WO2021056796A1

WO2021056796A1 - Compressor and cooling device

Info

Publication number: WO2021056796A1
Application number: PCT/CN2019/120829
Authority: WO
Inventors: 罗承卓; 谭琴; 朱晓涵
Original assignee: 安徽美芝精密制造有限公司
Priority date: 2019-09-29
Filing date: 2019-11-26
Publication date: 2021-04-01
Also published as: CN110685911A

Abstract

A compressor and a cooling device. The compressor comprises: a housing (160), a stator (111) and a rotor (112), a first cylinder (121), a first piston (122) provided in the first cylinder (121), a second cylinder (124), and a second piston (125) provided in the second cylinder (124). A crankshaft (130) has a first eccentric portion (131) and a second eccentric portion (132). The first piston (122) is sleeved on the first eccentric portion (131). The second piston (125) is sleeved on the second eccentric portion (132). The crankshaft (130) passes through the rotor (112) and a compression assembly (120). A bearing system comprises a first bearing (141), a second bearing (142), and an auxiliary bearing (143). The first bearing (141) is provided on one side of the first cylinder (121) close to a driving motor (110). The second bearing (142) is provided on one side of the second cylinder (124) located away from the driving motor (110). The auxiliary bearing (143) is provided on the crankshaft (130) and is located on one side of the driving motor (110) located away from the compression assembly (120). A balance system comprises a rotor counter weight (151) and a crankshaft counter weight (154). The rotor counter weight (151) is provided on the rotor (112). The crankshaft counter weight (154) is provided on the crankshaft (130) and is located on one side of the second bearing (142) located away from the first bearing (141). An isolation cover (170) partially surrounds the crankshaft counter weight (154). The bearing system and the balance system improve the reliability of high-speed operation of the compressor.

Description

Compressors and refrigeration equipment

This application claims the priority of a Chinese patent application filed with the Chinese Patent Office on September 29, 2019, with the application number "201910932835.3" and the invention title "compressor and refrigeration equipment", the entire content of which is incorporated into this application by reference .

Technical field

This application belongs to the technical field of compressors, and specifically relates to a compressor and a refrigeration equipment.

Background technique

In the rolling rotor compressor, in the axial direction of the crankshaft, there are the rotor, the upper bearing, the cylinder and the lower bearing in sequence. The crankshaft with an eccentric part rotates under the drive of the rotor, and the piston sleeved on the eccentric part performs eccentric motion compression in the cylinder. Gas does work. Due to the existence of the eccentric part and the eccentric movement of the piston, it is necessary to install balance weights on the upper and lower sides of the rotor to offset the unbalanced force and moment. The centrifugal force and bending moment generated by the balance weight on the upper side of the rotor and the balance weight on the lower side of the rotor will act on the crankshaft, and the resulting bending deformation of the crankshaft is mainly suppressed by the upper bearing.

With the development trend of compressor efficiency, miniaturization and high speed, and in order to improve the mechanical efficiency, the crankshaft diameter is often designed to be small, resulting in poor crankshaft rigidity. Since the centrifugal force is proportional to the square of the speed, for high-speed compressors, the crankshaft will be severely deformed under the action of the centrifugal force and bending moment generated by the balance weight on the rotor. The reliability is poor, which in turn makes the reliability of the compressor worse.

Summary of the invention

This application aims to solve one of the technical problems existing in the prior art or related technologies.

For this reason, the first aspect of this application proposes a compressor.

The second aspect of the application proposes a refrigeration equipment.

In view of this, according to the first aspect of the present application, a compressor is proposed, which includes: a shell, the bottom of the shell is configured as an oil sump; a drive motor including a stator and a rotor; a compression assembly including a first cylinder, a first The piston, the second cylinder and the second piston, the first piston is arranged in the first cylinder, the second piston is arranged in the second cylinder; the crankshaft has a first eccentric part and a second eccentric part, and the first piston is sleeved in the first cylinder. On the eccentric part, the second piston is sleeved on the second eccentric part, the crankshaft passes through the rotor and the compression assembly; the bearing system includes a first bearing, a second bearing and an auxiliary bearing, the first bearing is arranged on the first cylinder close to the drive motor The second bearing is arranged on the side of the second cylinder away from the drive motor, and the auxiliary bearing is arranged on the crankshaft and on the side of the drive motor away from the compression assembly; the balance system includes a rotor balance block and a crankshaft balance block, and the rotor is balanced The block is arranged on the rotor, the crankshaft balance weight is arranged on the crankshaft and is located on the side of the second bearing away from the first bearing; the isolation cover partially surrounds the crankshaft balance weight.

The compressor provided in this application includes a casing, a drive motor, a compression assembly, a crankshaft, a bearing system, a balance system, and an isolation cover. Wherein, the bottom of the shell is configured as an oil pool, which can contain lubricating oil, and the drive motor, compression assembly, crankshaft, bearing system, balance system and isolation cover are all arranged in the shell. The driving motor includes a stator and a rotor, the stator can be arranged on the casing of the compressor, and the rotor is rotatably arranged in the stator. The compression assembly includes a first cylinder, a first piston arranged in the first cylinder, a second cylinder, and a second piston arranged in the second cylinder. The first piston is sleeved on the first eccentric part of the crankshaft, and the first piston is set in the first eccentric part of the crankshaft. The two pistons are sleeved on the second eccentric part of the crankshaft, and the crankshaft passes through the rotor. The rotor can drive the crankshaft to rotate, which in turn drives the first piston to perform eccentric motion in the first cylinder to compress gas to perform work, and drives the second piston to perform work on the second eccentric portion of the crankshaft. The compressed gas does work by eccentric motion in the second cylinder. Among them, because the crankshaft has a first eccentric part and a second eccentric part, the existence of the two eccentric parts and the eccentric movement of the two pistons will produce unbalanced forces and moments. The bearing system and the balance system are further beneficial to Move the center of mass of the entire balance system down, that is, move down the center of mass, reduce the bending deformation of the crankshaft, improve the wear of the crankshaft and the upper bearing, and improve the reliability of the first bearing, thereby improving the reliability of the compressor operation, especially The improvement effect is more obvious in high speed and high load operation.

Specifically, by setting the rotor balance weight on the rotor and the crankshaft balance weight on the crankshaft, the crankshaft balance weight is located on the side of the second bearing away from the first bearing, and the first bearing can be balanced by the rotor balance weight and the crankshaft balance weight. The centrifugal force brought by the eccentric part and the second eccentric part, specifically, the centrifugal force brought by the first eccentric part can be balanced by the rotor balance weight, and the centrifugal force brought by the second eccentric part can also be balanced by the crankshaft balance part Because there is no need for the rotor balance weight to balance the first eccentric part and the second eccentric part independently, the weight of the rotor balance weight can be effectively reduced, which is beneficial to move the entire balance system of the compressor down, and improve the operating stability and reliability of the compressor . Moreover, by providing the first bearing on the side of the first cylinder on the crankshaft close to the drive motor, and setting the auxiliary bearing on the side of the drive motor far away from the compression assembly on the crankshaft, the first bearing and the auxiliary bearing can bear the centrifugal force of the rotor balance weight together. And torque can effectively reduce the wear of the first bearing, improve the reliability and service life of the first bearing, and avoid the occurrence of the related technology relying on the first bearing alone, and because the first bearing is located in the first cylinder close to the drive motor On one side, it is far from the oil sump of the compressor, the oil supply is more difficult than the second bearing, the lubricating oil temperature is higher, and the reliability is poor. Moreover, by providing a second bearing on the side of the second cylinder on the crankshaft away from the drive motor, the centrifugal force and moment of the first eccentric part, the first piston, the second eccentric part and the second piston can pass through the first bearing and The second bearing is borne together to further reduce the wear of the first bearing. The centrifugal force and moment of the crankshaft balance weight can be borne by the second bearing. Since the second bearing is located on the side of the second cylinder away from the drive motor, it is easier to be lubricated by the oil in the oil sump, and the oil supply is sufficient, thereby preventing wear. Moreover, by setting the isolation cover to partially surround the crankshaft balance weight, the crankshaft balance weight can avoid excessive agitation of the oil in the oil sump during the rotation process, and can ensure that the oil sump supplies oil to the crankshaft, the second bearing, etc. Therefore, the compressor proposed in the present application operates stably and reliably, and particularly meets the requirements of a high-speed compressor, such as a compressor with a maximum speed greater than 150 rps (revolutions per second).

In addition, the compressor in the above technical solution provided by this application may also have the following additional technical features:

In some possible designs, the first eccentric portion and the second eccentric portion are relatively distributed around the rotation center line of the crankshaft.

In this design, by setting the first eccentric portion and the second eccentric portion to be relatively distributed around the rotation center line of the crankshaft, it is beneficial to improve the stability of the crankshaft rotation and the stability of the motor operation.

In some possible designs, the center of mass of the rotor balance weight and the first eccentric portion are relatively distributed around the rotation centerline of the crankshaft; the center of mass of the crankshaft balance weight and the second eccentric portion are relatively distributed around the rotation centerline of the crankshaft.

In this design, by making the center of mass of the rotor balance weight and the first eccentric portion relatively distributed around the rotation center line of the crankshaft, the rotor balance weight can be used to offset the inconsistency caused by the eccentric movement of the first eccentric portion and the first piston. Balance force and moment, and by making the center of mass of the crankshaft balance weight and the second eccentric part to be relatively distributed around the rotation centerline of the crankshaft, the crankshaft balance weight can be used to offset the eccentric movement of the second eccentric part and the second piston. Unbalanced force and moment, because there is no need for the rotor balance weight to balance the first eccentric part and the second eccentric part independently, the weight of the rotor balance weight can be effectively reduced, which is beneficial to move the entire balance system of the compressor down and improve the operation of the compressor Stability and reliability.

In some possible designs, the rotor balance weight is arranged on the side of the rotor close to the auxiliary bearing.

In other possible designs, the rotor balance weight is arranged on the side of the rotor close to the first bearing. It is beneficial to move the entire balance system down and improve the operating stability and reliability of the compressor.

In other possible designs, the rotor counterweight includes a first rotor counterweight and a second rotor counterweight. The first rotor counterweight is arranged on the side of the rotor close to the auxiliary bearing, and the second rotor counterweight is arranged on the rotor close to the first rotor counterweight. One side of the bearing.

In this design, the rotor balance weight can be set on both sides of the rotor, that is, the first rotor balance weight is set on the side of the rotor close to the auxiliary bearing, and the second rotor balance weight is set on the side of the rotor close to the first bearing. To balance the demand, set the specific position of the rotor balance weight.

Further, the center of mass of the first rotor balance weight and the center of mass of the second rotor balance weight are relatively distributed in the extension direction of the rotation center line of the crankshaft. It is convenient for the quick installation of the first rotor balance weight and the second rotor balance weight, and it is also convenient to quickly and accurately realize the offset of the unbalanced force and moment caused by the eccentric part.

In some possible designs, the outer peripheral surface of the crankshaft balance weight is a cylindrical surface, and the axis of the cylindrical surface is collinear with the rotation center line of the crankshaft.

In this design, since one end of the crankshaft will extend into the oil sump of the compressor, the outer circumference of the crankshaft balance weight will be filled with lubricating oil, and then by setting the outer peripheral surface of the crankshaft balance weight as a cylindrical surface, the axis of the cylindrical surface is aligned with the crankshaft The collinear centerline of rotation can effectively prevent the crankshaft from squeezing the oil and doing work during high-speed rotation and losing energy efficiency.

In some possible designs, the crankshaft balance weight and the crankshaft are connected together by screws; or the crankshaft balance weight and the crankshaft are interference-fitted together and installed by cold pressing or hot sleeve; or the crankshaft balance weight and the crankshaft are fixed together by a pin key .

In some possible designs, the maximum speed of the compressor is greater than 150 rps. Not only can it meet the high-speed compressor requirements in related technologies, but it also runs stably and reliably.

In some possible designs, an opening is provided on the isolation cover through which the oil in the oil sump can flow to the crankshaft balance weight. The isolation cover does not completely enclose the crankshaft balance weight, but leaves a gap, which is beneficial for the lubricating oil of the second bearing to return to the oil pool to form a circulation.

In some possible designs, the compressor further includes: a partition to separate the first cylinder and the second cylinder.

Further, the first bearing, the partition plate and the first piston jointly seal the first cylinder; the second bearing, the partition plate and the second piston jointly seal the second cylinder. Avoid gas leakage.

Further, the partition includes a first partition and a second partition. The first partition and the second partition are both provided with exhaust holes, and the exhaust holes are provided with exhaust valves. The first partition and the second partition An exhaust cavity is enclosed by the partition. Ensure that the exhaust is unobstructed.

In some possible designs, a first exhaust hole is provided on the first bearing, a first exhaust valve and a first muffler are provided at the first exhaust hole, and a second exhaust hole is provided on the second bearing. A second exhaust valve and a second muffler are arranged at the second exhaust hole, and the crankshaft balance weight is located on the side of the second muffler away from the first bearing. Conducive to reducing exhaust noise.

In some possible designs, the auxiliary bearing is a sliding bearing or a rolling bearing or an articulated bearing.

In some possible designs, the auxiliary bearing is an integral bearing or a split bearing. It can be determined according to the fixing method of the auxiliary bearing and the housing. The integrated bearing has low cost, and the split bearing is convenient for self-aligning installation.

Further, when the auxiliary bearing is a split bearing, the auxiliary bearing includes a bearing seat, a rolling bearing and a bracket, the bracket is fixedly connected to the housing, the bearing seat is arranged on the bracket, and the rolling bearing is arranged on the bearing seat.

The second aspect of the present application proposes a refrigeration equipment, including: a compressor as in any one of the above technical solutions. Since the refrigeration equipment provided in the present application has the compressor of any of the above technical solutions, it further has the beneficial effects of any of the above technical solutions, which will not be repeated here. Among them, any of the above designs combined with the compressor of the first aspect constitutes a technical solution.

Further, the refrigeration equipment also includes a heat exchanger and a throttle valve, which are directly or indirectly connected with the compressor to form a refrigeration circuit or a heating circuit.

Further, the refrigeration equipment is an air conditioner or a refrigerator.

The additional aspects and advantages of the present application will become apparent in the following description, or be understood through the practice of the present application.

Description of the drawings

The above and/or additional aspects and advantages of the present application will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, in which:

Fig. 1 shows a schematic structural diagram of a compressor according to an embodiment of the present application;

Fig. 2 shows a schematic structural diagram of a crankshaft balance weight according to an embodiment of the present application.

Among them, the corresponding relationship between the reference signs and component names in Figures 1 and 2 is:

100 compressor, 110 drive motor, 111 stator, 112 rotor, 120 compression assembly, 121 first cylinder, 122 first piston, 123 first diaphragm, 124 second cylinder, 125 second piston, 126 second diaphragm, 130 crankshaft, 131 first eccentric part, 132 second eccentric part, 141 first bearing, 142 second bearing, 143 auxiliary bearing, 144 bearing seat, 145 rolling bearing, 146 bracket, 151 rotor balance weight, 154 crankshaft balance weight, 160 Housing, 170 isolation cover, 171 opening, 180 first exhaust valve, 190 second exhaust valve, 210 first muffler, 220 second muffler.

detailed description

In order to be able to understand the above objectives, features and advantages of the application more clearly, the application will be further described in detail below with reference to the accompanying drawings and specific implementations. It should be noted that the embodiments of the application and the features in the embodiments can be combined with each other if there is no conflict.

In the following description, many specific details are set forth in order to fully understand this application. However, this application can also be implemented in other ways different from those described here. Therefore, the scope of protection of this application is not covered by the specific details disclosed below. Limitations of the embodiment.

Hereinafter, the compressor 100 according to some embodiments of the present application will be described with reference to FIGS. 1 and 2.

Example one:

As shown in Figures 1 and 2, the first embodiment of the present application proposes a compressor 100 with a maximum speed greater than or equal to 150 rps (revolutions per second), which includes a housing 160, a drive motor 110, a compression assembly 120, and a crankshaft. 130. Bearing system and balance system. Among them, the bottom of the housing 160 is configured as an oil pool; the drive motor 110 includes a stator 111 and a rotor 112; the compression assembly 120 includes a first cylinder 121, a first piston 122, a second cylinder 124, a second piston 125, and a partitioned first cylinder 121 and the partition plate of the second cylinder 124, the first piston 122 is arranged in the first cylinder 121, the second piston 125 is arranged in the second cylinder 124; the crankshaft 130 has a first eccentric portion 131 and a second eccentric portion 132, An eccentric portion 131 and a second eccentric portion 132 are relatively distributed around the centerline of rotation of the crankshaft 130. The first piston 122 is sleeved on the first eccentric portion 131 and closes the first cylinder 121 with the partition plate and the first piston 122. The two pistons 125 are sleeved on the second eccentric part 132 and close the second cylinder 124 with the partition plate and the second piston 125, the crankshaft 130 passes through the rotor 112 and the compression assembly 120; the first cylinder 121, the partition plate, and the second cylinder 124 are arranged in sequence from near to far along the axial direction of the drive motor 110; the bearing system includes a first bearing 141, a second bearing 142 and an auxiliary bearing 143. The first bearing 141 is arranged on a side of the first cylinder 121 close to the drive motor 110. On the other hand, the second bearing 142 is arranged on the side of the second cylinder 124 away from the drive motor 110, and the auxiliary bearing 143 is arranged on the crankshaft 130 and on the side of the drive motor 110 away from the compression assembly 120; the balance system includes a rotor balance block 151 and a crankshaft The balance weight 154, the rotor balance weight 151 is set on the rotor 112, the crankshaft balance weight 154 is set on the crankshaft 130 and is located on the side of the second bearing 142 away from the first bearing 141; the isolation cover 170 partially surrounds the crankshaft balance weight 154.

The compressor 100 provided in the present application includes a housing 160, a drive motor 110, a compression assembly 120, a crankshaft 130, a bearing system, a balance system, and an isolation cover 170. Among them, the driving motor 110, the compression assembly 120, the crankshaft 130, the bearing system, the balance system and the isolation cover 170 are all arranged inside the housing 160. The driving motor 110 includes a stator 111 and a rotor 112. The stator 111 may be disposed on the casing 160 of the compressor 100, and the rotor 112 may be rotatably disposed in the stator 111. The compression assembly 120 includes a first cylinder 121, a first piston 122 disposed in the first cylinder 121, a second cylinder 124, a second piston 125 disposed in the second cylinder 124, and separating the first cylinder 121 and the second cylinder 124 The first piston 122 is sleeved on the first eccentric part 131 of the crankshaft 130, and the first cylinder 121 is sealed with the diaphragm and the first piston 122, and the second piston 125 is sleeved on the first eccentric portion 131 of the crankshaft 130. The second cylinder 124 is closed by the two eccentric parts 132, the partition plate and the second piston 125, and the crankshaft 130 passes through the rotor 112. The rotor 112 can drive the crankshaft 130 to rotate, thereby driving the first piston 122 in the first cylinder 121 The internal eccentric movement compresses the gas to do work, and the second piston 125 drives the eccentric movement in the second cylinder 124 to compress the gas to perform work. Among them, because the crankshaft 130 has a first eccentric part 131 and a second eccentric part 132, the existence of the two eccentric parts and the eccentric movement of the two pistons will produce unbalanced forces and moments, and then the bearing system and the balance system are provided. , It is beneficial to move the center of mass of the entire balance system downward, reduce the bending deformation of the crankshaft 130, improve the wear of the crankshaft 130 and the upper bearing, and improve the reliability of the first bearing 141, thereby improving the reliability of the compressor 100 operation, especially The improvement effect is more obvious in high speed and high load operation. Moreover, the first eccentric portion 131 and the second eccentric portion 132 are relatively distributed around the rotation center line of the crankshaft 130. That is, the first eccentric portion 131 and the second eccentric portion 132 are 180° apart from the rotation center line of the crankshaft 130, which is beneficial to improve the stability of the rotation of the crankshaft 130 and the stability of the motor operation.

Specifically, by arranging the rotor counterweight 151 on the rotor 112 and the crankshaft counterweight 154 on the crankshaft 130, the crankshaft counterweight 154 is located on the side of the second bearing 142 away from the first bearing 141 and can pass through the rotor counterweight 151. The centrifugal force brought by the first eccentric portion 131 and the second eccentric portion 132 can be balanced together with the crankshaft balance weight 154. Specifically, the centrifugal force brought by the first eccentric portion 131 can be balanced by the rotor balance weight 151, and the centrifugal force brought by the first eccentric portion 131 can also be balanced by the crankshaft 130 balance part to balance the centrifugal force brought by the second eccentric part 132, since there is no need for the rotor balance weight 151 to balance the first eccentric part 131 and the second eccentric part 132, the weight of the rotor balance weight 151 can be effectively reduced, which is conducive to the use of The entire balance system of the compressor 100 moves downwards, which improves the operating stability and reliability of the compressor 100. Moreover, by providing a first bearing 141 on the crankshaft 130 on the side of the first cylinder 121 close to the driving motor 110, and providing an auxiliary bearing 143 on the crankshaft 130 on the side of the driving motor 110 away from the compression assembly 120, the first bearing 141 and the auxiliary The bearing 143 can bear the centrifugal force and moment of the rotor balance weight 151 together, which can effectively reduce the wear of the first bearing 141, improve the reliability and service life of the first bearing 141, and avoid relying on the first bearing 141 alone in the related art. However, since the first bearing 141 is located on the side of the first cylinder 121 close to the drive motor 110 and is farther from the oil sump of the compressor 100, it is more difficult to supply oil than the second bearing 142, the lubricating oil temperature is higher, and the reliability is higher. Poor phenomenon occurs. Moreover, by providing the second bearing 142 on the crankshaft 130 on the side of the second cylinder 124 away from the drive motor 110, the centrifugal force and moment of the first eccentric portion 131, the first piston 122, the second eccentric portion 132 and the second piston 125 The function can be borne by the first bearing 141 and the second bearing 142 together to further reduce the wear of the first bearing 141. The centrifugal force and moment of the crankshaft balance weight 154 can be borne by the second bearing 142. Since the second bearing 142 is located on the side of the second cylinder 124 away from the drive motor 110, it is more likely to be lubricated by the oil in the oil pool, and the oil supply is sufficient. It is not easy to produce abrasion. Moreover, by setting the isolation cover 170 to partially surround the crankshaft balance weight 154, the crankshaft balance weight 154 can avoid excessive agitation of the oil in the oil sump during the rotation, and can ensure that the oil sump supplies oil to the crankshaft 130, the second bearing 142, and the like. Therefore, the compressor 100 proposed in the present application operates stably and reliably, and particularly meets the requirements of a high-speed compressor 100, such as a compressor 100 with a maximum speed of 180 rps, 200 rps, and 250 rps.

Further, as shown in FIG. 1, the isolation cover 170 is provided with an opening 171, and the oil in the oil pool can flow to the crankshaft balance weight 154 through the opening 171. The isolation cover 170 does not completely enclose the crankshaft balance weight 154, but leaves a gap, which is beneficial for the lubricating oil of the second bearing 142 to return to the oil pool to form a circulation. The opening 171 may be provided on the bottom wall or the side wall of the isolation cover.

Embodiment two:

The difference from the first embodiment is that the rotation center line of the first eccentric portion 131 and the second eccentric portion 132 around the crankshaft 130 is different by 90°. That is, the projections of the first eccentric portion 131 and the second eccentric portion 132 on a cross section of the crankshaft 130 differ by a central angle of 90°.

Of course, the centerline of rotation around the crankshaft 130 may differ by 60° or 120°, and so on.

Example three:

On the basis of the first or second embodiment above, it is further set that the center of mass of the rotor balance weight 151 and the first eccentric portion 131 are relatively distributed around the rotation center line of the crankshaft 130; the center of mass of the crankshaft balance weight 154 and the second eccentric portion 132 are further set Relatively distributed around the rotation center line of the crankshaft 130. So that no matter how the first eccentric portion 131 and the second eccentric portion 132 are distributed, the rotor balance weight 151 can be used to offset the unbalanced force and moment caused by the eccentric movement of the first eccentric portion 131 and the first piston 122, and The unbalanced force and moment caused by the eccentric movement of the second eccentric portion 132 and the second piston 125 are offset by the crankshaft balance weight 154. Since there is no need for the rotor balance weight 151 to balance the first eccentric portion 131 and the second eccentric portion 132 independently, the weight of the rotor balance weight 151 can be effectively reduced, which is beneficial to move the entire balance system of the compressor 100 down and improve the operation of the compressor 100 Stability and reliability.

In a specific embodiment, the rotor balance weight 151 is arranged on the side of the rotor 112 close to the auxiliary bearing 143.

In another specific embodiment, as shown in FIG. 1, the rotor balance weight 151 is arranged on the side of the rotor 112 close to the first bearing 141. It is beneficial to move the entire balance system down and improve the operating stability and reliability of the compressor 100.

In another specific embodiment, the rotor balance weight 151 includes a first rotor balance weight and a second rotor balance weight, the first rotor balance weight is arranged on the side of the rotor 112 close to the auxiliary bearing 143, and the second rotor balance weight is arranged on The rotor 112 is close to the side of the first bearing 141.

Further, the center of mass of the first rotor balance weight and the center of mass of the second rotor balance weight are relatively distributed in the extension direction of the rotation center line of the crankshaft 130. That is to say, the projections of the two on a cross section of the crankshaft 130 overlap, which facilitates the quick installation of the first rotor balance weight and the second rotor balance weight, and also facilitates, quickly and accurately realizes the imbalance force and the imbalance caused by the eccentric part. Cancellation of torque.

Of course, the center of mass of the first rotor balance weight and the center of mass of the second rotor balance weight may not be relatively distributed in the extension direction of the rotation center line of the crankshaft 130. Instead, the projection interval distribution on a cross section of the crankshaft 130.

Embodiment four:

In any of the above embodiments, as shown in FIGS. 1 and 2, the outer peripheral surface of the crankshaft balance weight 154 is further set to be a cylindrical surface, and the axis of the cylindrical surface is collinear with the rotation center line of the crankshaft 130. Since one end of the crankshaft 130 will extend into the oil sump of the compressor 100, the outer circumference of the crankshaft balance weight 154 will be filled with lubricating oil. By setting the outer peripheral surface of the crankshaft balance weight 154 to be a cylindrical surface, the axis of the cylindrical surface is aligned with that of the crankshaft 130. The collinear rotation centerline can effectively prevent the crankshaft 130 from squeezing the oil and doing work during the high-speed rotation process and losing energy efficiency.

In a specific embodiment, as shown in FIG. 2, the crankshaft balance weight 154 and the crankshaft 130 are connected together by screws. Both the crankshaft balance weight 154 and the crankshaft 130 are provided with threaded holes.

In another specific embodiment, the crankshaft balance weight 154 and the crankshaft 130 are interference-fitted together, and are installed by cold pressing or hot sleeve installation.

In another specific embodiment, the crankshaft balance weight 154 and the crankshaft 130 are fixed together by a pin.

In a specific embodiment, as shown in FIG. 2, the crankshaft balance weight 154 has a cylindrical shape, and its inner part is a hollow structure and part is a solid structure.

Embodiment five:

In any of the foregoing embodiments, as shown in FIG. 1, the compressor 100 further includes: a partition, which separates the first cylinder 121 and the second cylinder 124. The first bearing 141, the partition plate and the first piston 122 jointly seal the first cylinder 121; the second bearing 142, the partition plate and the second piston 125 jointly seal the second cylinder 124. Avoid gas leakage.

Further, as shown in FIG. 1, the partition includes a first partition 123 and a second partition 126. Both the first partition 123 and the second partition 126 are provided with exhaust holes, and the exhaust holes are provided with exhaust holes. The air valve, the first partition 123 and the second partition 126 enclose an exhaust cavity. Ensure that the exhaust is unobstructed.

Further, a first exhaust hole (not shown in the figure) is provided on the first bearing 141, a first exhaust valve 180 and a first muffler 210 are provided at the first exhaust hole, and a second bearing 142 is provided with There is a second exhaust hole (not shown in the figure). The second exhaust hole is provided with a second exhaust valve 190 and a second muffler 220. The crankshaft balance weight 154 is located in the second muffler 220 away from the first bearing 141 On the side. Conducive to reducing exhaust noise.

In a specific embodiment, the auxiliary bearing 143 is a sliding bearing or a rolling bearing 145 or an articulated bearing.

In a specific embodiment, the auxiliary bearing 143 is an integral bearing or a split bearing. It can be determined according to the fixing method of the auxiliary bearing 143 and the housing 160. The integrated bearing has low cost, and the split bearing is convenient for self-aligning installation.

Further, as shown in FIG. 1, when the auxiliary bearing 143 is a split bearing, the auxiliary bearing 143 includes a bearing seat 144, a rolling bearing 145, and a bracket 146. The bracket 146 is fixedly connected to the housing 160, and the bearing seat 144 is arranged on the bracket. On 146, the rolling bearing 145 is arranged on the bearing seat 144.

The embodiment of the second aspect of the present application proposes a refrigeration device, including: the compressor 100 as in any one of the foregoing embodiments.

Since the refrigeration equipment provided in the present application has the compressor 100 of any one of the above embodiments, it further has the beneficial effects of any one of the above embodiments, so it will not be repeated here.

Further, the refrigeration equipment also includes a heat exchanger and a throttle valve, which are directly or indirectly connected to the compressor 100 to form a refrigeration circuit or a heating circuit.

Further, the refrigeration equipment is an air conditioner or a refrigerator.

In this application, the term "plurality" refers to two or more than two, unless specifically defined otherwise. The terms "installed", "connected", "connected", "fixed" and other terms should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "connected" can be It is directly connected or indirectly connected through an intermediary. For those of ordinary skill in the art, the specific meanings of the above-mentioned terms in this application can be understood according to specific circumstances.

In the description of this specification, the description of the terms "one embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiments or examples are included in this application In at least one embodiment or example. In this specification, the schematic representations of the above-mentioned terms do not necessarily refer to the same embodiment or example. Moreover, the described specific features, structures, materials or characteristics can be combined in any one or more embodiments or examples in a suitable manner.

The above descriptions are only preferred embodiments of the application, and are not intended to limit the application. For those skilled in the art, the application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of this application shall be included in the protection scope of this application.

Claims

A compressor, wherein the compressor includes:

A shell, the bottom of the shell is configured as an oil sump;

Drive motor, including stator and rotor;

The compression assembly includes a first cylinder, a first piston, a second cylinder, and a second piston, the first piston is disposed in the first cylinder, and the second piston is disposed in the second cylinder;

The crankshaft has a first eccentric portion and a second eccentric portion, the first piston is sleeved on the first eccentric portion, the second piston is sleeved on the second eccentric portion, and the crankshaft passes through The rotor and the compression assembly;

The bearing system includes a first bearing, a second bearing and an auxiliary bearing. The first bearing is arranged on the side of the first cylinder close to the drive motor, and the second bearing is arranged on the second cylinder far away from the drive motor. On one side of the drive motor, the auxiliary bearing is arranged on the crankshaft and located on the side of the drive motor away from the compression assembly;

The balance system includes a rotor balance weight and a crankshaft balance weight. The rotor balance weight is arranged on the rotor, and the crankshaft balance weight is arranged on the crankshaft and is located on a side of the second bearing away from the first bearing. side;

An isolation cover partially surrounds the crankshaft balance weight.
The compressor according to claim 1, wherein:

The first eccentric portion and the second eccentric portion are relatively distributed around the rotation center line of the crankshaft.
The compressor according to claim 1 or 2, wherein:

The center of mass of the rotor balance weight and the first eccentric portion are relatively distributed around the rotation center line of the crankshaft;

The center of mass of the crankshaft balance weight and the second eccentric portion are relatively distributed around the rotation center line of the crankshaft.
The compressor according to any one of claims 1 to 3, wherein:

The rotor balance weight is arranged on the side of the rotor close to the auxiliary bearing; or

The rotor balance weight is arranged on a side of the rotor close to the first bearing.
The compressor according to any one of claims 1 to 3, wherein:

The rotor balance weight includes a first rotor balance weight and a second rotor balance weight, the first rotor balance weight is arranged on the side of the rotor close to the auxiliary bearing, and the second rotor balance weight is arranged on the The rotor is close to the side of the first bearing.
The compressor according to claim 5, wherein:

The center of mass of the first rotor balance weight and the center of mass of the second rotor balance weight are relatively distributed in the extension direction of the rotation center line of the crankshaft.
The compressor according to any one of claims 1 to 6, wherein:

The outer peripheral surface of the crankshaft balance weight is a cylindrical surface, and the axis of the cylindrical surface is collinear with the rotation center line of the crankshaft.
The compressor according to claim 7, wherein:

The crankshaft balance weight and the crankshaft are connected together by screws, or the crankshaft balance weight and the crankshaft are interference-fitted together, or the crankshaft balance weight and the crankshaft are fixed together by a pin.
The compressor according to any one of claims 1 to 6, wherein:

The maximum speed of the compressor is greater than 150 rps.
The compressor according to any one of claims 1 to 6, wherein:

The isolation cover is provided with an opening, and the oil in the oil pool can flow to the crankshaft balance weight through the opening.
The compressor according to any one of claims 1 to 6, wherein the compressor further comprises:

A partition, which separates the first cylinder and the second cylinder;

The first bearing, the partition plate and the first piston jointly close the first cylinder;

The second bearing, the partition plate and the second piston jointly close the second cylinder.
The compressor according to claim 11, wherein:

The partition includes a first partition and a second partition. Both the first partition and the second partition are provided with exhaust holes, and an exhaust valve is provided at the exhaust holes. The first partition and the second partition enclose an exhaust cavity.
The compressor according to any one of claims 1 to 6, wherein:

The first bearing is provided with a first exhaust hole, the first exhaust hole is provided with a first exhaust valve and a first muffler, and the second bearing is provided with a second exhaust hole, so A second exhaust valve and a second muffler are provided at the second exhaust hole, and the crankshaft balance weight is located on a side of the second muffler away from the first bearing.
The compressor according to any one of claims 1 to 6, wherein:

The auxiliary bearing is a sliding bearing or a rolling bearing or an articulated bearing.
A refrigeration equipment, including:

The compressor according to any one of claims 1 to 14.