CN201771770U - Rotary type compressor - Google Patents
Rotary type compressor Download PDFInfo
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- CN201771770U CN201771770U CN2010201883733U CN201020188373U CN201771770U CN 201771770 U CN201771770 U CN 201771770U CN 2010201883733 U CN2010201883733 U CN 2010201883733U CN 201020188373 U CN201020188373 U CN 201020188373U CN 201771770 U CN201771770 U CN 201771770U
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Abstract
A rotary type compressor comprises a compression mechanism and a motor. The compression mechanism and the motor are arranged in a sealed casing, the compression mechanism comprises a cylinder, a piston, a crankshaft, a main bearing, an auxiliary bearing and a slide plate, wherein a cylinder compression cavity is formed at the center of the cylinder, the piston rotates in the cylinder compression cavity eccentrically, the crankshaft drives the piston, the main bearing and the auxiliary bearing support the crankshaft and are mounted on the cylinder, and the front end of the slide plate is connected to the periphery of the piston. The motor comprises a stator component and a rotor, the rotor is tightly sleeved on the crankshaft, the stator component comprises a stator iron core and a motor coil, the outer diameter of the stator component is larger than the inner diameter of the sealed casing, a ring-shaped framework is arranged on the upper end surface and/or the lower end surface of the stator component and fixed on the inner wall of the sealed casing, and the outer diameter of the framework is larger than the inner diameter of the sealed casing. The rotary type compressor has the advantages of being capable of effectively preventing the stator iron core from deforming, uniformly adjusting the size of an air gap between the inner diameter of the stator and the outer diameter of the rotor, avoiding reduction of efficiency of the motor, and stopping poor start and noise of the motor.
Description
Technical field
The utility model relates to a kind of rotary compressor.
Background technique
In the past, for the motor performance that improves the variable-frequency type rotary compressor with make convenience, adopted directly motor coil is rolled onto method on the stator iron core.When using this method, the rigidity of stator iron core can die down, and then exists the problem of motor distortion in the process of assemble compressible machine.
In the process of assemble compressible machine, usually adopt the hot jacket method that motor is fixed on the inner walls, be fixed in the stator iron core on the columniform inner walls of high rigidity, because the internal diameter of stator iron core distortion, cause the inwall and the air gap between the rotor outer wall of stator iron core unequal, so can become the reason that motor characteristic worsens and motor noise takes place.
The model utility content
The purpose of this utility model aim to provide a kind of simple and reasonable, prevent stator iron core distortion, equably adjust motor gas-gap size between diameter of stator bore and the rotor diameter, prevent that electric efficiency from descending, prevent the generation of poor starting and motor noise, rotary compressor applied widely, to overcome deficiency of the prior art.
A kind of rotary compressor by this purpose design, comprise the compression mechanical part and the motor section that are arranged in the seal casinghousing, during being included in, compression mechanical part is formed centrally the cylinder of cylinder compression chamber, in the cylinder compression chamber, make the piston of eccentric rotation, the bent axle of driven plunger, support bent axle and be installed on main bearing and supplementary bearing on the cylinder, the slide plate that tip and piston periphery are joined, motor section comprises stator module and rotor, rotor tightly is enclosed within on the bent axle, its structure characteristic is that stator module comprises stator iron core and motor coil, and the external diameter of stator module is bigger than the internal diameter of seal casinghousing; Upper-end surface and/or lower end surface at stator module are provided with circular frame, and frame is fixed on the inwall of seal casinghousing, and the external diameter of this frame is bigger than the internal diameter of seal casinghousing.
Be provided with circular cylinder frame between described compression mechanical part and the motor section, this cylinder frame is fixed on the inwall of seal casinghousing, and the external diameter of cylinder frame is bigger than the internal diameter of seal casinghousing, and compression mechanical part is arranged on the cylinder frame.
The periphery of described main bearing is rounded, and main bearing is fixed on the inwall of seal casinghousing by its periphery.
Described seal casinghousing comprises upper shell, middle casing and lower shell body, and it is cylindric that middle casing is.
The circular frame that the utility model is provided with high rigidity in the upper-end surface and/or the lower end surface of stator iron core, behind the housing hot jacket, because the contour projector of circular frame restriction inner walls, so can reduce the distortion of stator iron core, thereby can adjust the motor gas-gap size between diameter of stator bore and the rotor diameter correctly, equably, prevent that electric efficiency from descending, and prevents the generation of poor starting and motor noise.
The utlity model has characteristics simple and reasonable, that electric efficiency is high, noise of motor is low and the Safety performance of compressor is high.
Description of drawings
Fig. 1 is the utility model one example structure schematic representation.
Fig. 2 is that M-M among Fig. 1 is to the sectional structure schematic representation.
Structural representation when Fig. 3 assembles for motor section.
Structural representation when Fig. 4 finishes for the motor section assembling.
Fig. 5 is stator iron core stress deformation figure in the past.
Fig. 6 is that N-N among Fig. 5 is to the sectional structure schematic representation.
Fig. 7 is the cross-sectional view of middle casing.
Fig. 8 is the cross-sectional view of motor section.
Fig. 9 is the cross-sectional view of first frame.
Figure 10 is the assembling relationship figure of motor section and first frame and second frame.
Figure 11 is an application examples structural representation of the present utility model.
Among the figure: 1 is rotary compressor, and 2 is seal casinghousing, and 2a is a middle casing, 2b is a upper shell, and 2c is a lower shell body, and 3 is discharge pipe, 5 is outdoor heat exchanger, and 6 is indoor heat exchanger, and 7 is expansion valve, 8 is liquid-storage container, and 9 is suction pipe, and 11a is the first circular frame, 11b is the second circular frame, and 12 is the cylinder frame, and 13 are spot welding, 21 is compression mechanical part, and 23 is cylinder, and 25 is main bearing, 26 is supplementary bearing, and 27 is bent axle, and 28 is piston, 31 is motor section, and 32 is stator module, and 32a is a stator iron core, 32b is a motor coil, and 33 is rotor, and 34 is the stator outer diameter gap, 35 is the rotor diameter gap, and 36 is diameter of stator bore, and 37 is outer diameter flat portion, 41 is the cylinder screw, 42 is set screw, and 51 is assembling fixture, and 52 is supporting post.
Embodiment
Below in conjunction with drawings and Examples the utility model is further described.
Referring to Fig. 1, rotary compressor 1 comprises the compression mechanical part 21 on the inwall that is fixed on seal casinghousing 2 and is disposed at the motor section 31 on its top.Seal casinghousing 2 is made of columniform middle casing 2a, the upper shell 2b that seals its upper and lower opening and lower shell body 2c.
Compression mechanical part 21 comprises the piston 28 of doing eccentric rotation by cylinder 23, in the cylinder compression chamber, join with piston and reciprocating slide plate (not having diagram), the bent axle 27 of driven plunger 28, sliding main bearing 25 and the supplementary bearing 26 that supports bent axle 27 that close, more than each component fit together by cylinder screw 41.
As embodiment 1 feature, the upper-end surface of stator iron core 32a and lower end surface dispose the first frame 11a that is circular respectively and are the second circular frame 11b, configuration cylinder frame 12 below stator iron core 32a.These as by housing hot jacket method described later, are fixed on the inwall of middle casing 2a.The first above-mentioned frame and second frame both can contact the upper and lower end face of stator iron core 32a closely, also can and the upper and lower end face of stator iron core 32a between form the gap.
The compression mechanical part 21 of assembling after finishing is inserted into from the lower openings of middle housing 2a, is fixed on the cylinder frame 12 by three set screws 42.Thereafter, the upper opening of middle casing 2a and lower openings are welded with upper shell 2b and lower shell body 2c respectively, finish rotary compressor 1.
The rotary compressor of finishing 1 is carried on aircondition or refrigerating plant, the water heater.At this moment, become pressurized gas after the low-pressure gas that sucks from suction pipe 9 is compressed cylinder 23; Pressurized gas spue behind the inside of seal casinghousing 2, from discharge pipe 3, via outdoor heat exchanger 5, expansion valve 7, indoor heat exchanger 6 and liquid-storage container 8, turn back to suction pipe 9 once more.
Referring to Fig. 2, for the M-M of Fig. 1 to the sectional structure schematic representation.In the present embodiment, be arranged on the first frame 11a of stator iron core 32a upper end, the second frame 11b with being arranged on the stator module lower end is fixed on the inwall of housing 2.
Referring to Fig. 3, the method on the inwall that stator module 32, the first frame 11a, the second frame 11b and cylinder frame 12 is fixed to middle casing 2a is described.
By two sections assembling fixtures 51 that round platform constitutes up and down, be provided with four supporting posts 52 in the periphery that is positioned at the epimere round platform.From the lower end of supporting post 52, the first frame 11a of Cha Ruing, stator module 32, the second frame 11b are assembled on the supporting post 52 temporarily successively.At last, cylinder frame 12 is arranged on the upper end of supporting post 52.Cold forging or the manufacturing such as cast iron by steel of first frame, second frame and cylinder frame forms.
Subsequently, middle casing 2a is heated, and its internal diameter is expanded, and as shown, middle casing 2a is inserted from assembling fixture 51, and in the time of above the lower end of middle housing 2a is still in the round platform that is positioned at hypomere, assembling is finished.Middle casing 2a is during by air cooling, and its internal diameter dwindles, and is arranged on the state that four component on the assembling fixture 51 become interference fit, will be securely fixed on the inwall of middle casing 2a.
Next, middle casing 2a after assembling fixture 51 taking-ups, as shown in Figure 4, is finished the assembling of middle casing 2a and above-mentioned four component.The periphery of cylinder frame 12 begins to carry out the part welding by arc spot welding 13, from the outside of middle housing 2a.On cylinder frame 12, compression mechanical part 21 will be installed, compression mechanical part 21 is shown in the dotted line among the figure.
By this hot jacket method, the most universal on rotary compressor the assembling method that stator module 32 is fixed on the middle casing 2a inwall.But, when the rigidity of stator iron core 32a is the most weak or the periphery of stator iron core 32a when being provided with outer diameter flat portion 37 or the wall thickness of middle casing 2a when thicker, exist external diameter and the big problem of diameter of stator bore 36 distortion of stator iron core 32a.
Referring to Fig. 5, for the stator module that do not have the first circular frame and second frame by the in the past embodiment of hot jacket to the middle casing inwall.Based on this figure, the external diameter of stator iron core and the distortion of internal diameter are described.
When the hot jacket method of stator module 32 by middle casing is fixed on the inwall of middle casing, become interference fit between the outer wall of stator iron core 32a and the middle casing 2a inwall.At this moment, the maximum periphery of stator iron core is circular part, is subjected to maximum stress P; Have the gap between the outer diameter flat portion 37 of stator iron core and the middle casing, the stress that acts on this part is zero, and therefore, stress concentrates on the part of four circles.
Consequently, stator iron core 32a external diameter and diameter of stator bore 36 have very big-difference.In Fig. 5,,, also there is distortion along Y-axis owing to be subjected to the influence of X-axis distortion along the maximum that is deformed into of X-axis.Behind hot jacket, the actual circularity of the internal diameter of middle casing 2a is affected, and the actual circularity of the external diameter of stator iron core and internal diameter also is affected.
Except the distortion of stator iron core, carry out the outer distortion of upward and downward as the inwall of cross section N-N, the stator iron core 32a of Fig. 5.That is to say that in this part, 5～10 stacked block plates peel off, and form the gap therebetween.
The distortion of above stator iron core is subjected to the size and the middle casing influence of wall thickness of the rigidity of stator iron core own largely.
When pressing to the high pressure side in the housing of rotary compressor, the wall ratio of its housing is bigger.For example, when the housing internal diameter was the household air-conditioner compressor of 150～200mm, its wall thickness was about 2.6～3.0mm.
Using CO
2In the rotary compressor of refrigerant, the housing internal pressure surpasses 10Mpa, and wall thickness becomes about 6～7mm, compares with before wall thickness 2.6～3.0mm, and its rigidity has increased by 8～10 times.Therefore, in the latter's example, the distortion of stator iron core is excessive, needs to solve the excessive means of this distortion.
For rotor diameter gap or the little motor of motor gas-gap, its electric efficiency is better.But, consider the accent core between rotor shaft and the motor shaft and the distortion of bent axle, be generally 0.4～0.5mm.
But, the distortion of stator iron core in the past can be dwindled the rotor diameter gap or make it unequal, thereby make motor performance worsen, or make the startup of compressor become difficult, or become the reason that produces the discontinuous sound of motor by the attraction force that produces between rotor and the electric machine assembly.Even, can cause producing the worst fault that the inwall of rotor periphery and stator iron core expands.
In the present embodiment, as the solution of above problem, setting is the circular first frame 11a and the second frame 11b on the upper and lower end face of stator iron core 32a respectively.The stress that the first frame 11a and the second frame 11b are taken place when disperseing middle casing 2a to shrink in its full week has the effect of slowing down stator iron core 32a distortion.
Referring to Fig. 7-Fig. 9, be the size of each component relevant with assembling preceding stator iron core 32a distortion.Figure 10 is stator iron core 32a, the first frame 11a after assembling and the configuration details drawing of the second frame 11b.
Suppose that the internal diameter of middle casing 2a is dc, the external diameter of stator iron core 32a is Ds, and the internal diameter of stator iron core 32a is ds, and the external diameter of the first frame 11a is Df, and the external diameter of rotor 33 is Dr.Wherein, relevant with stator module 32 distortion significant dimensions is dc, Ds and Df.
Difference between the outer diameter D s of the inner diameter d c of middle casing 2a and stator iron core 32a is called the magnitude of interference Δ s of stator iron core, Δ s=dc-Ds is arranged.
At this, the inner diameter d s of outer diameter D s, middle casing 2a by stator iron core 32a diminishes behind the 0.2mm, be Δ s=-0.2, when not having the first frame 11a and the second frame 11b, after the assembling that stator module 32 is installed to middle casing 2a was finished, the anticipation maximum distortion of stator iron core 32a inner diameter d s was 0.2mm.
But as mentioned above, this amount of deformation is not only relevant with Δ s, and relevant with the rigidity of housing and stator iron core.
When disposing the first above-mentioned frame and second frame, first frame and the second frame frame are subjected to the stress of middle casing 2a, thereby and this stress be reflected to the reduction volume that reduces middle casing in full week of first frame and second frame.Therefore, by the first circular frame and second shelf design, the amount of deformation of the inner diameter d s of the adjustable sub-iron core 32a that adjusts.Followingly be, to adjusting the explanation of amount of deformation means.
When the outer diameter D s of stator iron core 32a equated with the outer diameter D f of the circular first frame 11a, the amount of deformation of the stator iron core 32a and the first frame 11a equated at the upper and lower end face of stator iron core 32a.Near the central authorities of stator iron core 32a, for the effect that prevents two motor stand stretches dies down, worry that therefore the amount of deformation of stator iron core 32a increases, still, because near the rigidity of stator iron core 32a central authorities is the highest, so stator iron core 32a does not have big distortion.
When Δ s=-0.2mm, for example, design the outer diameter D f of the first circular frame 11a than the big 0.15mm of outer diameter D s of stator iron core 32a, the shrinking stress of relative middle casing 2a, when the maximum distortion of first frame is 0.15mm, the external diameter of the first frame 11a after distortion equates with the outer diameter D s of stator iron core 32a, and be indeformable.
As mentioned above, if when designing the outer diameter D f of the first frame 11a of motor fully greatlyyer than the outer diameter D s of stator iron core 32a, the amount of deformation vanishing of stator iron core 32a.But, when stator module 32 is fixed to strength deficiency on the inwall of middle casing internal diameter 32, outer diameter D f that need be by optimizing the first frame 11a or connect first frame, second frame and stator iron core 32a by rivet in advance and solve.
Next, during Δ s=-0.2mm, for example, when designing the outer diameter D f of the first circular frame 11a than the little 0.1mm of outer diameter D s of stator iron core 32a, stator iron core 32a at first is out of shape, when its outer diameter D s becomes with after the outer diameter D f of the first frame 11a equates, by the effect of the first circular frame, not redeformation or amount of deformation tail off.
So, in the present embodiment, the first circular frame 11a and the second frame 11b are set, relation between the outer diameter D s of outer diameter D f, stator iron core 32a by optimizing the first frame 11a and the second frame 11b and the inner diameter d c of middle casing 2a, can limit the amount of deformation of stator iron core 32a, it be reached minimize.
The first circular frame 11a and the second frame 11b also play a part to proofread and correct the circularity of middle casing 2a internal diameter.Middle casing 2a is heated by the high temperature more than 300 ℃ before assembling; After the assembling, middle casing 2a is through supercooling and contraction.Consequent distortion is bigger to its circularity influence.Because above reason, the circularity of the internal diameter of stator iron core 32a can worsen, and makes that rotor diameter gap or motor gas-gap are unequal.
The employed first circular frame and second frame in the present embodiment, the circularity that can proofread and correct middle casing 2a, the deterioration of prevention stator iron core 32a internal diameter circularity.
So, the circular frame in the present embodiment can be brought into play the effect that prevents stator module distortion, can prevent dwindling and unequalization of the rotor diameter gap that forms between rotor diameter and the stator iron core internal diameter or motor gas-gap substantially.By this effect, can solve a plurality of problems in the past.
In the present embodiment, cylinder frame 12 performances effect and the effect identical with the first circular frame 11a.That is to say that frame 12 is positioned at the downside of the second circular frame 11b, can dwindle middle casing 2a amount of deformation, can prevent from the deterioration of circularity from therefore, can prevent the distortion of stator iron core 32a.
When the periphery that outer diameter flat portion, stator iron core are not set on the stator iron core is that the rigidity of circle and stator iron core is when having advantage, or when the wall thickness of middle housing approaches, even omit any in above-mentioned two frames, also can give full play to the purpose of this utility model.At this moment, about preventing the distortion of stator iron core, therefore the first circular frame and the effect maximum of second frame, not necessarily need the cylinder frame.
Referring to Figure 11, when the external diameter of the main bearing 25 of formation compression mechanical part 21 is suitable with the internal diameter of middle casing 2a, because the periphery of main bearing 25 is rounded, main bearing 25 is fixed on by its periphery on the inwall of seal casinghousing 2, and can omit the second circular frame 11b this moment.Therefore,, not only can omit cylinder frame 12, also can omit the second circular frame 11b, can improve manufacturing and cost by this method.
In sum, the disclosed technology of the utility model imports industry easily, and produces in batches easily.
Claims (4)
1. rotary compressor, comprise the compression mechanical part (21) and the motor section (31) that are arranged in the seal casinghousing (2), during being included in, compression mechanical part (21) is formed centrally the cylinder (23) of cylinder compression chamber, in the cylinder compression chamber, make the piston (28) of eccentric rotation, the bent axle (27) of driven plunger (28), support bent axle (27) and be installed on main bearing (25) and supplementary bearing (26) on the cylinder (23), the slide plate that tip and piston (28) periphery is joined, motor section (31) comprises stator module (32) and rotor (33), rotor (33) tightly is enclosed within on the bent axle (27), it is characterized in that stator module (32) comprises stator iron core (32a) and motor coil (32b), the external diameter of stator module (32) is bigger than the internal diameter of seal casinghousing (2); Upper-end surface and/or lower end surface at stator module (32) are provided with circular frame, and frame is fixed on the inwall of seal casinghousing (2), and the external diameter of this frame is bigger than the internal diameter of seal casinghousing (2).
2. rotary compressor according to claim 1, it is characterized in that being provided with between described compression mechanical part (21) and the motor section (31) circular cylinder frame (12), this cylinder frame (12) is fixed on the inwall of seal casinghousing (2), the external diameter of cylinder frame (12) is bigger than the internal diameter of seal casinghousing (2), and compression mechanical part (21) is arranged on the cylinder frame (12).
3. rotary compressor according to claim 1 and 2 is characterized in that the periphery of described main bearing (25) is rounded, and main bearing (25) is fixed on the inwall of seal casinghousing (2) by its periphery.
4. rotary compressor according to claim 3 is characterized in that described seal casinghousing (2) comprises upper shell (2a), middle casing (2b) and lower shell body (2c), and middle casing (2b) is cylindric.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201883733U CN201771770U (en) | 2010-05-05 | 2010-05-05 | Rotary type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201883733U CN201771770U (en) | 2010-05-05 | 2010-05-05 | Rotary type compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201771770U true CN201771770U (en) | 2011-03-23 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010201883733U Expired - Lifetime CN201771770U (en) | 2010-05-05 | 2010-05-05 | Rotary type compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201771770U (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103727039A (en) * | 2014-01-08 | 2014-04-16 | 广东美芝制冷设备有限公司 | Two-stage compression rotary compressor, pump body assembly of two-stage compression rotary compressor, and air conditioning system |
| CN103727040A (en) * | 2012-10-11 | 2014-04-16 | 三菱电机株式会社 | Enclosed rotary compressor and refrigeration cycle device |
| CN104481884A (en) * | 2014-12-05 | 2015-04-01 | 广东美芝制冷设备有限公司 | Refrigerating system and rotary compressor with axial flux motor |
| CN104976120A (en) * | 2015-07-02 | 2015-10-14 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN106062367A (en) * | 2013-12-01 | 2016-10-26 | 阿斯彭压缩机有限责任公司 | Compact low noise rotary compressor |
| CN106121959A (en) * | 2016-08-09 | 2016-11-16 | 珠海凌达压缩机有限公司 | The assembling structure of compressor electric motor and housing and compressor |
| CN107313938A (en) * | 2017-08-22 | 2017-11-03 | 广东美的制冷设备有限公司 | Compressor assembly and the refrigeration system with it |
| CN107355381A (en) * | 2017-08-22 | 2017-11-17 | 广东美的制冷设备有限公司 | Compressor assembly and there is its refrigeration system |
| CN107404161A (en) * | 2017-07-28 | 2017-11-28 | 安徽美芝精密制造有限公司 | Compressor |
| CN109254247A (en) * | 2018-09-20 | 2019-01-22 | 精进百思特电动（上海）有限公司 | A kind of new energy rotor mechanism for testing under high-speed condition |
| WO2022107212A1 (en) * | 2020-11-17 | 2022-05-27 | 三菱電機株式会社 | Hermetic electric compressor |
| US11614086B2 (en) | 2016-12-30 | 2023-03-28 | Aspen Compressor, Llc | Flywheel assisted rotary compressors |
-
2010
- 2010-05-05 CN CN2010201883733U patent/CN201771770U/en not_active Expired - Lifetime
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103727040A (en) * | 2012-10-11 | 2014-04-16 | 三菱电机株式会社 | Enclosed rotary compressor and refrigeration cycle device |
| US10670017B2 (en) | 2013-12-01 | 2020-06-02 | Aspen Compressor, Llc | Compact low noise rotary compressor |
| CN106062367A (en) * | 2013-12-01 | 2016-10-26 | 阿斯彭压缩机有限责任公司 | Compact low noise rotary compressor |
| CN106062367B (en) * | 2013-12-01 | 2019-11-19 | 阿斯彭压缩机有限责任公司 | Compact type low-noise rotary compressor |
| CN103727039A (en) * | 2014-01-08 | 2014-04-16 | 广东美芝制冷设备有限公司 | Two-stage compression rotary compressor, pump body assembly of two-stage compression rotary compressor, and air conditioning system |
| CN104481884A (en) * | 2014-12-05 | 2015-04-01 | 广东美芝制冷设备有限公司 | Refrigerating system and rotary compressor with axial flux motor |
| CN104976120B (en) * | 2015-07-02 | 2018-09-11 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN104976120A (en) * | 2015-07-02 | 2015-10-14 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN106121959A (en) * | 2016-08-09 | 2016-11-16 | 珠海凌达压缩机有限公司 | The assembling structure of compressor electric motor and housing and compressor |
| US11614086B2 (en) | 2016-12-30 | 2023-03-28 | Aspen Compressor, Llc | Flywheel assisted rotary compressors |
| CN107404161A (en) * | 2017-07-28 | 2017-11-28 | 安徽美芝精密制造有限公司 | Compressor |
| CN107355381A (en) * | 2017-08-22 | 2017-11-17 | 广东美的制冷设备有限公司 | Compressor assembly and there is its refrigeration system |
| CN107313938A (en) * | 2017-08-22 | 2017-11-03 | 广东美的制冷设备有限公司 | Compressor assembly and the refrigeration system with it |
| CN109254247A (en) * | 2018-09-20 | 2019-01-22 | 精进百思特电动（上海）有限公司 | A kind of new energy rotor mechanism for testing under high-speed condition |
| WO2022107212A1 (en) * | 2020-11-17 | 2022-05-27 | 三菱電機株式会社 | Hermetic electric compressor |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20110323 |