat board, accomplishes central diaphragm 100.
In embodiment 2, change first dull and stereotyped 110 and second dull and stereotyped 120 thickness, on second dull and stereotyped 120, can dispose limited valve.According to embodiment 2, can omit exhaust valve component necessary among the embodiment 1.
Certainly, through changing the thickness of first dull and stereotyped 110 and second flat board 120, on first flat board, also can dispose limited valve, thereby also can realize the object of the invention.
All the other are not stated part and see embodiment 1, no longer repeat.
Claims (6)
1. twin-tub rotation-type compressor; Be provided with motor section (5) and compressing mechanism (4) in the housing (2) of sealing; Compressing mechanism (4) comprise first cylinder (13a), second cylinder (13b) that has second compression chamber (14b) that has first compression chamber (14a) and be folded in first cylinder (13a) and second cylinder (13b) between and have a central diaphragm (100) of center hole (101); Be provided with first piston (17a) and first slide plate (18a) in first compression chamber (14a); Be provided with second piston (17b) and second slide plate (18b) in second compression chamber (14b); Bent axle (21) drives first piston (17a) and second piston (17b) simultaneously; Be used to support the main bearing (25) of bent axle (21) and the side that supplementary bearing (26) is separately positioned on first cylinder (13a) and second cylinder (13b), it is characterized in that central diaphragm (100) comprises first flat board (110) and second flat board (120) that links together at least, is provided with outlet valve (131) in first flat board (110) and/or second flat board (120).
2. twin-tub rotation-type compressor according to claim 1 is characterized in that said first flat board (110) and second flat board (120) are joined together at least around center hole (101).
3. twin-tub rotation-type compressor according to claim 1; The layout of the groove that is provided with on the convexity that it is characterized in that being provided with on any in said first flat board (110) and second flat board (120) and the another one is consistent, is joined together at the inside of this groove first flat board (110) and second flat board (120).
4. twin-tub rotation-type compressor according to claim 3; It is characterized in that said convexity comprises the annular protrusion (122) in the outside of the center hole (101) that is arranged on second flat board (120), the arranged outside of this annular protrusion (122) has the conic convex (123) more than two.
5. twin-tub rotation-type compressor according to claim 3 is characterized in that said groove comprises the circular groove (112) in the outside of the center hole (101) that is arranged on first flat board (110), and the arranged outside of this circular groove (112) has the circular trough (119) more than two.
6. according to the arbitrary described twin-tub rotation-type compressor of claim 1 to 3, it is characterized in that said central diaphragm (100) adopts sintered alloy machine shaping.
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| CN2011100983790A CN102748289A (en) | 2011-04-19 | 2011-04-19 | Double-cylinder rotary compressor |
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| CN2011100983790A CN102748289A (en) | 2011-04-19 | 2011-04-19 | Double-cylinder rotary compressor |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104251206A (en) * | 2013-06-28 | 2014-12-31 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary double-stage compressor |
| CN105392995A (en) * | 2013-09-27 | 2016-03-09 | 三菱重工业株式会社 | Rotary compressor |
| CN105736374A (en) * | 2016-02-01 | 2016-07-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor |
| CN106089655A (en) * | 2016-08-10 | 2016-11-09 | 珠海凌达压缩机有限公司 | A kind of duplex cylinder compressor and use its air-conditioning |
| CN107829937A (en) * | 2017-10-10 | 2018-03-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and apply its air conditioner |
| CN109404286A (en) * | 2018-10-19 | 2019-03-01 | 珠海格力电器股份有限公司 | The judgment method of positive displacement compressor and its inner cylinder body state change |
| CN109595163A (en) * | 2017-09-30 | 2019-04-09 | 广东美芝制冷设备有限公司 | For the middle baffle assembly of compressor and with its double-cylinder compressor |
| CN112412786A (en) * | 2020-10-26 | 2021-02-26 | 珠海格力节能环保制冷技术研究中心有限公司 | High-efficient compressor exhaust structure |
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| CN106089655B (en) * | 2016-08-10 | 2018-07-17 | 珠海凌达压缩机有限公司 | A kind of horizontal dual cylinder compressor and use its air-conditioning |
| CN109595163A (en) * | 2017-09-30 | 2019-04-09 | 广东美芝制冷设备有限公司 | For the middle baffle assembly of compressor and with its double-cylinder compressor |
| CN107829937A (en) * | 2017-10-10 | 2018-03-23 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and apply its air conditioner |
| CN107829937B (en) * | 2017-10-10 | 2024-03-22 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioner using same |
| CN109404286A (en) * | 2018-10-19 | 2019-03-01 | 珠海格力电器股份有限公司 | The judgment method of positive displacement compressor and its inner cylinder body state change |
| CN112412786A (en) * | 2020-10-26 | 2021-02-26 | 珠海格力节能环保制冷技术研究中心有限公司 | High-efficient compressor exhaust structure |
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