CN110685911A

CN110685911A - Compressor and refrigeration equipment

Info

Publication number: CN110685911A
Application number: CN201910932835.3A
Authority: CN
Inventors: 罗承卓; 谭琴; 朱晓涵
Original assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Current assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Priority date: 2019-09-29
Filing date: 2019-09-29
Publication date: 2020-01-14
Also published as: WO2021056796A1

Abstract

The invention provides a compressor and refrigeration equipment. The compressor includes: a housing; a stator and a rotor; the device comprises a first cylinder, a first piston arranged in the first cylinder, a second cylinder and a second piston arranged in the second cylinder; the crankshaft is provided with a first eccentric part and a second eccentric part, a first piston is sleeved on the first eccentric part, a second piston is sleeved on the second eccentric part, and the crankshaft penetrates through the rotor and the compression assembly; the bearing system comprises a first bearing, a second bearing and an auxiliary bearing, wherein the first bearing is arranged on one side of the first cylinder close to the driving motor, the second bearing is arranged on one side of the second cylinder far away from the driving motor, and the auxiliary bearing is arranged on the crankshaft and is positioned on one side of the driving motor far away from the compression assembly; the balance system comprises a rotor balance block and a crankshaft balance block, the rotor balance block is arranged on the rotor, and the crankshaft balance block is arranged on the crankshaft and is positioned on one side, far away from the first bearing, of the second bearing; the isolation cover portion surrounds the crankshaft balance block. The reliability of high-speed operation of the compressor is improved.

Description

Compressor and refrigeration equipment

Technical Field

The invention belongs to the technical field of compressors, and particularly relates to a compressor and refrigeration equipment.

Background

In the rolling rotor compressor, a rotor, an upper bearing, a cylinder and a lower bearing are sequentially arranged in the axial direction of a crankshaft, the crankshaft with an eccentric part rotates under the driving of the rotor, and a piston sleeved on the eccentric part does eccentric motion in the cylinder to compress gas to work. Due to the existence of the eccentric part and the eccentric motion of the piston, balance blocks are required to be arranged on the upper side and the lower side of the rotor to offset unbalanced force and moment. 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 act on the crankshaft, and bending deformation of the crankshaft generated by the centrifugal force and the bending moment is mainly restrained by the upper bearing.

With the trend of high efficiency, miniaturization and high speed of compressors, the shaft diameter of the crankshaft is designed to be smaller and the rigidity of the crankshaft is poorer in order to improve the mechanical efficiency. And because the centrifugal force is proportional to the square of the rotating speed, for a high-rotating-speed compressor, the crankshaft can seriously deform under the action of the centrifugal force and the bending moment generated by the balance block on the rotor, and the crankshaft and the upper bearing are abraded, so that the reliability of the upper bearing is poor, and further the reliability of the compressor is poor.

Disclosure of Invention

The present invention is directed to solving one of the technical problems of the prior art or the related art.

To this end, a first aspect of the invention proposes a compressor.

A second aspect of the invention proposes a refrigeration device.

In view of this, according to a first aspect of the present invention, there is provided a compressor comprising: the bottom of the shell is configured as an oil pool; a driving motor including a stator and a rotor; the compression assembly comprises a first cylinder, a first piston, a second cylinder and a second piston, wherein the first piston is arranged in the first cylinder, and the second piston is arranged in the second cylinder; the crankshaft is provided with a first eccentric part and a second eccentric part, a first piston is sleeved on the first eccentric part, a second piston is sleeved on the second eccentric part, and the crankshaft penetrates through the rotor and the compression assembly; the bearing system comprises a first bearing, a second bearing and an auxiliary bearing, wherein the first bearing is arranged on one side, close to the driving motor, of the first cylinder, the second bearing is arranged on one side, far away from the driving motor, of the second cylinder, and the auxiliary bearing is arranged on the crankshaft and is positioned on one side, far away from the compression assembly, of the driving motor; the balance system comprises a rotor balance block and a crankshaft balance block, wherein the rotor balance block is arranged on the rotor, and the crankshaft balance block is arranged on the crankshaft and is positioned on one side, far away from the first bearing, of the second bearing; and the isolation cover partially surrounds the crankshaft balance block.

The invention provides a compressor, which comprises a shell, a driving motor, a compression assembly, a crankshaft, a bearing system, a balance system and an isolation cover. Wherein, the bottom of casing is constructed into the oil bath, can hold lubricating oil, and driving motor, compression assembly, bent axle, bearing system, balanced system and cage all set up in the casing. The drive motor includes a stator that may be disposed on a housing of the compressor and a rotor rotatably disposed within the stator. The compression assembly comprises 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 eccentric part of the crankshaft is sleeved with the first piston, the second eccentric part of the crankshaft is sleeved with the second piston, the crankshaft penetrates through a rotor, the rotor can drive the crankshaft to rotate, the first piston is driven to do eccentric motion compressed gas in the first cylinder to do work, and the second piston is driven to do eccentric motion compressed gas in the second cylinder to do work. The crankshaft is provided with the first eccentric part and the second eccentric part, unbalanced force and moment can be generated due to the existence of the two eccentric parts and the eccentric motion of the two pistons, and further, by arranging the bearing system and the balance system, the center of mass of the whole balance system can be favorably moved downwards, namely the center of mass is moved downwards, the bending deformation of the crankshaft is reduced, the abrasion of the crankshaft and an upper bearing is improved, the reliability of the first bearing is improved, the reliability of the operation of the compressor is improved, and the improvement effect is more obvious particularly in high-speed and high-load operation.

Specifically, through set up the rotor balancing piece on the rotor, and set up the bent axle balancing piece on the bent axle, make the bent axle balancing piece be located one side that first bearing was kept away from to the second bearing, accessible rotor balancing piece and bent axle balancing piece balance the centrifugal force that first eccentric portion and second eccentric portion brought jointly, specifically, the centrifugal force that first eccentric portion brought is balanced to the accessible rotor balancing piece, also can balance the centrifugal force that second eccentric portion brought through bent axle balancing piece, owing to need not first eccentric portion of rotor balancing piece and second eccentric portion of rotor balancing piece balance alone, can effectively reduce the weight of rotor balancing piece, be favorable to making the whole balanced system of compressor move down, the operating stability and the reliability of compressor are improved. And, one side through being close to driving motor at first cylinder on the bent axle sets up first bearing, one side that driving motor kept away from compression assembly on the bent axle sets up auxiliary bearing, make first bearing and auxiliary bearing can undertake the centrifugal force and the moment effect of rotor balancing piece together, can effectively reduce the wearing and tearing of first bearing, improve the reliability and the life of first bearing, it undertakes to rely on first bearing alone in the correlation technique to avoid appearing, and because first bearing is located one side that first cylinder is close to driving motor, it is far away from the oil bath of compressor, the oil supply is more difficult for the second bearing, the lubricating oil temperature is higher, the relatively poor phenomenon of reliability takes place. And, through set up the second bearing on the bent axle on one side that the second cylinder keeps away from driving motor for the centrifugal force and the moment effect of first eccentric part, first piston, second eccentric part and second piston can be born together through first bearing and second bearing, further reduce the wearing and tearing of first bearing. And the centrifugal force and the moment effect of bent axle balancing piece can be born through the second bearing, because the second bearing is located the second cylinder and keeps away from one side of driving motor, are lubricated by the oil in the oil bath more easily, and the fuel feeding is sufficient, and then difficult production wearing and tearing. And, through setting for the crankshaft balancing piece of isolation cover part branch enclosure, can avoid the crankshaft balancing piece to excessively stir the oil in the oil bath in the rotation process, can ensure that the oil bath supplies oil to bent axle, second bearing etc.. The compressor proposed by the application thus operates stably and reliably, and particularly meets the requirements of high-speed compressors, such as compressors with the highest speed of more than 150rps (revolutions per second).

In addition, according to the compressor in the above technical solution provided by the present invention, the following additional technical features may be further provided:

in some possible designs, the first eccentric portion and the second eccentric portion are relatively distributed about a rotational centerline of the crankshaft.

In the design, the first eccentric part and the second eccentric part are relatively distributed around the rotation center line of the crankshaft, so that the stability of the rotation of the crankshaft is improved, and the stability of the operation of the motor is improved.

In some possible designs, the center of mass of the rotor counterbalance is distributed opposite to the first eccentric portion around the rotation center line of the crankshaft; the center of mass of the crankshaft balance weight and the second eccentric part are distributed oppositely around the rotation center line of the crankshaft.

In this design, through making the barycenter of rotor balancing piece and first eccentric portion distribute relatively around the rotation center line of bent axle, the off-balance force and moment that are brought by the eccentric motion of first eccentric portion and first piston are offset to accessible rotor balancing piece, and through making the barycenter of bent axle balancing piece and the relative distribution of the rotation center line of second eccentric portion around the bent axle of second eccentric portion, off-balance force and moment that are brought by the eccentric motion of second eccentric portion and second piston are offset to accessible crankshaft balancing piece, owing to need not first eccentric portion of rotor balancing piece alone and second eccentric portion, can effectively reduce the weight of rotor balancing piece, be favorable to making the whole balanced system of compressor move down, improve the operating stability and the reliability of compressor.

In some possible designs, the rotor counterbalance is disposed on a side of the rotor adjacent to the auxiliary bearing.

In other possible designs, the rotor counterbalance is disposed on a side of the rotor proximate the first bearing. The whole balance system can be moved down, and the operation stability and reliability of the compressor can be improved.

In other possible designs, the rotor balancing weights include a first rotor balancing weight disposed on a side of the rotor proximate the auxiliary bearing and a second rotor balancing weight disposed on a side of the rotor proximate the first bearing.

In this design, the rotor balancing piece can set up the both sides at the rotor, and first rotor balancing piece setting is close to one side of auxiliary bearing at the rotor promptly, and the second rotor balancing piece setting is close to one side of first bearing at the rotor, can set up the concrete position of rotor balancing piece according to balanced demand.

Further, the center of mass of the first rotor counterbalance and the center of mass of the second rotor counterbalance are distributed relatively in the extending direction of the rotation center line of the crankshaft. The first rotor balance block and the second rotor balance block are convenient to install quickly, and the unbalance force and the moment brought by the eccentric part can be offset conveniently, quickly and accurately.

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

In this design, because the one end of bent axle can stretch into the oil sump of compressor, the periphery of bent axle balancing piece can be filled with lubricating oil, and then the outer peripheral face through setting for the bent axle balancing piece is the face of cylinder and makes the axis of face of cylinder and the rotation center line collineation of bent axle, can effectively avoid the bent axle to extrude and do work and lose the efficiency oil at high-speed rotatory in-process.

In some possible designs, the crankshaft counterbalance is connected with the crankshaft through a screw; or the crankshaft balance block and the crankshaft are assembled together in an interference fit mode and are installed by means of cold pressing or hot sleeving; or the crankshaft balance block and the crankshaft are fixed together through a pin key.

In some possible designs, the maximum rotational speed of the compressor is greater than 150 rps. The requirement of high rotating speed of the compressor in the related technology can be met, and the operation is stable and reliable.

In some possible designs, the cage has openings through which oil in the sump can flow to the crankshaft counterbalance. The isolation cover does not completely seal the crankshaft balance block, and a gap is reserved, so that the lubricating oil of the second bearing can return to the oil pool to form circulation.

In some possible designs, the compressor further comprises: and a partition plate partitioning 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. Avoiding gas leakage.

Furthermore, the baffle includes first baffle and second baffle, has all seted up the exhaust hole on first baffle and the second baffle, and exhaust hole department is equipped with discharge valve, and first baffle and second baffle enclose into there is the exhaust chamber. Ensuring smooth exhaust.

In some possible designs, a first exhaust hole is formed in the first bearing, a first exhaust valve and a first silencer are arranged at the position of the first exhaust hole, a second exhaust hole is formed in the second bearing, a second exhaust valve and a second silencer are arranged at the position of the second exhaust hole, and the crankshaft balance block is located on one side, away from the first bearing, of the second silencer. It is favorable for reducing exhaust noise.

In some possible designs, the auxiliary bearing is a sliding bearing or a rolling bearing or a spherical plain bearing.

In some possible designs, the auxiliary bearing is a one-piece bearing or a split bearing. It may be determined according to the fixing manner of the auxiliary bearing and the housing. The integrated bearing is low in cost, and the split bearing is convenient to center and install.

Further, under the condition that the auxiliary bearing is a split bearing, the auxiliary bearing comprises a bearing seat, a rolling bearing and a support, the support is fixedly connected with the shell, the bearing seat is arranged on the support, and the rolling bearing is arranged on the bearing seat.

A second aspect of the present invention provides a refrigeration apparatus comprising: a compressor according to any one of the preceding claims. The refrigeration equipment provided by the invention has the advantages of any technical scheme due to the compressor of any technical scheme, and the details are not repeated herein. Wherein, any one of the above designs forms a technical solution in combination with the compressor of the first aspect.

Furthermore, the refrigeration equipment also comprises a heat exchanger and a throttle valve which are directly or indirectly connected with the compressor to form a refrigeration loop or a heating loop.

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

Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

fig. 1 shows a schematic structural view of a compressor according to an embodiment of the present invention;

FIG. 2 shows a schematic diagram of a crankshaft counterbalance according to an embodiment of the present invention.

Wherein, the correspondence between the reference numbers and the component names in fig. 1 and fig. 2 is:

100 compressor, 110 driving motor, 111 stator, 112 rotor, 120 compression assembly, 121 first cylinder, 122 first piston, 123 first partition plate, 124 second cylinder, 125 second piston, 126 second partition plate, 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 block, 154 crankshaft balance block, 160 housing, 170 cage, 171 opening, 180 first exhaust valve, 190 second exhaust valve, 210 first muffler, 220 second muffler.

Detailed Description

In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.

A compressor 100 according to some embodiments of the present invention is described below with reference to fig. 1 and 2.

The first embodiment is as follows:

as shown in fig. 1 and 2, the first embodiment of the present invention provides a compressor 100 with a maximum rotation speed of 150rps (revolutions per second) or more, which includes a housing 160, a driving motor 110, a compression assembly 120, a crankshaft 130, a bearing system and a balance system. Wherein the bottom of the casing 160 is configured as an oil sump; the driving 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 partition separating the first cylinder 121 and the second cylinder 124, the first piston 122 being disposed in the first cylinder 121, the second piston 125 being disposed in the second cylinder 124; the crankshaft 130 has a first eccentric portion 131 and a second eccentric portion 132, the first eccentric portion 131 and the second eccentric portion 132 are distributed relatively around the rotation center line of the crankshaft 130, the first piston 122 is sleeved on the first eccentric portion 131 and seals the first cylinder 121 with the partition plate and the first piston 122, the second piston 125 is sleeved on the second eccentric portion 132 and seals the second cylinder 124 with the partition plate and the second piston 125, and 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 sequentially arranged from near to far along the axial direction of the driving motor 110; the bearing system comprises a first bearing 141, a second bearing 142 and an auxiliary bearing 143, wherein the first bearing 141 is arranged on one side of the first cylinder 121 close to the driving motor 110, the second bearing 142 is arranged on one side of the second cylinder 124 far from the driving motor 110, and the auxiliary bearing 143 is arranged on the crankshaft 130 and is positioned on one side of the driving motor 110 far from the compression assembly 120; the balance system comprises a rotor balance weight 151 and a crankshaft balance weight 154, wherein the rotor balance weight 151 is arranged on the rotor 112, and the crankshaft balance weight 154 is arranged on the crankshaft 130 and is positioned on one side, far away from the first bearing 141, of the second bearing 142; and a cage 170 partially surrounding the crankshaft counterbalance 154.

The compressor 100 of the present invention includes a housing 160, a driving motor 110, a compression assembly 120, a crankshaft 130, a bearing system, a balance system, and a cage 170. The driving motor 110, the compression assembly 120, the crankshaft 130, the bearing system, the balance system, and the isolation cover 170 are disposed inside the housing 160. The driving motor 110 includes a stator 111 and a rotor 112, the stator 111 may be disposed on a housing 160 of the compressor 100, and the rotor 112 may be rotatably disposed within 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 a partition separating the first cylinder 121 and the second cylinder 124, wherein the first piston 122 is sleeved on the first eccentric portion 131 of the crankshaft 130, the partition and the first piston 122 enclose the first cylinder 121, the second piston 125 is sleeved on the second eccentric portion 132 of the crankshaft 130, the partition and the second piston 125 enclose the second cylinder 124, the crankshaft 130 passes through the rotor 112, the rotor 112 can drive the crankshaft 130 to rotate, and further drive the first piston 122 to perform eccentric motion in the first cylinder 121 to compress gas to perform work, and drive the second piston 125 to perform eccentric motion in the second cylinder 124 to perform work. Because the crankshaft 130 is provided with the first eccentric part 131 and the second eccentric part 132, unbalanced force and moment can be generated due to the existence of the two eccentric parts and the eccentric motion of the two pistons, and further, by arranging the bearing system and the balance system, the center of mass of the whole balance system can be moved downwards, the bending deformation of the crankshaft 130 can be reduced, the abrasion of the crankshaft 130 and an upper bearing can be improved, the reliability of the first bearing 141 can be improved, the operation reliability of the compressor 100 can be improved, and the improvement effect is more obvious particularly in high-speed and high-load operation. Also, the first eccentric portion 131 and the second eccentric portion 132 are relatively distributed around the rotational center line of the crankshaft 130. That is, the difference between the rotation center lines of the first eccentric portion 131 and the second eccentric portion 132 around the crankshaft 130 is 180 °, which is beneficial to improving the rotation stability of the crankshaft 130 and the operation stability of the motor.

Specifically, by providing the rotor balancer 151 on the rotor 112 and providing the crankshaft balancer 154 on the crankshaft 130, the crankshaft balancer 154 is located on the side of the second bearing 142 away from the first bearing 141, the centrifugal forces of the first eccentric portion 131 and the second eccentric portion 132 can be balanced by the rotor balancer 151 and the crankshaft balancer 154, specifically, the centrifugal force of the first eccentric portion 131 can be balanced by the rotor balancer 151, the centrifugal force of the second eccentric portion 132 can be balanced by the crankshaft 130, and since the first eccentric portion 131 and the second eccentric portion 132 do not need to be balanced by the rotor balancer 151 alone, the weight of the rotor balancer 151 can be effectively reduced, which is beneficial to moving down the whole balance system of the compressor 100, and improving the operation stability and reliability of the compressor 100. Moreover, the first bearing 141 is disposed on the side of the first cylinder 121 close to the driving motor 110 on the crankshaft 130, and the auxiliary bearing 143 is disposed on the side of the driving motor 110 far from the compression assembly 120 on the crankshaft 130, so that the first bearing 141 and the auxiliary bearing 143 can bear the centrifugal force and moment of the rotor balance block 151 together, thereby effectively reducing the wear of the first bearing 141, improving the reliability and the service life of the first bearing 141, and avoiding the phenomenon that the first bearing 141 is solely used for bearing in the related art, and because the first bearing 141 is disposed on the side of the first cylinder 121 close to the driving motor 110, the first bearing 141 is far from the oil sump of the compressor 100, the oil supply is difficult relative to the second bearing 142, the temperature of the lubricating oil is high, and the reliability is poor. Further, by providing the second bearing 142 on the crankshaft 130 on the side of the second cylinder 124 remote 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 can be borne by the first bearing 141 and the second bearing 142 together, and the wear of the first bearing 141 is further reduced. The centrifugal force and moment of the crankshaft balance weight 154 can be borne by the second bearing 142, and the second bearing 142 is located on the side of the second cylinder 124 far away from the driving motor 110, so that the second cylinder is more easily lubricated by oil in the oil sump, and the oil supply is sufficient, so that the wear is not easily caused. Furthermore, by providing the isolation cover 170 to partially surround the crankshaft balance weight 154, the crankshaft balance weight 154 is prevented from excessively stirring the oil in the oil sump during rotation, and the oil sump can be ensured to supply oil to the crankshaft 130, the second bearing 142, and the like. The compressor 100 proposed by the present application thus operates stably and reliably, particularly meeting the requirements of high speed compressors 100, such as compressors 100 with maximum speeds of 180rps, 200rps, and 250 rps.

Further, as shown in fig. 1, an opening 171 is provided on the cage 170, and the oil in the oil sump can flow to the crankshaft balancer 154 through the opening 171. The isolation cover 170 does not completely enclose the crankshaft counterweight 154, but leaves a void that facilitates circulation of the lubricating oil of the second bearing 142 back into the sump. The opening 171 may be provided on the bottom wall or on the side wall of the shield.

Example two:

unlike the first embodiment, the first eccentric portion 131 and the second eccentric portion 132 are different by 90 ° about the rotation center line of the crankshaft 130. That is, the projections of the first eccentric portion 131 and the second eccentric portion 132 on a cross section of the crankshaft 130 are different by a central angle of 90 °.

Of course, it may be different by 60 ° or 120 ° around the rotational center line of crankshaft 130, or the like.

Example three:

in addition to the first or second embodiment, the center of mass of the rotor balance weight 151 and the first eccentric portion 131 are further set to be distributed relatively around the rotation center line of the crankshaft 130; the center of mass of the crankshaft counterbalance 154 is distributed opposite to the second eccentric portion 132 about the rotational center line of the crankshaft 130. So that the unbalanced force and moment by the eccentric motion of the first eccentric portion 131 and the first piston 122 can be offset by the rotor balance weight 151 and the unbalanced force and moment by the eccentric motion of the second eccentric portion 132 and the second piston 125 can be offset by the crankshaft balance weight 154, regardless of the distribution of the first eccentric portion 131 and the second eccentric portion 132. Since the first eccentric portion 131 and the second eccentric portion 132 are not required to be balanced by the rotor balancing block 151 alone, the weight of the rotor balancing block 151 can be effectively reduced, which is beneficial to moving down the whole balancing system of the compressor 100, and improving the operation stability and reliability of the compressor 100.

In one particular embodiment, the rotor counterbalance 151 is disposed on a side of the rotor 112 proximate the auxiliary bearing 143.

In another specific embodiment, as shown in FIG. 1, the rotor weight 151 is disposed on a side of the rotor 112 adjacent to the first bearing 141. The whole balance system is moved down, and the operation stability and reliability of the compressor 100 are improved.

In another specific embodiment, the rotor weights 151 include a first rotor weight disposed on a side of the rotor 112 adjacent to the auxiliary bearing 143 and a second rotor weight disposed on a side of the rotor 112 adjacent to 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 distributed relatively in the extending direction of the rotation center line of the crankshaft 130. That is, the projections of the two on a cross section of the crankshaft 130 are overlapped, so that the first rotor balance weight and the second rotor balance weight can be conveniently and quickly mounted, and the unbalance force and the moment brought by the eccentric part can be conveniently, quickly and accurately offset.

Of course, the center of mass of the first rotor counterbalance and the center of mass of the second rotor counterbalance may not be located relative to each other in the direction in which the center line of rotation of crankshaft 130 extends. But rather are spaced apart in projection across a cross-section of crankshaft 130.

Example four:

in any of the above embodiments, as shown in fig. 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. Because one end of the crankshaft 130 extends into the oil sump of the compressor 100, the periphery of the crankshaft balance weight 154 is filled with lubricating oil, and by setting the outer peripheral surface of the crankshaft balance weight 154 to be a cylindrical surface and making the axis of the cylindrical surface collinear with the rotation center line of the crankshaft 130, the energy efficiency loss caused by the extrusion and the work of the crankshaft 130 on the oil in the high-speed rotation process can be effectively avoided.

In one embodiment, as shown in FIG. 2, the crankshaft counterbalance 154 is bolted to the crankshaft 130. Threaded bores are provided in both the crankshaft counterbalance 154 and the crankshaft 130.

In another embodiment, the crankshaft counterbalance 154 is an interference fit with the crankshaft 130, and is installed by cold pressing or shrink fitting.

In another embodiment, the crankshaft counterbalance 154 is pinned to the crankshaft 130.

In one embodiment, as shown in FIG. 2, the crankshaft counterbalance 154 is cylindrical in shape, with an inner portion that is hollow and a portion that is solid.

Example five:

in any of the above embodiments, as shown in fig. 1, the compressor 100 further includes: and a partition plate partitioning the first cylinder 121 and the second cylinder 124. The first bearing 141, the partition plate and the first piston 122 jointly enclose the first cylinder 121; the second bearing 142, the diaphragm and the second piston 125 together enclose the second cylinder 124. Avoiding gas leakage.

Further, as shown in fig. 1, the partition plate includes a first partition plate 123 and a second partition plate 126, the first partition plate 123 and the second partition plate 126 are both provided with an exhaust hole, an exhaust valve is disposed at the exhaust hole, and an exhaust cavity is defined by the first partition plate 123 and the second partition plate 126. Ensuring smooth exhaust.

Further, a first exhaust hole (not shown in the figure) is formed in the first bearing 141, a first exhaust valve 180 and a first muffler 210 are arranged at the first exhaust hole, a second exhaust hole (not shown in the figure) is formed in the second bearing 142, a second exhaust valve 190 and a second muffler 220 are arranged at the second exhaust hole, and the crankshaft balance weight 154 is located on one side, away from the first bearing 141, of the second muffler 220. It is favorable for reducing exhaust noise.

In a particular embodiment, the auxiliary bearing 143 is a sliding or rolling bearing 145 or a spherical plain bearing.

In a particular embodiment, the auxiliary bearing 143 is a one-piece bearing or a split bearing. May be determined according to the fixing manner of the auxiliary bearing 143 to the housing 160. The integrated bearing is low in cost, and the split bearing is convenient to center and install.

Further, as shown in fig. 1, in the case that 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 with the housing 160, the bearing seat 144 is disposed on the bracket 146, and the rolling bearing 145 is disposed on the bearing seat 144.

A second aspect of the present invention provides a refrigeration apparatus, including: the compressor 100 according to any of the above embodiments.

The refrigeration equipment provided by the present invention has the advantages of the compressor 100 according to any of the above embodiments, and therefore, the advantages of any of the above embodiments are not repeated herein.

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

In the present invention, the term "plurality" means two or more unless explicitly defined otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A compressor, comprising:

a housing, the bottom of the housing configured as an oil sump;

a driving motor including a stator and a rotor;

the compression assembly comprises a first cylinder, a first piston, a second cylinder and a second piston, wherein the first piston is arranged in the first cylinder, and the second piston is arranged in the second cylinder;

the crankshaft is provided with a first eccentric part and a second eccentric part, the first piston is sleeved on the first eccentric part, the second piston is sleeved on the second eccentric part, and the crankshaft penetrates through the rotor and the compression assembly;

the bearing system comprises a first bearing, a second bearing and an auxiliary bearing, wherein the first bearing is arranged on one side, close to the driving motor, of the first cylinder, the second bearing is arranged on one side, far away from the driving motor, of the second cylinder, and the auxiliary bearing is arranged on the crankshaft and is positioned on one side, far away from the compression assembly, of the driving motor;

the balance system comprises 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 positioned on one side, far away from the first bearing, of the second bearing;

a cage partially surrounding the crankshaft counterbalance.

2. The compressor of claim 1,

the first eccentric portion and the second eccentric portion are distributed relatively around a rotation center line of the crankshaft.

3. The compressor of claim 1,

the center of mass of the rotor balance weight and the first eccentric part are distributed oppositely around the rotation center line of the crankshaft;

the center of mass of the crankshaft balance weight and the second eccentric part are distributed oppositely around the rotation center line of the crankshaft.

4. The compressor of claim 1,

the rotor balance block is arranged on one side of the rotor close to the auxiliary bearing; or

The rotor balancing block is arranged on one side of the rotor close to the first bearing.

5. The compressor of claim 1,

the rotor balancing block comprises a first rotor balancing block and a second rotor balancing block, the first rotor balancing block is arranged on one side, close to the auxiliary bearing, of the rotor, and the second rotor balancing block is arranged on one side, close to the first bearing, of the rotor.

6. The compressor of claim 5,

the center of mass of the first rotor balance weight and the center of mass of the second rotor balance weight are distributed oppositely in the extending direction of the rotation center line of the crankshaft.

7. The compressor of any one of claims 1 to 6,

the peripheral surface of the crankshaft balance block is a cylindrical surface, and the axis of the cylindrical surface is collinear with the rotation center line of the crankshaft.

8. The compressor of claim 7,

the crankshaft balance weight and the crankshaft are connected together through a screw, or the crankshaft balance weight and the crankshaft are assembled together in an interference mode, or the crankshaft balance weight and the crankshaft are fixed together through a pin key.

9. The compressor of any one of claims 1 to 6,

the maximum rotational speed of the compressor is greater than 150 rps.

10. The compressor of any one of claims 1 to 6,

an opening is formed in the isolation cover, and oil in the oil pool can flow to the crankshaft balance block through the opening.

11. The compressor of any one of claims 1 to 6, further comprising:

a partition plate partitioning the first cylinder and the second cylinder;

the first bearing, the partition plate and the first piston jointly enclose the first cylinder;

the second bearing, the partition plate and the second piston jointly enclose the second cylinder.

12. The compressor of claim 11,

the partition plates comprise a first partition plate and a second partition plate, exhaust holes are formed in the first partition plate and the second partition plate, exhaust valves are arranged at the exhaust holes, and an exhaust cavity is defined by the first partition plate and the second partition plate.

13. The compressor of any one of claims 1 to 6,

the crankshaft balance block is located on one side, away from the first bearing, of the second silencer.

14. The compressor of any one of claims 1 to 6,

the auxiliary bearing is a sliding bearing or a rolling bearing or a joint bearing.

15. A refrigeration apparatus, comprising:

a compressor as claimed in any one of claims 1 to 14.