CN114320916B - Pump body structure, compressor and air conditioner - Google Patents
Pump body structure, compressor and air conditioner Download PDFInfo
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- CN114320916B CN114320916B CN202111592299.0A CN202111592299A CN114320916B CN 114320916 B CN114320916 B CN 114320916B CN 202111592299 A CN202111592299 A CN 202111592299A CN 114320916 B CN114320916 B CN 114320916B
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Abstract
The invention belongs to the technical field of compressors and discloses a pump body structure, a compressor and an air conditioner. The pump body structure is connected with the shell of the compressor through the flange, and is also connected with the shell through the shaft neck of the flange and the support frame component, so that the moment generated by the rotor of the compressor along the radial direction is reduced, and the influence on the vibration of the pump body structure is small enough; in addition, due to the arrangement of the support frame component, the connection rigidity of the pump body rotor component is also increased, the swing natural frequency and the frequency response amplitude of the pump body rotor component are further improved, and the problem that the 6-frequency doubling noise peak value is prominent in the operation range of 30-50Hz is solved.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a pump body structure, a compressor and an air conditioner.
Background
The rolling rotor type compressor has the outstanding advantages of small volume, simple structure and the like, and is widely applied to the fields of household air conditioners, commercial air conditioners, low-temperature heat pumps and the like; in order to adapt to the gradually increased compressor displacement, the height of a compressor motor is increased, and the weight is increased; the pump body of the compressor is generally welded on the inner wall of the shell through a flange or an air cylinder, after the weight of the motor is increased, the weight of two sides of a welding point of the pump body is increased, so that the swing natural frequency of a pump body rotor assembly is reduced to 200-250Hz, generally, in order to improve the energy efficiency of the compressor, the motor generally adopts a 6-pole motor, and therefore the pump body rotor assembly resonates under the action of 6 frequency doubling exciting forces of the motor when the compressor operates within the range of 30-50Hz, and the 6 frequency doubling noise peak value is greatly increased.
In order to solve the problems, the currently adopted method is to shield the abnormal operating frequency point of the noise, however, the range of 30-50Hz is the most commonly used frequency point of the air conditioning unit, and if the method is adopted, the use comfort of consumers is reduced.
Disclosure of Invention
In view of this, the invention provides a pump body structure, a compressor and an air conditioner, which improve the rigidity of a rotor by sleeving a support frame assembly on a flange, improve the swing natural frequency and the frequency response amplitude of the rotor, and alleviate the problem that 6-frequency doubling noise peak value is prominent in the operation range of 30-50 Hz.
In order to solve the above problem, according to an aspect of the present application, an embodiment of the present invention provides a pump body structure for a compressor, where the pump body structure includes a cylinder assembly, a flange, and a crankshaft, the crankshaft passes through the cylinder assembly, the flange is sleeved on the crankshaft, the pump body structure further includes a support frame assembly, the support frame assembly is sleeved on a journal of the flange, and the support frame assembly is connected to a casing of the compressor.
In some embodiments, the support frame assembly includes an annular flange fitting portion, a support portion extends outwards along the outer periphery of the flange fitting portion, and a housing connection portion is disposed at one end of the support portion away from the flange fitting portion; the flange matching part is sleeved on the shaft neck of the flange, and the shell connecting part is fixed on the shell of the compressor.
In some embodiments, at least two support portions are provided, and the number of the shell connecting portions matches the number of the support portions.
In some embodiments, adjacent shell connecting parts are connected by reinforcing ribs, and the reinforcing ribs and the shell connecting parts are integrally formed, so that all the reinforcing ribs and the shell connecting parts form a circular ring structure together.
In some embodiments, the flange mating portion is an interference fit with the journal of the flange.
In some embodiments, the inner diameter D of the flange fitting and the diameter D of the flange journal satisfy: D-D is more than or equal to 0.005mm and less than or equal to 0.03mm.
In some embodiments, when N support portions are provided, and N is an even number, the angle between two support portions spaced by N/2-1 is 180 °.
In some embodiments, the at least two support portions are evenly distributed along a circumference of the flange fitting portion.
In some embodiments, the shell connection is fixed to the shell of the compressor by welding.
In some embodiments, when the number of the shell connecting parts is N, and N is an even number, two shell connecting parts spaced by N/2-1 are welded at the same time corresponding to the shell.
In some embodiments, at least two shell connections are welded simultaneously in correspondence with the shell.
According to another aspect of the present application, an embodiment of the present invention provides a compressor including the pump body structure described above.
In some embodiments, the compressor includes a shell having attachment points for attachment to a support bracket assembly.
In some embodiments, when the pump body structure comprises housing connections and at least two housing connections are provided, the number of connection points matches the number of housing connections.
According to another aspect of the present application, an embodiment of the present invention provides an air conditioner, which is characterized in that the air conditioner comprises the above-mentioned compressor.
Compared with the prior art, the pump body structure at least has the following beneficial effects:
the pump body structure is connected with the shell of the compressor through the flange, and also connected with the shell through the shaft neck of the flange and the support frame component, so that the moment generated by the rotor of the compressor along the radial direction is reduced, and the influence on the vibration of the pump body structure is small enough; in addition, due to the arrangement of the support frame assembly, the connection rigidity of the pump body rotor assembly is increased, the swing inherent frequency and the frequency response amplitude of the pump body rotor assembly are further improved, the problem that 6-frequency doubling noise peak values are prominent in the operation range of 30-50Hz is solved, and abnormal operation frequency points of noise do not need to be shielded, so that the use of a user is not influenced.
On the other hand, the compressor provided by the present invention is designed based on the pump body structure, and the beneficial effects thereof refer to the beneficial effects of the pump body structure, which are not repeated herein.
On the other hand, the air conditioner provided by the present invention is designed based on the compressor, and the beneficial effects thereof refer to the beneficial effects of the compressor, which are not described herein again.
The foregoing description is only an overview of the technical solutions of the present invention, and in order to make the technical solutions of the present invention more clearly understood and to make the technical solutions of the present invention practical in accordance with the contents of the specification, the following detailed description is given of preferred embodiments of the present invention with reference to the accompanying drawings.
Drawings
Fig. 1 is a sectional view of a pump body structure applied to a compressor according to an embodiment of the present invention;
FIG. 2 is a cross-sectional view taken along line B-B of FIG. 1;
FIG. 3 is an exploded view of a support bracket assembly and flange in a pump body structure according to an embodiment of the present invention;
FIG. 4 is a mating view of a support bracket assembly and flange in a pump body structure provided by an embodiment of the present invention;
FIG. 5 is a schematic view of a support frame assembly in a pump body structure according to an embodiment of the present invention;
FIG. 6 is a schematic view of another embodiment of a support frame assembly in a pump body structure according to the present invention;
FIG. 7 is another cross-sectional view of a pump body structure for use in a compressor according to an embodiment of the present invention;
FIG. 8 is a schematic view of another embodiment of a support bracket assembly for a pump body structure according to the present invention;
FIG. 9 is a schematic view of another embodiment of a support bracket assembly in a pump body structure according to the present invention;
FIG. 10 is a graph comparing rotor frequency response curves for a compressor according to an embodiment of the present invention with a conventional compressor;
FIG. 11 is a graph comparing the frequency doubling noise peak curves for a compressor and a pure copper compressor 6 according to an embodiment of the present invention;
fig. 12 is a sectional view of a compressor in the related art.
Wherein:
1. a cylinder assembly; 2. a flange; 3. a crankshaft; 4. a support frame assembly; 5. a housing; 6. a liquid separator; 7. a motor assembly; 21. a journal; 41. a flange mating portion; 42. a support portion; 43. a housing connecting portion; 44. reinforcing ribs; 51. a connection point; 71. a stator; 72. a rotor; 421. a first support section; 422. a second support portion; 423. a third support portion; 424. a fourth support portion; 431. a first housing connecting portion; 432. a second housing connecting portion; 433. a third housing connecting portion; 434. and a fourth housing connecting portion.
Detailed Description
To further explain the technical means and effects of the present invention adopted to achieve the predetermined object, the following detailed description of the embodiments, structures, features and effects according to the present invention will be made with reference to the accompanying drawings and preferred embodiments. In the following description, different "one embodiment" or "an embodiment" refers to not necessarily the same embodiment. Furthermore, the particular features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.
In the description of the present invention, it is to be understood that the terms "vertical", "lateral", "longitudinal", "front", "rear", "left", "right", "upper", "lower", "horizontal", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description of the present invention, and do not mean that the device or member to which the present invention is directed must have a specific orientation or position, and thus, cannot be construed as limiting the present invention.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Example 1
The embodiment provides a pump body structure for a compressor, as shown in fig. 1, the pump body structure comprises a cylinder assembly 1, a flange 2 and a crankshaft 3, the crankshaft 3 penetrates through the cylinder assembly 1, the flange 2 is sleeved on the crankshaft 3, the pump body structure further comprises a support frame assembly 4, the support frame assembly 4 is sleeved on a shaft neck 21 of the flange 2, and the support frame assembly 4 is connected with a shell of the compressor.
Specifically, the pump body structure provided in this embodiment is applied to a rolling rotor compressor, as shown in fig. 1, the rolling rotor compressor includes a liquid distributor 6, and the liquid distributor 6 is disposed outside the housing 5 and is used for delivering a low-pressure refrigerant to the cylinder assembly 1 in the pump body structure; the shell 5 wraps the motor assembly 7 and is isolated from the external environment in an airtight mode; the motor assembly 7 comprises a stator 71 and a rotor 72, the stator 71 is fixedly connected to the upper part in the shell 5 in an interference manner, and the cylinder assembly 1 and the flange 2 are arranged on the lower part of the motor assembly 7 and are connected with the shell 5 through welding spots. When the air conditioner works, the rotor 72 drives the crankshaft 3 to rotate when rotating, and a refrigerant enters the air cylinder assembly 1 through the air inlet of the liquid separator 6 to be compressed, then is discharged into the shell 5, and then is discharged into the air conditioning unit through the air outlet to participate in refrigeration and heating circulation.
In the embodiment, the pump body structure is connected with the shell 5 of the compressor through the flange 2, and also through the shaft neck 21 of the flange 2 and the support frame assembly 4, so that the moment generated by the rotor 72 of the compressor along the radial direction is reduced, and the influence on the structural vibration of the pump body is small enough; in addition, in the embodiment, due to the arrangement of the support frame assembly 4, the connection rigidity of the rotor 72 is also increased, so that the swing natural frequency and the frequency response amplitude of the rotor 72 are improved, and the problem that 6-frequency doubling noise peaks are prominent in the operation range of 30-50Hz is solved.
In a specific embodiment:
as shown in fig. 5, the supporting frame assembly 4 includes an annular flange fitting portion 41, a supporting portion 42 extends outwards along the outer periphery of the flange fitting portion 41, and one end of the supporting portion 42 away from the flange fitting portion 41 is provided with a housing connecting portion 43; the flange fitting portion 41 is fitted over the journal 21 of the flange 2, and the housing connecting portion 43 is fixed to the housing of the compressor.
Specifically, the flange engaging portion 41 is an annular structure, which is sleeved on the journal 21 of the flange 2, and an extending section extending outward along an outer peripheral surface of the flange engaging portion 41 is a supporting portion 42, and a width of an end of the supporting portion 42 is larger than that of the supporting portion 42, so as to be fixedly connected to the casing 5 of the compressor.
In a specific embodiment: in order to ensure the stability of the connection, at least two support portions 42 are provided, and the number of the housing connection portions 43 matches the number of the support portions 42.
In a specific embodiment:
as shown in fig. 2 and 6, the adjacent housing connecting portions 43 are connected by the reinforcing ribs 44, and the reinforcing ribs 44 are integrally formed with the housing connecting portions 43, so that all the reinforcing ribs 44 and the housing connecting portions 43 form a circular ring structure together.
Specifically, the annular structure formed by the reinforcing ribs 44 and the housing connecting portion 43 matches the shape of the cross section of the housing 5, so as to achieve the close-fit connection of the support frame assembly 4 and the housing 5.
Of course, the adjacent housing connecting portions 43 may be connected by the reinforcing ribs 44 (as shown in fig. 6), and the structure shown in fig. 5 may also be adopted, that is, the adjacent housing connecting portions 43 are not connected by the reinforcing ribs 44, because the force of the flange 2 applied to the support frame assembly 4 is mainly in the radial direction; if the reinforcing ribs 44 are added between the housing connection portions 43 in the configuration shown in fig. 6, a certain effect can be obtained in enhancing the connection rigidity between the pump body and the housing 5, but this is not a major factor.
In a specific embodiment:
the flange fitting portion 41 is in interference fit with the journal 21 of the flange 2; as shown in fig. 3, the inner diameter D of the flange fitting portion 41 and the diameter D of the journal 21 of the flange 2 satisfy: D-D is more than or equal to 0.005mm and less than or equal to 0.03mm.
Specifically, when the shaft journal 21 of the flange 2 receives the acting force transmitted by the crankshaft 3, the acting force needs to be transmitted to the housing 5 through the supporting frame assembly 4 to resist the swing of the rotor 72, so that the supporting frame assembly 4 and the flange 2 need to adopt interference fit; if the interference is too large, the inner hole of the flange 2 is deformed, and the running stability of the crankshaft 3 is affected, but if the interference is too small, the support frame assembly 4 is not enough to assist the journal 21 of the flange 2 to resist the swing of the rotor 72, and therefore the setting of the interference has a great influence on the implementation effect. Through experimental verification, satisfy between the internal diameter D of flange cooperation portion 41 and the diameter D of flange 2 axle journal 21 in support frame subassembly 4: when D-D is more than or equal to 0.005mm and less than or equal to 0.03mm, the influence on the running stability of the crankshaft 3 can be reduced, and the effects of supporting the shaft neck 21 of the flange 2 and reducing the swing of the rotor 72 can be achieved.
In a specific embodiment: when the number of the supporting portions 42 is N, and N is an even number, an included angle between two supporting portions 42 spaced by N/2-1 is 180 °.
Specifically, as shown in fig. 2 to 4, when four support portions 42 are provided, an included angle between two support portions 42 which are provided at intervals is 180 °.
When the support portions 42 are provided in six, the angle between two support portions 42 provided at an interval of two support portions is 180 °, that is, assuming that a certain support portion is a designated support portion, clockwise or counterclockwise along the designated support portion, a third support portion at an interval of two support portions is a target support portion, and the angle formed between the designated support portion and the target support portion is 180 °.
Preferably, at least two support portions 42 are uniformly distributed along the circumferential direction of the flange fitting portion 41.
Specifically, the housing connection portion 43 is fixed to the housing 5 by welding, and the support frame assembly 4 is inevitably deformed by a large amount of heat generated during welding, and if the deformation amount is too large, it may be deviated from the rotation center of the crankshaft 3 by the journal 21 of the flange 2, which not only increases noise of the compressor but also reduces reliability of the compressor. To avoid the above problem, at least two support portions 42 are uniformly distributed along the circumferential direction of the flange fitting portion 41.
As shown in fig. 2 to 6, the number of the supporting portions 42 is four, and the angle between adjacent supporting portions should be 90 ° in principle, but in a specific implementation, when the supporting portions 42 cannot be arranged exactly at 90 ° due to a structural limitation, the supporting portions 42 arranged at intervals must be in a straight line, for example, the included angle between the first supporting portion 421 and the third supporting portion 423 must be 180 °, but the included angle between the first supporting portion 421 and the second supporting portion 422 may be greater than 90 ° or smaller than 90 °, and the angle variation range thereof may be 45 ° to 135 °.
As shown in fig. 7-9 in particular, the number of the supporting portions 42 is three, in which case the angles between adjacent supporting portions 42 are ensured to be the same, i.e. 120 °.
In a specific embodiment: the housing connection 43 is fixed to the housing 5 of the compressor by welding. In specific implementation, when the number of the shell connecting parts 43 is N, and N is an even number, two shell connecting parts 43 spaced by N/2-1 are welded at the corresponding positions of the shell simultaneously. More preferably, at least two case connecting parts 43 are simultaneously welded to the corresponding case, regardless of whether N is even or odd.
The welding time sequence is required correspondingly to avoid different cooling time of each connecting point of the shell 5 and avoid the phenomenon that the support frame assembly 4 is pulled to deviate from the shaft neck 21 of the flange 2 due to different welding deformation; it is reasonable to weld the connection point of each housing 5 and the corresponding housing connection 43 at the same time, which is generally difficult to satisfy, especially when the number of the housing connection 43 is large. Therefore, a form of welding in two times may be adopted, as shown in fig. 6, when the number of the case connection parts 43 is four, the first case connection part 431 and the third case connection part 433 may be welded first, and then the second case connection part 432 and the fourth case connection part 434 may be welded (or the second case connection part 432 and the fourth case connection part 434 may be welded first, and then the first case connection part 431 and the third case connection part 433 may be welded second), because only when the two welding methods are adopted, the forces generated by the thermal deformation when the case connection points are welded may be balanced with each other; for example, when the first housing connecting portion 431 is welded, a force in a direction of connecting the third housing connecting portion 433 to the first housing connecting portion 431 is generated, and at the same time, when the third housing connecting portion 433 is welded, a force in a direction of connecting the first housing connecting portion 431 to the third housing connecting portion 433 is also generated, and the two forces are equal in magnitude and opposite in direction, so that the journal 21 of the flange 2 is prevented from being deviated in the direction of connecting the first housing connecting portion 431 and the third housing connecting portion 433. Similarly, the second housing connecting portion 432 and the fourth housing connecting portion 434 are welded together, so that the journal 21 of the flange 2 can be prevented from deviating along the connecting line between the second housing connecting portion 432 and the fourth housing connecting portion 434.
As shown in fig. 7-9, when there are three housing connection portions 43, the three housing connection portions 43 should be welded at the same time, so as to not only prevent the flange 2 from being pulled off by the support frame assembly 4, but also improve the rigidity of the rotor 72; the reason is that if three case connection portions 43 are welded at the same time, the resultant force of the thermal stresses generated by the welding thermal deformation of the three points is along the line from the rotation center of the crankshaft 3 to the case connection portion 43, the thermal stresses generated when the three case connection portions 43 are welded at the same time are equal in magnitude and different in direction by 120 °, and the thermal stresses generated finally cancel each other out.
After the pump body structure provided by the embodiment is adopted, the pump body structure and the housing 5 are connected with each other by welding through the flange 2 and the housing 5, and are also indirectly connected with the housing 5 through the shaft neck 21 of the flange 2 and the support frame assembly 4, so that the torque generated by the rotor 72 along the radial direction is reduced. For the compressor adopting the prior art, the moment generated by the rotor is F0 × L0 (as shown in fig. 12), and for the compressor adopting the present embodiment, the moment generated by the rotor is F1 × L1 (as shown in fig. 1), and F0 and F1 are the same when the displacement is the same, but L1 is shorter than L0, which results in smaller moment of the rotor 72 and smaller influence on the vibration of the pump body; in addition, the connection point between the pump body structure and the housing 5 of the present embodiment is increased, and the connection rigidity is also increased.
Example 2
The present embodiment provides a compressor including the pump body structure of embodiment 1.
In a specific embodiment:
the compressor comprises a shell 5, wherein a connecting point 51 connected with the support frame assembly 4 is arranged on the shell 5; and when the pump body structure includes the housing connection portions 43 and the housing connection portions 43 are provided in at least two, the number of the connection points 51 matches the number of the housing connection portions 43.
By applying a periodic excitation force of a sine or cosine function to the rotor 72, the pump body structure of the embodiment generates a maximum displacement (or called a response amplitude value) corresponding to the rotor 72 under the action of the excitation force, and the frequency response curve of the rotor 72 can be obtained by only increasing the frequency without changing the magnitude of the force; when the frequency of the excitation force is equal to the natural frequency of the rotor 72, the response amplitude thereof will reach a maximum value; according to the method, the response amplitudes of the rotor in the pump body structure in the prior art and the rotor in the pump body structure in the embodiment are respectively tested, and the frequency response curves of the two rotors are obtained as shown in fig. 10. As can be seen in fig. 12: compared with the frequency response curve of the rotor in the prior art, the natural frequency of the rotor is higher, and the response amplitude is lower; the compressor has the advantages that resonance of the pump body rotor assembly is avoided when the compressor operates at the middle and low frequency of 30-50Hz, and the pump body rotor assembly has lower response amplitude under the action of force and is not easy to generate larger 6-frequency multiplication noise peak even when the compressor operates at the high frequency above 50 Hz.
As shown in fig. 11, which is a comparison between the peak value of the 6-fold-frequency noise of the compressor using the prior art and the compressor using the present embodiment, it can be seen that the peak value of the 6-fold-frequency noise of the compressor of the present embodiment is significantly reduced.
Example 3
The present embodiment provides an air conditioner including the compressor of embodiment 2.
The present invention is not intended to be limited to the particular embodiments shown, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (12)
1. A pump body structure for a compressor, the pump body structure comprising a cylinder assembly (1), a flange (2) and a crankshaft (3), the crankshaft (3) passing through the cylinder assembly (1), the flange (2) being sleeved on the crankshaft (3), characterized in that: the pump body structure further comprises a support frame assembly (4), the support frame assembly (4) is sleeved on a shaft neck (21) of the flange (2), and the support frame assembly (4) is connected with a shell of the compressor; the support frame assembly (4) comprises an annular flange matching part (41), a support part (42) extends outwards along the periphery of the flange matching part (41), and a shell connecting part (43) is arranged at one end, far away from the flange matching part (41), of the support part (42); the flange matching part (31) is sleeved on a shaft neck 21 of the flange (2), and the shell connecting part (43) is fixed on a shell of the compressor; the flange matching part (41) is in interference fit with a shaft neck (21) of the flange (2); the inner diameter D of the flange fitting part (31) and the diameter D of the shaft neck (21) satisfy the following condition: D-D is more than or equal to 0.005mm and less than or equal to 0.03mm.
2. The pump body structure according to claim 1, wherein the support portions (42) are provided in at least two, and the housing connecting portions (43) are matched in number to the support portions (42).
3. The pump body structure according to claim 2, wherein adjacent housing connecting portions (43) are connected by a reinforcing rib (44), and the reinforcing rib (44) is integrally formed with the housing connecting portions (43), so that all the reinforcing ribs (44) and the housing connecting portions (43) form a circular ring structure together.
4. The pump body structure according to claim 2 or 3, characterized in that when the support portions (32) are provided in N number, and N is an even number, an angle between two of the support portions (42) spaced by N/2-1 is 180 °.
5. The pump body structure according to claim 2 or 3, characterized in that at least two of the support portions (42) are evenly distributed along a circumferential direction of the flange fitting portion (41).
6. Pump body structure according to claim 2 or 3, characterized in that the housing connection (43) is fixed to the compressor housing by welding.
7. The pump body structure according to claim 6, wherein when the number of the housing connecting portions (43) is set to be N, and N is an even number, two housing connecting portions (43) spaced by N/2-1 are welded at the same time in correspondence with the housing.
8. Pump body structure according to claim 6, characterized in that at least two of said housing connection portions (43) are welded simultaneously in correspondence of the housing.
9. A compressor, characterized in that it comprises a pump body structure according to any one of claims 1 to 8.
10. Compressor according to claim 9, characterized in that it comprises a shell (5), said shell (5) being provided with connection points (51) to said supporting frame assembly (4).
11. Compressor according to claim 10, characterized in that when the pump body structure comprises housing connections (43) and the housing connections (43) are provided in at least two, the number of connection points (51) matches the number of housing connections (43).
12. An air conditioner characterized in that it comprises a compressor according to any one of claims 9 to 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202111592299.0A CN114320916B (en) | 2021-12-23 | 2021-12-23 | Pump body structure, compressor and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111592299.0A CN114320916B (en) | 2021-12-23 | 2021-12-23 | Pump body structure, compressor and air conditioner |
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| CN114320916A CN114320916A (en) | 2022-04-12 |
| CN114320916B true CN114320916B (en) | 2023-03-24 |
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Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2585440B2 (en) * | 1989-10-18 | 1997-02-26 | 株式会社日立製作所 | Hermetic rotary compressor |
| JPH03129795U (en) * | 1990-04-13 | 1991-12-26 | ||
| JP2001323886A (en) * | 2000-05-16 | 2001-11-22 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| KR20080018743A (en) * | 2006-08-25 | 2008-02-28 | 엘지전자 주식회사 | Structure for decreasing vibration of rotary compressor |
| CN102549267B (en) * | 2009-09-25 | 2014-12-10 | 东芝开利株式会社 | Hermetically sealed compressor and refrigeration cycle device employing the same |
| CN104747449A (en) * | 2013-12-30 | 2015-07-01 | 上海日立电器有限公司 | Double support compressor making and assembling method |
| WO2019032096A1 (en) * | 2017-08-08 | 2019-02-14 | Hitachi-Johnson Controls Air Conditioning, Inc. | Rotary compressor and assembly method thereof |
| CN208669600U (en) * | 2018-08-28 | 2019-03-29 | 珠海凌达压缩机有限公司 | A kind of dual-support structure of rotary compressor, rotary compressor and air conditioner |
| CN209943101U (en) * | 2019-06-04 | 2020-01-14 | 上海海立电器有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
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