CN216044413U

CN216044413U - Compressor and air conditioner

Info

Publication number: CN216044413U
Application number: CN202122153856.0U
Authority: CN
Inventors: 胡余生; 魏会军; 阙沛祯; 周瑜; 崔雪梅
Original assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Current assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority date: 2021-09-07
Filing date: 2021-09-07
Publication date: 2022-03-15
Anticipated expiration: 2031-09-07

Abstract

The utility model provides a compressor and an air conditioner, wherein the compressor comprises: the partition plate assembly is arranged between the first cylinder and the second cylinder, the crankshaft comprises a middle shaft section positioned between the first cylinder and the second cylinder, and the partition plate assembly is arranged on the middle shaft section in a penetrating mode; the diaphragm assembly includes a first diaphragm that interfaces with the midshaft segment to form a diaphragm bearing for supporting the midshaft segment. According to the utility model, the abrasion of the joint of the middle section of the crankshaft and the first cylinder, the second cylinder, the first bearing and the second bearing due to bending is reduced, the contact stress is reduced, the problem of shaft system abrasion during high-frequency operation of the compressor is solved, the reliability of high-frequency operation of the small-shell large-displacement double-cylinder compressor is improved, the shaft system abrasion is improved and the operation frequency of the compressor is improved on the premise of ensuring the performance.

Description

Compressor and air conditioner

Technical Field

The utility model relates to the technical field of compressors, in particular to a compressor and an air conditioner.

Background

In recent years, the rotary compressor has become a trend of miniaturization, large displacement and high speed, i.e. the smaller the outer diameter of the rotary compressor, the larger the displacement of the compressor, and the compressor is accompanied with the demand of high speed operation.

The total compressor displacement vtotai NxV, N-number of cylinders, vtotai the displacement of a single cylinder, i.e., the size of the total compressor displacement depends on the displacement of a single cylinder and the number of cylinders. And the displacement V of a single cylinder of the compressor is pi H e (D-e), wherein H is the height of the cylinder, D is the inner diameter of the cylinder, e is the eccentric amount of the crankshaft, that is, the displacement of the single cylinder is in direct proportion to the height of the cylinder, the inner diameter of the cylinder and the eccentric amount of the crankshaft. When the inner diameter of the shell of the compressor is certain, the inner diameter of the cylinder has a maximum large value, and when the inner diameter of the cylinder reaches the range of the maximum large value and the displacement of the cylinder needs to be further improved, the height H of the cylinder can only be increased: the cylinder height is higher, and it is big that corresponding roller gleitbretter and bent axle eccentric section atress are big, and it is big to have the wearing and tearing risk, and the cylinder height corresponds the bearing span big simultaneously, and bent axle bearing edge contact stress is too big, and the wearing and tearing problem easily appears in the bearing system, and compressor reliability risk is big. In addition, as the displacement of the individual cylinder increases, the corresponding exhaust passage needs to be increased.

Patent CN 212376877U proposes a technical route of a multi-cylinder rotary compressor (at least including 4 cylinders), which realizes large displacement by increasing the number of cylinders, and effectively reduces resultant force of gas borne by a crankshaft of the compressor, reduces bending degree of the crankshaft, reduces abrasion of the crankshaft, and ensures operation reliability of the compressor on the premise of improving refrigeration capacity of the compressor; however, the multi-cylinder technical route proposed by the patent has the problems of complex structure, high cost, uneconomic performance and the like.

The compressor and the air conditioner are researched and designed according to the utility model, because the compressor with more than two cylinders in the prior art has the technical problems that the height of a cylinder is increased and the length of a crankshaft is lengthened when the displacement is increased, and the crankshaft is bent between a first bearing and a second bearing due to the increase of the length when the compressor runs at high frequency, so that parts such as the crankshaft, the cylinder and the like are seriously abraded and the like.

SUMMERY OF THE UTILITY MODEL

Therefore, the technical problem to be solved by the utility model is to overcome the defect that a shafting abrasion exists when a compressor with more than two cylinders in the prior art is increased in displacement and operates under a high-frequency working condition, thereby providing a compressor and an air conditioner.

In order to solve the above problems, the present invention provides a compressor, comprising:

the partition plate assembly is arranged between the first cylinder and the second cylinder, the crankshaft comprises a middle shaft section positioned between the first cylinder and the second cylinder, and the partition plate assembly is arranged on the middle shaft section in a penetrating mode; the diaphragm assembly includes a first diaphragm that interfaces with the midshaft segment to form a diaphragm bearing for supporting the midshaft segment.

In some embodiments, the baffle assembly further comprises a second baffle: one axial end of the first partition plate is connected with the first cylinder, one axial end of the second partition plate is connected with the first partition plate, and the other axial end of the second partition plate is connected with the second cylinder;

the middle shaft section comprises a first middle section and a second middle section which are connected in the axial direction, the first partition plate is sleeved on the periphery of the first middle section and is in contact fit with the first middle section, and the first middle section can rotate relative to the first partition plate; the second baffle is located the periphery of second interlude and with do not contact between the second interlude and there is the clearance.

In some embodiments, the first intermediate section is a concentric circle section having a central axis that coincides with a rotational centerline of the crankshaft.

In some embodiments, the first partition is fixedly connected to the first cylinder, and the second partition is fixedly connected to the second cylinder; and/or the presence of a gas in the gas,

the axial height of the first partition is greater than the axial height of the second partition.

In some embodiments, a first cavity is disposed on the first partition plate and on a side opposite to the second partition plate, a second cavity is disposed on the second partition plate and on a side opposite to the first partition plate, the first cavity and the second cavity are butted to form a partition plate exhaust cavity, a first exhaust hole is disposed on the first partition plate, one end of the first exhaust hole can be communicated with the inside of the first cylinder, and the other end of the first exhaust hole can be communicated with the first cavity, so that exhaust gas in the first cylinder is introduced into the first cavity, a second exhaust hole is disposed on the second partition plate, one end of the second exhaust hole can be communicated with the inside of the second cylinder, and the other end of the second exhaust hole can be communicated with the second cavity, so that exhaust gas in the second cylinder is introduced into the second cavity.

In some embodiments, a first exhaust valve is disposed at the first exhaust hole, and a second exhaust valve is disposed at the second exhaust hole.

In some embodiments, further comprising a housing, the crankshaft, the first cylinder, the second cylinder, and the diaphragm assembly all located inside the housing; the height H of at least one cylinder in the first cylinder and the second cylinder, the cylinder inner diameter D and the inner diameter F of the shell meet the following requirements: H/D is not less than 0.45 and H/F is not less than 0.21.

In some embodiments, the maximum rotational speed of the compressor is greater than or equal to 120 rps; and/or the outer diameter of the shell is more than or equal to 160 mm.

In some embodiments, the crankshaft further includes a first eccentric portion, a second eccentric portion, and the compressor further includes a first roller and a second roller, the first roller is sleeved on the outer circumference of the first eccentric portion, and the first roller is located in the first cylinder and driven by the first eccentric portion to move in the first cylinder; the second roller is sleeved on the periphery of the second eccentric part, is positioned in the second cylinder and is driven by the second eccentric part to move in the second cylinder; the intermediate shaft section is located between the first and second eccentric portions.

In some embodiments, the crankshaft further comprises a long shaft and a short shaft, the crankshaft counterbalance is disposed on the short shaft, the motor rotor is disposed on the long shaft, the rotor counterbalance is connectively disposed on the motor rotor, the first eccentric portion is proximate to the long shaft relative to the second eccentric portion, the second eccentric portion is proximate to the short shaft relative to the first eccentric portion, and a center of mass of the rotor counterbalance is disposed opposite to the first eccentric portion about a rotational centerline of the crankshaft; the center of mass of the crankshaft counterbalance mass is disposed opposite the second eccentric portion about the centerline of rotation of the crankshaft.

In some embodiments, the diaphragm assembly further comprises a first bearing and a second bearing, the first bearing is sleeved on the long shaft and connected with the first air cylinder, and the first eccentric part is positioned between the first bearing and the diaphragm assembly; the rotor balancing block is arranged on one side, close to the first bearing, of the motor rotor, or the rotor balancing block is arranged on one side, far away from the first bearing, of the motor rotor.

In some embodiments, the rotor weights include a first rotor weight disposed on a side of the electric machine rotor proximate to the first bearing and a second rotor weight disposed on a side of the electric machine rotor distal from the first bearing.

In some embodiments, the center of mass of the first rotor counterbalance and the center of mass of the second rotor counterbalance enclose a center angle < 180 ° with the center of rotation of the crankshaft as a center of circle in a projection plane perpendicular to the axis of the crankshaft.

In some embodiments, the second bearing is sleeved on the short shaft to support the short shaft, a cover plate is further arranged on the short shaft, a main exhaust cavity is formed between the cover plate and the second bearing, and the crankshaft balance block is connected with the short shaft and is located in the main exhaust cavity.

In some embodiments, the center of mass of the crankshaft counterbalance and the center of mass of the rotor counterbalance are in relative distribution with a phase difference of 180 ° in a projection plane perpendicular to the axis of the crankshaft; and/or, in a projection plane perpendicular to the axis of the crankshaft, the crankshaft balance weight is of a fan-shaped structure; and/or the crankshaft balance block is in interference fit with the short shaft.

The utility model also provides an air conditioner, which comprises the compressor.

The compressor and the air conditioner provided by the utility model have the following beneficial effects:

according to the utility model, the partition plate assembly is arranged between the first cylinder and the second cylinder, the partition plate assembly is arranged on the middle shaft section of the crankshaft in a penetrating manner, the partition plate assembly comprises the first partition plate, the first partition plate is connected with the middle shaft section and forms a structural form of a bearing to support the middle shaft section of the crankshaft, the deflection and the deflection of the crankshaft can be effectively reduced, the abrasion of the middle section of the crankshaft at the connection part of the first cylinder, the second cylinder, the first bearing and the second bearing due to bending is effectively reduced, the contact stress is reduced, the stress on the first bearing and the second bearing is reduced, the problem of shafting abrasion in high-frequency operation of the compressor is effectively solved, the reliability in high-frequency operation of the small-shell large-displacement double-cylinder compressor is improved, the shafting abrasion is improved on the premise of ensuring the performance, the operation frequency of the compressor is improved, the effective abrasion reduction of the small-shell large-displacement double-cylinder compressor is realized, the compressor has a compact structure, Simple, stable and reliable operation, and especially meets the requirements of large-displacement and high-rotating-speed compressors.

Drawings

Fig. 1 is a sectional view of the interior of a compressor according to a first embodiment of the present invention;

FIG. 2 is a cross-sectional view of a portion of the pump body assembly of FIG. 1;

FIG. 3 is a cross-sectional view of a portion of the pump body rotor assembly of FIG. 1;

FIG. 4 is a cross-sectional view of a portion of a pump rotor assembly according to a second embodiment of the present invention;

FIG. 5 is a top view of the second cylinder of FIG. 1;

fig. 6 is a side cross-sectional view of the second cylinder of fig. 1.

The reference numerals are represented as:

1. a crankshaft; 11. a middle shaft section; 11a, a first intermediate section; 11b, a second intermediate section; 12. a first eccentric portion; 13. a second eccentric portion; 2. a first cylinder; 3. a second cylinder; 4. a bulkhead assembly; 41. a first separator; 42. a second separator; 5. a housing; 61. a first roller; 62. a second roller; 7. a baffle plate exhaust cavity; 71. a first cavity; 72. a second cavity; 8. a rotor counterbalance; 81. a first rotor balance weight; 82. a second rotor counterbalance; 9. a crankshaft counterbalance; 10. a motor rotor; 14. a long axis; 15. a minor axis; 16. a first bearing; 17. a second bearing; 18. a cover plate; 19. a motor stator; 20. a pump body assembly; 21. an upper cover; 100. a main exhaust chamber.

Detailed Description

In a first embodiment, as shown in fig. 1 to 3 and 5 to 6, the present invention provides a compressor, including:

the air cylinder comprises a crankshaft 1, a first air cylinder 2, a second air cylinder 3 and a partition plate assembly 4, wherein the partition plate assembly 4 is arranged between the first air cylinder 2 and the second air cylinder 3, the crankshaft 1 comprises a middle shaft section 11 positioned between the first air cylinder 2 and the second air cylinder 3, and the partition plate assembly 4 is arranged on the middle shaft section 11 in a penetrating mode; the diaphragm assembly 4 includes a first diaphragm 41, and the first diaphragm 41 is connected to the middle shaft section 11 to form a diaphragm bearing for supporting the middle shaft section 11.

According to the utility model, the partition plate assembly is arranged between the first cylinder and the second cylinder, the partition plate assembly is arranged on the middle shaft section of the crankshaft in a penetrating manner, the partition plate assembly comprises the first partition plate, the first partition plate is connected with the middle shaft section and forms a structural form of a bearing to support the middle shaft section of the crankshaft, the deflection and the deflection of the crankshaft can be effectively reduced, the abrasion of the middle section of the crankshaft at the connection part of the first cylinder, the second cylinder, the first bearing and the second bearing due to bending is effectively reduced, the contact stress is reduced, the stress on the first bearing and the second bearing is reduced, the problem of shafting abrasion in high-frequency operation of the compressor is effectively solved, the reliability in high-frequency operation of the small-shell large-displacement double-cylinder compressor is improved, the shafting abrasion is improved on the premise of ensuring the performance, the operation frequency of the compressor is improved, the effective abrasion reduction of the small-shell large-displacement double-cylinder compressor is realized, the compressor has a compact structure, Simple, stable and reliable operation, and especially meets the requirements of large-displacement and high-rotating-speed compressors. (the stress contrast after the auxiliary bearing is added is shown in table 1, the contact stress of the long and short shafts and the inclined deformation of the eccentric part are reduced by 40-50%, and the load shedding effect is obvious).

TABLE 1

Scheme(s)	Bearing without partition board	Bearing with partition plate
			Upper eccentric deformation mm/dip angle °	0.0251/0.00767	0.0134/0.0049
Lower eccentric deformation mm/dip angle °	0.0262/0.0066	0.0152/0.0032
			Short axis contact stress/MPa	35.5	22.1
Long axis contact stress/Mpa	39.2	21.3
			Intermediate shaft contact stress/Mpa	/	28.9

In some embodiments, the baffle plate assembly 4 further comprises a second baffle plate 42: one axial end of the first partition plate 41 is connected to the first cylinder 2, one axial end of the second partition plate 42 is connected to the first partition plate 41, and the other axial end of the second partition plate 42 is connected to the second cylinder 3;

the middle shaft section 11 comprises a first middle section 11a and a second middle section 11b which are connected along the axial direction, the first partition plate 41 is sleeved on the periphery of the first middle section 11a and is in contact fit with the first middle section 11a, and the first middle section 11a can rotate relative to the first partition plate 41; the second partition plate 42 is located on the outer periphery of the second intermediate section 11b without contact and with a gap from the second intermediate section 11 b. The first partition plate and the second partition plate can be respectively connected with the first cylinder and the second cylinder to play a role in sealing, and meanwhile, the first partition plate and the middle shaft section can play an effective supporting role in the middle shaft section through contact and matching, so that the middle part of the crankshaft is prevented from being bent, the stress is reduced, and the abrasion of a shaft system is reduced; the second baffle does not contact with the middle shaft section gap, and plays a role in axially sealing the first cylinder or the second cylinder through the second baffle.

Preferably, the first cylinder is an upper cylinder, the first partition plate connected with the first cylinder is an upper partition plate, the second cylinder is a lower cylinder, and the second partition plate connected with the second cylinder is a lower partition plate; or preferably, the first cylinder is a lower cylinder, the first partition plate connected with the first cylinder is a lower partition plate, the second cylinder is an upper cylinder, and the second partition plate connected with the second cylinder is an upper partition plate.

In some embodiments, the first intermediate section 11a is a concentric circle section, the central axis of which coincides with the rotational centerline of the crankshaft 1. The first middle section is matched with the first partition plate and is superposed with the rotation center line of the crankshaft, so that the first middle section and the crankshaft can rotate concentrically, the first partition plate can effectively support the crankshaft in a rotating mode, namely the first partition plate supports the crankshaft through a bearing, eccentricity is avoided, the supporting capacity of the shaft section is improved, and the abrasion of the crankshaft is reduced.

In some embodiments, the first partition plate 41 is fixedly connected to the first cylinder 2, and the second partition plate 42 is fixedly connected to the second cylinder 3; and/or the presence of a gas in the gas,

the axial height of the first partition plate 41 > the axial height of the second partition plate 42. The height H1 of the partition plate bearing is larger than the height H2 of the partition plate of the non-partition plate bearing, and the first partition plate in the schematic diagram shown in figure 2 is the partition plate bearing and is matched with the crankshaft in a concentric circle mode, so that H1 is larger than H2, and the effect of supporting the crankshaft can be effectively improved.

In some embodiments, a first cavity 71 is provided on the first partition 41 on a side opposite to the second partition 42, a second cavity 72 is formed in the second partition plate 42 on the side opposite to the first partition plate 41, the first cavity 71 and the second cavity 72 are butted to form a partition exhaust cavity 7, the first partition 41 is provided with a first exhaust hole not shown, one end of the first exhaust port not shown can communicate with the interior of the first cylinder 2 and the other end can communicate with the first cavity 71, to introduce the exhaust gas in the first cylinder 2 into the first cavity 71, the second partition plate 42 is provided with a second exhaust hole (not shown), one end of the second exhaust hole (not shown) can communicate with the inside of the second cylinder 3 and the other end can communicate with the second cavity 72 to introduce exhaust gas in the second cylinder 3 into the second cavity 72. The first partition plate and the second partition plate are provided with the cavities to be communicated with the exhaust cavity of the partition plate, so that the volume of the exhaust cavity can be increased, and the volumetric efficiency of the compressor is improved.

The cylinder bore is limited by the housing outer diameter and has an optimum range beyond which various reliability problems can exist. Under the condition that the inner diameter of a cylinder is limited, the problem of insufficient exhaust passages is inevitably brought by increasing the cylinder height to an extreme value range, the exhaust passages of the compressor related to the utility model are increased to 4 by exhausting through the partition plate, the exhaust loss of large displacement under the limit cylinder height and the cylinder diameter can be met in a reasonable range, and therefore, the partition plate of the compressor related to the utility model has the following advantages: the first partition plate and the second partition plate are both provided with exhaust holes, exhaust valves are arranged at the exhaust holes, and partition plate exhaust cavities are defined by the first partition plate and the second partition plate.

In some embodiments, a first exhaust valve is disposed at the first exhaust hole, and a second exhaust valve is disposed at the second exhaust hole. The two exhaust valves can respectively play a role in opening and closing the exhaust cavity of the partition plate.

In some embodiments, further comprising a housing 5, the crankshaft 1, the first cylinder 2, the second cylinder 3, and the diaphragm assembly 4 all being located inside the housing 5; the height H of at least one of the first cylinder 2 and the second cylinder 3, the cylinder inner diameter D and the inner diameter F of the shell 5 meet the following requirements: H/D is not less than 0.45 and H/F is not less than 0.21. The total displacement of the rotary compressor is the displacement of each cylinder, namely, the large displacement can be realized by increasing the number of cylinders and the displacement of a single cylinder. And the displacement V of a single cylinder is pi H e (D-e), where H is the height of the cylinder, D is the inner diameter of the cylinder, and e is the eccentricity of the crankshaft, i.e., the displacement of a single cylinder is proportional to the height of the cylinder, the inner diameter of the cylinder, and the eccentricity of the crankshaft. When the inner diameter F of the shell of the compressor is certain, the inner diameter of the cylinder has a maximum large value, and when the inner diameter of the cylinder reaches the range of the maximum large value and the displacement of the cylinder needs to be further improved, the height H of the cylinder can only be increased: the higher the cylinder height H. Therefore, the object of the present invention is to develop a small shell large displacement rotary double cylinder compressor satisfying H/D > 0.45 and H/F > 0.21.

The double-cylinder compressor provided by the utility model is a rotary double-cylinder compressor, and the compressor is characterized in that the inner diameter of a shell is small, the discharge capacity is large, and the number of cylinders is small (2), namely the double-cylinder compressor is characterized in that: the pump body assembly comprises a first cylinder and a second cylinder, wherein at least one of the height H of the cylinder, the inner diameter D of the cylinder and the inner diameter F of a shell of the compressor meets the following requirements: H/D is more than or equal to 0.45 and H/F is more than or equal to 0.21; (see schematic diagrams 1, 5 and 6).

Along with the increase of the height H of the cylinder, the bearing span H between the first bearing and the second bearing is increased, the deflection of the eccentric part of the crankshaft is large, the piston is seriously inclined, the contact stress between the crankshaft and the edge of the bearing is overlarge, so that the compressor is unstable in operation, and the bearing system is easy to have a wear problem. Aiming at the compressor with the structural characteristics, the auxiliary bearing, namely the clapboard bearing, is additionally arranged between the first bearing and the second bearing, so that the crank deflection and the stress of the first bearing and the second bearing can be effectively reduced, and the abrasion of a crank shaft is reduced.

In some embodiments, the maximum rotational speed of the compressor is greater than or equal to 120 rps; and/or the outer diameter of the shell 5 is more than or equal to 160 mm.

In some embodiments, the crankshaft 1 further includes a first eccentric portion 12, a second eccentric portion 13, the compressor further includes a first roller 61 and a second roller 62, the first roller 61 is sleeved on the outer circumference of the first eccentric portion 12, the first roller 61 is located in the first cylinder 2, and is driven by the first eccentric portion 12 to move in the first cylinder 2; the second roller 62 is sleeved on the outer periphery of the second eccentric portion 13, and the second roller 62 is located in the second cylinder 3 and driven by the second eccentric portion 13 to move in the second cylinder 3; the intermediate shaft section 11 is located between the first eccentric section 12 and the second eccentric section 13.

In some embodiments, the crankshaft 1 further comprises a long shaft 14 and a short shaft 15, the crankshaft balance weight 9 is disposed on the short shaft 15, the motor rotor 10 is disposed on the long shaft 14, the rotor balance weight 8 is disposed on the motor rotor 10 in a connected manner, the first eccentric portion 12 is close to the long shaft 14 relative to the second eccentric portion 13, the second eccentric portion 13 is close to the short shaft 15 relative to the first eccentric portion 12, and the center of mass of the rotor balance weight 8 is arranged opposite to the first eccentric portion 12 around the rotation center line of the crankshaft 1; the center of mass of the crankshaft balance mass 9 is arranged opposite to the second eccentric portion 13 about the rotational center line of the crankshaft 1.

During the operation of the crankshaft, the piston and the eccentric part follow the eccentric motion to generate unbalanced force and moment. When cylinder height and bore all are in great extreme value scope, it is big to correspond piston and bent axle eccentric portion quality, and the unbalance force and the moment that so correspond the production need balance through balanced system, set up conventional single rotor balancing piece, can't compromise performance, operating stability and shafting reliability: namely, the conventional single rotor balance block system can improve the reliability of a shaft system at a certain high rotating speed by reducing the height of a motor, but has large performance attenuation; the conventional single-rotor balance system can improve the reliability of a shafting at a certain high rotating speed by reducing the balance coefficient, but the compressor has larger vibration and poor operation stability. Therefore, the reliability of the compressor at a certain high rotating speed can be effectively ensured and the stability and the performance of the compressor at a high speed can be ensured by arranging the rotor balance block and the crankshaft balance block. The utility model relates to a balance system of a compressor, which comprises a rotor balance weight and a crankshaft balance weight, wherein the rotor balance weight is arranged on a rotor, and the crankshaft balance weight is arranged on a crankshaft.

The compressor crankshaft is provided with a first eccentric part, a second eccentric part and concentric circles arranged between the first eccentric part and the second eccentric part, wherein the first piston is sleeved on the first eccentric part, and the second piston is sleeved on the second eccentric part; and the partition plate comprises a first partition plate and a second partition plate, wherein one partition plate is a partition plate bearing and is matched with the concentric circle of the crankshaft.

In some embodiments, the device further comprises a first bearing 16 and a second bearing 17, the first bearing 16 is sleeved on the long shaft 14 and connected with the first cylinder 2, and the first eccentric part 12 is positioned between the first bearing 16 and the diaphragm assembly 4; the rotor balance weight 8 is arranged on one side of the motor rotor 10 close to the first bearing 16, or the rotor balance weight 8 is arranged on one side of the motor rotor 10 far away from the first bearing.

In some embodiments, the rotor weight 8 includes a first rotor weight 81 and a second rotor weight 82, the first rotor weight 81 is disposed on a side of the electric machine rotor 10 close to the first bearing 16, and the second rotor weight 82 is disposed on a side of the electric machine rotor 10 away from the first bearing 16.

In some embodiments, in a projection plane perpendicular to the axis of the crankshaft 1, the center of mass of the first rotor balancer 81 and the center of mass of the second rotor balancer 82 are centered at a central angle < 180 ° with respect to the rotation center of the crankshaft 1. That is, the center of mass of the first rotor counterbalance 81 and the center of mass of the second rotor counterbalance 82 are located on the same side as the crankshaft rotational center line.

A center of mass of the rotor counterbalance is disposed opposite the first eccentric portion about a center line of rotation of the crankshaft; the center of mass of the crankshaft counterbalance mass is disposed opposite the second eccentric portion about the centerline of rotation of the crankshaft. The rotor balancing mass may be disposed on a side of the rotor adjacent to the first bearing (see fig. 3), or may be disposed on a side of the rotor away from the first bearing. The number of the rotor balance weights can be 2, the rotor balance weights are respectively arranged on the upper end surface and the lower end surface of the rotor, and the mass center is arranged on the same side relative to the center of the crankshaft (see figure 4). The rotor balance blocks are arranged at different positions and in different quantities, and the corresponding weight adjustment can meet certain balance coefficient. The rotor counterbalance embodied in fig. 2 and 3 is disposed on a side of the rotor proximate the first bearing.

In some embodiments, the second bearing 17 is sleeved on the stub shaft 15 to support the stub shaft 15, a cover plate 18 is further disposed on the stub shaft 15, a main exhaust cavity 100 is formed between the cover plate 18 and the second bearing 17, and the crankshaft balance weight 9 is connected to the stub shaft 15 and is located in the main exhaust cavity 100. The crankshaft balance block is arranged in the exhaust cavity of the second bearing, and can be effectively isolated from the oil pool, so that the crankshaft balance block is prevented from stirring the oil pool in the rotation process. Meanwhile, a fan-shaped structure is adopted, so that turbulent flow (airflow disturbance) can be reduced to the maximum extent, and loss is reduced.

According to the utility model, the exhaust cavity is arranged between the sealing structure and the lower flange, the crankshaft balance block is arranged in the exhaust cavity and is connected with the short shaft of the crankshaft, so that the crankshaft balance block can play a role of balancing the eccentric part of the crankshaft, and a cavity is not required to be independently added for placing the crankshaft balance block, thereby avoiding the series of problems of lower cavity lengthening caused by independently adding a balance cavity, preventing the center of gravity of the lengthened pump body from moving upwards, solving the problem of the center of gravity of the pump body from moving upwards, fully utilizing the space, greatly reducing the size of the pump body in the axial direction, being beneficial to the running stability of the compressor, and further improving the vibration and reliability of the compressor; the crankshaft balance block is arranged in the lower flange exhaust cavity and is matched with the crankshaft short shaft, and a sealing structure is arranged between the crankshaft and the cover plate and is completely isolated from the oil pool, so that the problems of power consumption increase, shaft system instability, poor reliability and the like caused by oil stirring of the crankshaft balance block in operation are solved, and the problem of oil stirring of the balance block is effectively solved; the shape design of the crankshaft balance block is not limited, and the crankshaft balance block is easy to machine and assemble. The utility model provides a crankshaft balance block pump body structure, simple structure is rationally distributed, can not cause the compressor consumption to increase, and the shafting is stable, the reliability is high, the vibration is little.

The compressor provided by the application has the advantages of compact structure, simple structure, stable and reliable operation, and especially meets the requirements of large-displacement and high-rotating-speed compressors.

In some embodiments, the center of mass of the crankshaft balance mass 9 and the center of mass of the rotor balance mass 8 are in a relative distribution with a phase difference of 180 ° in a projection plane perpendicular to the axis of the crankshaft 1; and/or, in a projection plane perpendicular to the axis of the crankshaft 1, the crankshaft balance weight is in a fan-shaped structure; and/or the crankshaft balance weight 9 is assembled with the short shaft 15 in an interference fit mode.

The utility model also provides an air conditioner, which comprises the compressor. The compressor also comprises a motor stator 19 and an upper cover 21. The pump body assembly 20 is composed of a first cylinder, a second cylinder, a first roller, a second roller, a crankshaft and a partition plate assembly.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims

1. A compressor, characterized by: the method comprises the following steps:

the air cylinder comprises a crankshaft (1), a first air cylinder (2), a second air cylinder (3) and a partition plate assembly (4), wherein the partition plate assembly (4) is arranged between the first air cylinder (2) and the second air cylinder (3), the crankshaft (1) comprises a middle shaft section (11) positioned between the first air cylinder (2) and the second air cylinder (3), and the partition plate assembly (4) is arranged on the middle shaft section (11) in a penetrating mode; the diaphragm assembly (4) comprises a first diaphragm (41), the first diaphragm (41) being joined to the midshaft section (11) to form a diaphragm bearing for supporting the midshaft section (11).

2. The compressor of claim 1, wherein:

the diaphragm assembly (4) further comprises a second diaphragm (42): one axial end of the first partition plate (41) is connected with the first cylinder (2), one axial end of the second partition plate (42) is connected with the first partition plate (41), and the other axial end of the second partition plate (42) is connected with the second cylinder (3);

the middle shaft section (11) comprises a first middle section (11a) and a second middle section (11b) which are connected in the axial direction, the first partition plate (41) is sleeved on the periphery of the first middle section (11a) and is in contact fit with the first middle section (11a), and the first middle section (11a) can rotate relative to the first partition plate (41); the second partition plate (42) is located on the outer periphery of the second intermediate section (11b) and is not in contact with the second intermediate section (11b) and has a gap.

3. The compressor of claim 2, wherein:

the first middle section (11a) is a concentric circle section, and the central axis of the concentric circle section coincides with the rotation central line of the crankshaft (1).

4. The compressor of claim 2, wherein:

the first partition plate (41) is fixedly connected with the first cylinder (2), and the second partition plate (42) is fixedly connected with the second cylinder (3); and/or the presence of a gas in the gas,

the axial height of the first partition (41) is greater than the axial height of the second partition (42).

5. The compressor of claim 2, wherein:

a first cavity (71) is formed in one side, opposite to the second partition plate (42), of the first partition plate (41), a second cavity (72) is formed in one side, opposite to the first partition plate (41), of the second partition plate (42), the first cavity (71) and the second cavity (72) are connected in a butt joint mode to form a partition plate exhaust cavity (7), a first exhaust hole is formed in the first partition plate (41), one end of the first exhaust hole can be communicated with the inside of the first air cylinder (2), the other end of the first exhaust hole can be communicated with the first cavity (71), exhaust gas in the first air cylinder (2) is led into the first cavity (71), a second exhaust hole is formed in the second partition plate (42), one end of the second exhaust hole can be communicated with the inside of the second air cylinder (3), and the other end of the second exhaust hole can be communicated with the second cavity (72), to introduce the exhaust gases in the second cylinder (3) into the second cavity (72).

6. The compressor of claim 5, wherein:

and a first exhaust valve is arranged at the first exhaust hole, and a second exhaust valve is arranged at the second exhaust hole.

7. The compressor of claim 1, wherein:

the crankshaft (1), the first cylinder (2), the second cylinder (3) and the partition plate assembly (4) are all located inside the shell (5); the height H of at least one of the first cylinder (2) and the second cylinder (3), the cylinder inner diameter D and the inner diameter F of the shell (5) meet the following requirements: H/D is not less than 0.45 and H/F is not less than 0.21.

8. The compressor of claim 7, wherein:

the maximum rotating speed of the compressor is more than or equal to 120 rps; and/or the outer diameter of the shell (5) is more than or equal to 160 mm.

9. The compressor of claim 1, wherein:

the crankshaft (1) further comprises a first eccentric part (12) and a second eccentric part (13), the compressor further comprises a first roller (61) and a second roller (62), the first roller (61) is sleeved on the periphery of the first eccentric part (12), the first roller (61) is located in the first cylinder (2) and driven by the first eccentric part (12) to move in the first cylinder (2); the second roller (62) is sleeved on the periphery of the second eccentric part (13), and the second roller (62) is positioned in the second cylinder (3) and driven by the second eccentric part (13) to move in the second cylinder (3); the intermediate shaft section (11) is located between the first eccentric section (12) and the second eccentric section (13).

10. The compressor of claim 9, wherein:

the crankshaft (1) further comprises a long shaft (14) and a short shaft (15), the crankshaft balance block (9) is arranged on the short shaft (15), the motor rotor (10) is arranged on the long shaft (14), the rotor balance block (8) is connected and arranged on the motor rotor (10), the first eccentric part (12) is close to the long shaft (14) relative to the second eccentric part (13), the second eccentric part (13) is close to the short shaft (15) relative to the first eccentric part (12), and the mass center of the rotor balance block (8) and the first eccentric part (12) are arranged opposite to each other around the rotation center line of the crankshaft (1); the center of mass of the crankshaft balance mass (9) is arranged opposite to the second eccentric portion (13) about the rotational center line of the crankshaft (1).

11. The compressor of claim 10, wherein:

the baffle plate assembly further comprises a first bearing (16) and a second bearing (17), the first bearing (16) is sleeved on the long shaft (14) and connected with the first cylinder (2), and the first eccentric part (12) is located between the first bearing (16) and the baffle plate assembly (4); the rotor balance weight (8) is arranged on one side, close to the first bearing (16), of the motor rotor (10), or the rotor balance weight (8) is arranged on one side, far away from the first bearing, of the motor rotor (10).

12. The compressor of claim 11, wherein:

the rotor balancing block (8) comprises a first rotor balancing block (81) and a second rotor balancing block (82), the first rotor balancing block (81) is arranged on one side, close to the first bearing (16), of the motor rotor (10), and the second rotor balancing block (82) is arranged on one side, far away from the first bearing (16), of the motor rotor (10).

13. The compressor of claim 12, wherein:

in a projection plane perpendicular to the axis of the crankshaft (1), the center of mass of the first rotor balance weight (81) and the center of mass of the second rotor balance weight (82) are centered around the rotation center of the crankshaft (1) and form a central angle of less than 180 degrees.

14. The compressor of claim 11, wherein:

the second bearing (17) is sleeved on the short shaft (15) to support the short shaft (15), a cover plate (18) is further arranged on the short shaft (15), a main exhaust cavity (100) is formed between the cover plate (18) and the second bearing (17), and the crankshaft balance block (9) is connected with the short shaft (15) and is located in the main exhaust cavity (100).

15. The compressor of claim 10, wherein:

in a projection plane perpendicular to the axis of the crankshaft (1), the mass center of the crankshaft balance weight (9) and the mass center of the rotor balance weight (8) are distributed in a relative mode with a phase difference of 180 degrees; and/or, in a projection plane perpendicular to the axis of the crankshaft (1), the crankshaft balance weight is of a fan-shaped structure; and/or the crankshaft balance weight (9) is in interference fit with the short shaft (15).

16. An air conditioner, characterized in that: comprising a compressor according to any one of claims 1 to 15.