CN102400916A - Rotary type compressor - Google Patents
Rotary type compressor Download PDFInfo
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- CN102400916A CN102400916A CN2010102805952A CN201010280595A CN102400916A CN 102400916 A CN102400916 A CN 102400916A CN 2010102805952 A CN2010102805952 A CN 2010102805952A CN 201010280595 A CN201010280595 A CN 201010280595A CN 102400916 A CN102400916 A CN 102400916A
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Abstract
The invention relates to a rotary type compressor, a compressing mechanism part is provided in a seal housing, the compressing mechanism part comprises a cylinder with a cylinder compressing chamber, a piston is provided in the cylinder compressing chamber, an eccentric crankshaft as well as a main bearing and an auxiliary bearing used for supporting the eccentric crankshaft drive the piston to carry out eccentric rotation by the eccentric shaft, the main bearing and the auxiliary bearing are arranged on the cylinder, a front-end of a slide plate is abut against peripheral region of the piston, a plane slot is provided on an upper plane part and/or a lower plane part of the piston, a circular plate is provided in the plane part slot, the differential pressure between pressure in the piston and pressure in the cylinder compressing chamber causes the floating of the circular plate. A sealing ring or an elastic component used for preventing gas leakage is provided between the piston and the circular plate. The rotary type compressor has the advantages of reasonable and simple structure, flexible operation and low making cost, and is capable of effectively improving the loss of high pressure gas leaked from the internal part of the rotary type compressor piston to the cylinder compressing chamber, and raising the efficiency of the compressor, the rotary type compressor has the characteristic of wide application scope.
Description
Technical field
The present invention relates to a kind of rotary compressor, relevant with the efficiengy-increasing of rotary compressor in being applied in air conditioner or refrigerating plant.
Background technique
From preventing the viewpoint of global greenhouse effectization, the efficiengy-increasing of the rotary compressor that carries in the air conditioner is a very big problem.The depth pistion gap that forms between the piston of rotary compressor and the bearing, the efficient that expands again to rotary compressor of the pressurized gas that leak to the cylinder compression chamber from internal piston through this depth pistion gap has very big influence.
Summary of the invention
The object of the invention aim to provide a kind of simple and reasonable, flexible operation, fabricating cost low, can effectively improve the pressurized gas loss of leaking to the cylinder compression chamber from the inside of rotary piston for compressor; Improve the efficiency of compressor and rotary compressor applied widely, to overcome deficiency of the prior art.
A kind of rotary compressor by this purpose design; Be provided with compression mechanical part in the housing of sealing; This compression mechanical part comprises the cylinder that has the cylinder compression chamber, be accommodated in piston in the cylinder compression chamber, make the eccentric crankshaft of eccentric rotary and main bearing and the supplementary bearing that supports eccentric crankshaft through the eccentric shaft driven plunger; Main bearing and supplementary bearing are arranged on the cylinder, and the tip of slide plate is resisted against on the periphery of piston, it is characterized in that the last planar surface portion of piston and/or lower flat portion are provided with the planar surface portion groove; Be provided with plectane in the planar surface portion groove, pressure in the piston and the pressure reduction between the pressure in the cylinder compression chamber cause that plectane floats.
Be provided with the seal ring or the elastic component that are used to prevent gas leakage between said piston and the plectane.
Said piston is provided with the fitting recess that is used to install seal ring, and fitting recess is more than one.
Said piston is provided with spacer groove, and elastic component is arranged in the spacer groove and is crimped between plectane and the piston.
Said plectane is provided with more than one oilhole.
The thickness of the degree of depth >=plectane of said planar surface portion groove.
The internal diameter of the internal diameter＜piston of said plectane.
Said rotary compressor is connected in series the formation refrigeration plant successively with condenser, expansion valve, vaporizer.
The present invention is generally the upper and lower plane of on high-tension side piston in inside; Be equipped with plectane on the just upper and lower slip surface; This plectane is owing to the pressure reduction between the interior pressure of pressure in the piston and cylinder compression chamber floats, so the depth pistion gap can reduce its result; Can reduce the gas that comes out from clearance leakage, thereby the efficient that prevents compressor reduces.And rotary compressor also starts more easily.
It is on high-tension side high pressure type rotary compressor that the present invention is not only applicable to housing pressure; Also going for housing pressure is the low pressure type rotary compressor of low voltage side; It has simple and reasonable, flexible operation, fabricating cost low, can effectively improve inside from rotary piston for compressor to the pressurized gas loss that the cylinder compression chamber leaks, improve the efficiency and the advantage of wide range of application of compressor.
Description of drawings
Fig. 1 is the structural representation of embodiments of the invention 1.
Fig. 2 is the broken section structure for amplifying schematic representation of the compression mechanical part among the embodiment 1.
Fig. 3 is the cross section structure for amplifying schematic representation of the compression mechanical part among the embodiment 1.
Fig. 4 is piston and the decomposition texture schematic representation of plectane among the embodiment 1.
Fig. 5 is the efficiency curve diagram of rotary compressor in the past.
Fig. 6 is the plectane force analysis figure among the embodiment 1.
Fig. 7 is piston and the decomposition texture schematic representation of plectane in the embodiments of the invention 2.
Fig. 8 is the sectional structure schematic representation after piston and the plectane assembling in the embodiments of the invention 3.
Fig. 9 is piston and the decomposition texture schematic representation of plectane in the embodiments of the invention 4.
Among the figure: 1 is rotary compressor, and 2 is housing, and 5 is condenser, and 6 is vaporizer, and 7 is expansion valve, and 13 is liquid-storage container; 14 is sucking pipe, and 15 is exhaust port, and 16 is eccentric crankshaft, and 17 is eccentric shaft, and 18 is plectane, and 21 is compression mechanical part; 22 is motor part, and 23 is cylinder, and 24 is the cylinder compression chamber, and 25 is main bearing, and 26 is supplementary bearing, and 28 is piston; 29 is slide plate, and 30 is the planar surface portion groove, and 31a is a low pressure chamber, and 31b is a hyperbaric chamber, and 33 is oil; 35 is seal ring, and 36 is oilhole, and 37 is corrugated gasket, and 38 is spacer groove, and 40 is the cylinder screw.
Embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is further described.
Referring to Fig. 1, rotary compressor 1 is made up of compression mechanical part in the housing that is installed in columniform sealing 2 21 and the motor part 22 that is configured in compression mechanical part 21 tops.Compression mechanical part 21 is by cylinder 23; With at the inner piston 28 of doing eccentric rotation of cylinder compression chamber 24 and the slide plate 29 that moves back and forth with the periphery butt of this piston 28; The main bearing 25 of the eccentric crankshaft 16 that driven plunger 28 is rolled and this eccentric crankshaft 16 of support that slides constitutes with supplementary bearing 16.The upper and lower planar surface portion of piston 28 has been installed plectane 18 respectively.The compression mechanical part 21 that more than constitutes is accomplished through 40 assemblings of cylinder screw.
The periphery of the compression mechanical part 21 that assembling is accomplished through cylinder 23 is fixed on the inwall of housing 2 of sealing.Oil 33 is stored in the bottom of the housing 2 of sealing.
In the system of carrying rotary compressor 1, the low-pressure gas that sucks from suction pipe 14 is compressed into pressurized gas enter the housing 2 of sealing from exhaust port 15 inside in cylinder compression chamber 24.Therefore, the internal pressure of the housing 2 of sealing is the high pressure side that equates with head pressure.After this, the pressurized gas from outlet pipe (not having diagram) is discharged get into liquid-storage container 13 through expansion valve 7, vaporizer 6 backs successively from condenser 5 beginnings, flow into sucking pipe 14 at last, are inhaled into cylinder compression chamber 24 once again.
Having the oil 33 that the eccentric crankshaft 16 of eccentric shaft 17 can rely on centrifugal force will be trapped in housing 2 bottoms of sealing drinks up.Therefore, the inner space of piston 28 has been full of enough oil.
Referring to Fig. 2, be the detail drawing of compression mechanical part 21.Two plectanes 18 are installed in respectively on the planar surface portion groove 30 of the upper and lower planar surface portion that is positioned at piston 28.
During rotary compressor 1 running, rely on piston 28 pressure difference between inside and outside, plectane 18 floats; Each plectane 18 is through the off-centre rotation of piston 28; Remain between the planar surface portion of main bearing 25 and supplementary bearing 26 in only gap, state in the plectane flying height after just, slide.
Referring to Fig. 3, be the cross-sectional view of compression mechanical part 21.The cylinder compression chamber 24 that is configured in cylinder 28 central authorities in the housing 2 that is fixed in sealing is divided into low pressure chamber 31a and hyperbaric chamber 31b by piston 28 and slide plate 29.
The piston 28 that eccentric shaft 17 through eccentric crankshaft 16 drives by direction shown in the dotted arrow among the figure, rotates with motor part 22 synchronously, and in cylinder compression chamber 24, carries out off-centre and rotate.Low pressure chamber 31a and hyperbaric chamber 31b carry out volume-variation at high speed.The pressure of hyperbaric chamber 31b begins to be varied to and the identical high pressure of the housing that seals 2 internal pressures from low pressure.
Referring to Fig. 4, be the decomposition texture schematic representation of piston 28 and plectane 18.Because the D outer diameter of D outer diameter of planar surface portion groove 30 1 and plectane 18 2 keeps only gap to be slidingly matched, so plectane 18 can fluctuate.The inner diameter d 2 of plectane 18 is littler than the inner diameter d 1 of piston 28.Piston 28 becomes the slip surface of eccentric shaft 17.
The relation that has w1 >=w2 between the thickness w2 of the degree of depth w1 of planar surface portion groove 30 and plectane 18 is set w1-w2＜about 10 μ m.But, because fluctuation is greatly also out of question even this difference becomes again.
So when rotary compressor 1 stops, perhaps in cylinder compression chamber 24, producing till the pressure, plectane 18 can be received in the planar surface portion groove 30 and go.
But; As after state because the running of rotary compressor 1, the compression pressure of cylinder compression chamber 24 uprises; So plectane 18 can float, the minimum clearance between the planar surface portion of plectane 18 and main bearing 25 and supplementary bearing 26 is that the flying height by plectane 18 decides.The gap that plectane 18 produces when floating is become " plectane flying height ", with " the depth pistion gap " in the technology before being different from.
The precision of planenesses such as plectane 18 recommendation use Sweden steel, thickness and wear resistance performance and processability aspect are first-class, are rich in the material of elastic force.Certainly, use other steel plate also to be fine.
Referring to Fig. 5, expression be the air-conditioning rotary compressor in the past that is about 20cc about displacement volume, the size of depth pistion clearance delta r and the relation of compressor efficiency.
Depth pistion clearance delta r is the summation in each gap of forming of the interplanar of the upper and lower planar surface portion of piston and main bearing relative with it and supplementary bearing.
Transverse axis is represented Δ r, and unit is μ m; The longitudinal axis is represented power consumption, and unit is kw/h.The unit of refrigerating capacity is kw/h; Efficiency COP=refrigerating capacity/power consumption.And motor efficiency is certain.
As illustrating, refrigerating capacity and consumes electric power are very sensitive for the variation of Δ r.When depth pistion clearance delta r equaled 15 μ m, COP reached peak.When depth pistion clearance delta r is in the scope of 14～17 μ m, think that then efficiency COP is qualified.
But, if depth pistion clearance delta r became than 14 μ m hours, can occur, and cause the upper and lower planar surface portion of piston 28 and the loss of the sliding friction between two bearing plane portions excessive because depth pistion clearance delta r is too little, thus the consumption that increases electric power.And it is bad compressor start to take place, and then because the not enough generation wearing and tearing of the oil slick thickness of slide member.
On the other hand, bigger if depth pistion clearance delta r becomes than 17 μ m, leak into high pressure air the low pressure chamber of cylinder compression chamber through piston upper and lower face from internal piston and know from experience once again and expand, thereby reduce refrigerating capacity.Same, the high pressure air cognition that leaks into the hyperbaric chamber (intermediate pressure) the compression from internal piston here reexpands, thus the consumption that increases electric power.
Like this, leak into the pressurized gas the cylinder compression chamber, not only reduced refrigerating capacity from internal piston, thereby also because the increase of power consumption greatly reduces efficiency COP.
In order to solve this problem, be necessary to optimize the depth pistion gap.
The present invention has inserted plectane 18. at the planar surface portion groove 30 that is arranged on piston 28 planar surface portion.And, rely on the pressure reduction in the operation process, plectane 18 is floated, above-mentioned " plectane flying height " diminished than former " depth pistion gap ".
Referring to Fig. 6, explained in the inside of cylinder compression chamber 24 since plectane 18 float the principle that the plectane flying height diminishes.And it is 1/2 Δ r that the gap between the planar surface portion of the upper end of piston 28 and main bearing 25 resembles technological in the past.In addition, for the simplification of explaining, omitted eccentric crankshaft among Fig. 6.
What the size of arrow was represented among Fig. 6 is the distribution that acts on the pressure on the plectane 18.Pressure in the piston 28 is through the high pressure side of being everlasting, so high pressure P d acts on the downside of plectane 18 and the gap between the planar surface portion groove 30.
But, because the pressure of low pressure chamber 31a low pressure normally, the pressure that occurs in the upside of plectane 18 diminish gradually from the inboard high pressure P d of piston to the piston outside and low pressure chamber 31a in the pressure of low pressure Ps and unequal.So the distribution of this pressure is tilted.This situation is called the L pattern.
Pressure in hyperbaric chamber 31b and exhaust pressure Pd when just the pressure P d in the piston 28 equate, are created in the pressure balance of upside and the downside of plectane 18.This pressure distribution is called the H pattern.
Pressure in the hyperbaric chamber 31b is along with the variation of the angle of swing of piston, and between low pressure Ps and exhaust pressure Pd, changes, and therefore, the pressure on the plectane 18 changes between pattern L and pattern H.
Because the pressure in the piston 28 is low unlike the pressure of low pressure chamber 31a and hyperbaric chamber 31b, so plectane 18 floats to main bearing 25 directions, the plectane flying height diminishes.
Owing in the plectane flying height that this diminishes, produced oil film, so plectane 18 upper ends in the plectane flying height and bearing plane portion are not having in the scope of Metal Contact, it is minimum that its gap value reaches.And piston 28 is during the off-centre rotation, because the form error of bearing plane portion is being kept minimum gap in the time of the earthquake of plectane flying height.
In embodiment 1,, so just needn't change this design if can realize the optimization in depth pistion gap by former design.If the technological scheme of in this design, appending plectane 18 so just can reach effect and effect best as above-mentioned.
In a word, be that as required, plectane 18 can float because there is the relation of w1 >=w2 in the thickness w2 of the degree of depth w1 of the planar surface portion groove 30 among the embodiment 1 and plectane 18.And, in the instance as shown in Figure 5, can think that the amount of floating of plectane 18 is that the thickness total amount of two plectanes is 8 μ m to the maximum, the thickness of a plectane on average will be below 4 μ m.
As above-mentioned, because the planar surface portion precision of main bearing 25 and supplementary bearing 26 is different, the upper and lower end that is provided in plectane 18 in each piston is optimal.But even abolished plectane on one side, the amount of floating of plectane 18 still can increase, and still has significant effect.
If according to the present invention; Even under the occasion of setting bigger depth pistion gap; Because the height pressure difference, plectane 18 can be turned the gap automatically down, and the gas leakage from internal piston to the cylinder compression chamber has reduced; So, expand once again and the situation of the loss of compression efficiency that causes is improved by the pressurized gas of rotary compressor.
When rotary compressor just started, because whole gas pressures equates that at this moment, it is maximum that the depth pistion gap reaches, it is minimum that the slippage loss of piston reaches, so the effect that has rotary compressor to start easily.
And; Because floating of plectane 18; Although piston 28 inner pressurized gas have the worry that leaks into the low voltage side of cylinder compression chamber 24 from the gap between the D outer diameter 2 of the D outer diameter 1 of planar surface portion groove 30 and plectane 18, above-mentioned gap control gets minimum, and gas is little as almost can to ignore.
Be installed in piston 28 17 last times of eccentric shaft, because plectane 18 can be assembled on the piston 28, image pattern 4 that kind, because inner diameter d 2＜piston inner diameter d1 of plectane 18, so can enlarge the Effective face width of plectane 18.Therefore, the gas flow that leaks in the cylinder compression chamber 24 from internal piston might further obtain reducing.
Referring to Fig. 7, the planar surface portion groove 30 of piston 28 has been appended fitting recess, be used to install seal ring 35.Seal ring 35 is to have eliminated when plectane 18 floats, the good method of the inner pressurized gas of piston 28 from the clearance leakage between the D outer diameter 2 of the D outer diameter 1 of planar surface portion groove 30 and plectane 18 to the worry of the low voltage side of cylinder compression chamber 24.
When from above-mentioned gap gas leakage taking place, seal ring 35 is because pressure difference is unsteady together with plectane 18, thereby prevented gas leakage.Seal ring 35 can adopt O-ring seals.
In order to improve effect, also several the fitting recess that are used to install seal ring 35 can be set on piston 28 more.
All the other are not stated part and see first embodiment, no longer repeat.
Embodiment 3
Referring to Fig. 8, on the spacer groove on the planar surface portion of piston 28 38, disposed corrugated gasket 37 appending.For only plectane 18 being floated among the embodiment 1 through pressure reduction, in the present embodiment with corrugated gasket 37 as elastic component, the directions pressurization of floating at plectane 18 in advance, unsteady power has further strengthened.Therefore, when the pressure in the hyperbaric chamber 31b is the same with pressure in the piston 28, can plectane 18 be pressed on the direction of main bearing and supplementary bearing 26, the effect that prevents gas leakage of plectane 18 has further promoted.
Be to have adopted corrugated gasket 37 in an embodiment,,, can realize the object of the invention equally like post spring, tower spring, torsion spring or leaf spring etc. if other elastic component of exerting pressure to plectane 18 is arranged.
All the other are not stated part and see first embodiment, no longer repeat.
Embodiment 4
Referring to Fig. 9, on plectane 18, appended oilhole 36, lubricated the slip surface of plectane 18, and, prevented the gas leakage of coming out effectively from slip surface.
The inside of piston 28 provides abundant oil by eccentric crankshaft 16, because pressure difference, oil supplies toward cylinder compression chamber 24 from the inside of piston.At this moment, the oilhole 36 of plectane 18 and slip surface become the passage of fuel feeding.
In addition, suitably increase and decrease the quantity of oilhole according to necessity.And embodiment 4 also might use with embodiment 2, embodiment's 3 combinations.
Technological scheme provided by the invention has disclosed raising compression efficiency technology, but also can be applied in on the low pressure type rotary compressor of housing pressure as low voltage side simultaneously with housing pressure is relevant as on high-tension side high pressure type rotary compressor.
In low pressure type rotary compressor, because will control oil drain quantity, thus limited the oil mass that supplies in the cylinder compression chamber significantly, thus the low problem of compression efficiency just arranged.But,, can improve this problem significantly because after adopting technological scheme provided by the invention.
Claims (8)
1. rotary compressor; Be provided with compression mechanical part (21) in the housing (2) of sealing; This compression mechanical part (21) comprises the cylinder (23) that has cylinder compression chamber (24), be accommodated in piston (28) in the cylinder compression chamber (24), make the eccentric crankshaft (16) of eccentric rotary and the main bearing (25) and the supplementary bearing (26) of support eccentric crankshaft (16) through eccentric shaft (17) driven plunger (28); Main bearing (25) and supplementary bearing (26) are arranged on the cylinder (23); The tip of slide plate (29) is resisted against on the periphery of piston (28); The last planar surface portion and/or the lower flat portion that it is characterized in that piston (28) are provided with planar surface portion groove (30), are provided with plectane (18) in the planar surface portion groove (30), and pressure in the piston (28) and the pressure reduction between the pressure in the cylinder compression chamber (24) cause that plectane (18) floats.
2. rotary compressor according to claim 1 is characterized in that being provided with between said piston (28) and the plectane (18) seal ring (35) or the elastic component that is used to prevent gas leakage.
3. rotary compressor according to claim 2 is characterized in that said piston (28) is provided with the fitting recess that is used to install seal ring (35), and fitting recess is more than one.
4. rotary compressor according to claim 2 is characterized in that said piston (28) is provided with spacer groove (38), and elastic component is arranged in the spacer groove (38) and is crimped between plectane (18) and the piston (28).
5. rotary compressor according to claim 1 and 2 is characterized in that said plectane (18) is provided with more than one oilhole (36).
6. rotary compressor according to claim 1 is characterized in that the thickness (w2) of the degree of depth (the w1) >=plectane (18) of said planar surface portion groove (30).
7. rotary compressor according to claim 1 is characterized in that the internal diameter (d1) of internal diameter (the d2)＜piston (32) of said plectane (18).
8. rotary compressor according to claim 1 is characterized in that said rotary compressor (1) and condenser (5), expansion valve (7), vaporizer (6) are connected in series the formation refrigeration plant successively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102805952A CN102400916A (en) | 2010-09-07 | 2010-09-07 | Rotary type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102805952A CN102400916A (en) | 2010-09-07 | 2010-09-07 | Rotary type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102400916A true CN102400916A (en) | 2012-04-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010102805952A Pending CN102400916A (en) | 2010-09-07 | 2010-09-07 | Rotary type compressor |
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| Country | Link |
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| CN (1) | CN102400916A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103912497A (en) * | 2012-12-28 | 2014-07-09 | Lg电子株式会社 | Compressor |
| CN104110380A (en) * | 2014-07-23 | 2014-10-22 | 珠海凌达压缩机有限公司 | Compressor and roller structure thereof |
| CN105201828A (en) * | 2015-10-14 | 2015-12-30 | 珠海凌达压缩机有限公司 | Roller and rotary compressor comprising same |
| US9429156B2 (en) | 2012-12-28 | 2016-08-30 | Lg Electronics Inc. | Compressor |
| CN107514365A (en) * | 2017-09-29 | 2017-12-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly and there is its compressor |
| CN114017330A (en) * | 2021-11-05 | 2022-02-08 | 广东美芝制冷设备有限公司 | Rotor compressor and refrigeration equipment |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5783691A (en) * | 1980-11-11 | 1982-05-25 | Matsushita Electric Ind Co Ltd | Compressor |
| JPS58152193A (en) * | 1982-03-05 | 1983-09-09 | Hitachi Ltd | Enclosed type rotary compressor |
| JPS5951191A (en) * | 1982-09-18 | 1984-03-24 | Matsushita Electric Ind Co Ltd | Rolling piston type rotary compressor |
| CN101012832A (en) * | 2007-01-23 | 2007-08-08 | 美的集团有限公司 | Rotary compressor |
-
2010
- 2010-09-07 CN CN2010102805952A patent/CN102400916A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5783691A (en) * | 1980-11-11 | 1982-05-25 | Matsushita Electric Ind Co Ltd | Compressor |
| JPS58152193A (en) * | 1982-03-05 | 1983-09-09 | Hitachi Ltd | Enclosed type rotary compressor |
| JPS5951191A (en) * | 1982-09-18 | 1984-03-24 | Matsushita Electric Ind Co Ltd | Rolling piston type rotary compressor |
| CN101012832A (en) * | 2007-01-23 | 2007-08-08 | 美的集团有限公司 | Rotary compressor |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103912497A (en) * | 2012-12-28 | 2014-07-09 | Lg电子株式会社 | Compressor |
| US9394904B2 (en) | 2012-12-28 | 2016-07-19 | Lg Electronics Inc. | Compressor |
| US9429156B2 (en) | 2012-12-28 | 2016-08-30 | Lg Electronics Inc. | Compressor |
| CN104110380A (en) * | 2014-07-23 | 2014-10-22 | 珠海凌达压缩机有限公司 | Compressor and roller structure thereof |
| CN105201828A (en) * | 2015-10-14 | 2015-12-30 | 珠海凌达压缩机有限公司 | Roller and rotary compressor comprising same |
| CN107514365A (en) * | 2017-09-29 | 2017-12-26 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly and there is its compressor |
| CN107514365B (en) * | 2017-09-29 | 2024-02-27 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body assembly and compressor with same |
| CN114017330A (en) * | 2021-11-05 | 2022-02-08 | 广东美芝制冷设备有限公司 | Rotor compressor and refrigeration equipment |
| CN114017330B (en) * | 2021-11-05 | 2023-08-22 | 广东美芝制冷设备有限公司 | Rotor compressor and refrigeration equipment |
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Application publication date: 20120404 |