CN115126697B

CN115126697B - Compressor pump body, compressor and temperature regulating system

Info

Publication number: CN115126697B
Application number: CN202210622014.1A
Authority: CN
Inventors: 雒应学
Original assignee: Guangzhou Deshan Cnc Technology Co ltd
Current assignee: Guangzhou Deshan Cnc Technology Co ltd
Priority date: 2022-06-02
Filing date: 2022-06-02
Publication date: 2023-04-25
Anticipated expiration: 2042-06-02
Also published as: CN115126697A

Abstract

The invention relates to a compressor pump body, a compressor and a temperature regulating system. The eccentric rotor of the compressor pump body is provided with an air guide channel, the air guide channel is communicated with the inner cavity of the cylinder, the eccentric rotor is provided with a second cavity, the main bearing and/or the auxiliary bearing are/is provided with a transition channel, when the eccentric rotor rotates to a preset position between the exhaust end position and the zero position line, the transition channel is simultaneously communicated with the second cavity and the air guide channel, when the eccentric rotor rotates to a position between the zero position line and the air inlet end position, the transition channel is not simultaneously communicated with the second cavity and the air guide channel, and when the eccentric rotor rotates to a preset position between the air inlet end position and the exhaust start position, the transition channel is simultaneously communicated with the air guide channel and the second cavity. According to the compressor pump body, the compressor and the temperature regulating system, the cavity for temporarily storing the clearance gas is formed in the eccentric rotor, so that the clearance gas cannot influence air inlet of the compressor pump body, and the actual displacement volume of the compressor is effectively increased.

Description

Compressor pump body, compressor and temperature regulating system

Technical Field

The invention relates to the field of compressors, in particular to a compressor pump body, a compressor and a temperature regulating system.

Background

After the end of the exhaust, the rotor compressor still forms gaps, called clearances, between the eccentric rotor, the inner wall of the cylinder and the sliding sheets, and the pressure of the gas in the clearances is equivalent to the exhaust pressure of the compressor. When the highest point of the eccentric core rotor passes over the sliding vane and rotates by an angle beta, the clearance is in series air communication with the suction cavity behind the highest point, the high-pressure clearance air is expanded to suction pressure P0, and the sucked air is extruded out of the suction port of the cylinder, so that the actual displacement volume of the compressor is reduced.

Disclosure of Invention

Based on the defects of the prior art, the invention provides a compressor pump body capable of improving the actual displacement volume, a compressor and a temperature regulating system.

The embodiment of the invention provides a compressor pump body, which comprises a cylinder, a main bearing, an auxiliary bearing, a compressor rotor and a sliding vane, wherein a cylinder cavity and an air suction port communicated with the cylinder cavity are formed in the cylinder, the main bearing and the auxiliary bearing are respectively fixed at two sides of the cylinder to seal the cylinder cavity, the compressor rotor comprises a rotating shaft and a eccentric rotor connected with the rotating shaft, the eccentric rotor is accommodated in the cylinder cavity, the rotating shaft is respectively in rotary fit with the main bearing and the auxiliary bearing and is used for driving the eccentric rotor to rotate, the sliding vane is movably arranged in the cylinder and is in movable fit with the eccentric rotor and is used for separating the cylinder cavity, the eccentric rotor is driven by the rotating shaft to rotate relative to the cylinder, the main bearing and the auxiliary bearing, the eccentric rotor is provided with a side surface extending circumferentially around the rotating shaft and an end surface connecting the upper end and the lower end of the side surface, an air guide channel is arranged on the eccentric rotor and is communicated with the cylinder cavity, a second cavity is formed on the eccentric rotor, a transition channel is arranged between the eccentric rotor and a transition channel and the second cavity or the auxiliary rotor and the second cavity is in a transition channel is arranged at the end position of the transition channel and the transition channel is not in the transition position between the transition channel and the second cavity and the transition channel and the end position of the transition channel when the transition channel is in the transition position between the transition position and the second cavity and the transition position and the air guide channel and the end position and the transition channel and the position is at the end position and the transition position and the position, the transition channel is simultaneously communicated with the air guide channel and the second cavity.

As a further improvement of the embodiment, when the eccentric rotor rotates to a preset position between the air inlet end position and the air outlet start position, the transition channel is simultaneously communicated with the air guide channel and the second cavity, and when the eccentric rotor rotates to a preset position between the air inlet end position and the air outlet start position, the gas in the second cavity sequentially passes through the transition channel and the air guide channel and enters the inner cavity of the cylinder.

As a further improvement of the above embodiment, the air guide channel includes an air guide groove disposed on the end surface and an air guide port disposed on the side surface, the air guide port is communicated with the cylinder cavity and the air guide groove, and the position of the transition channel corresponds to the position of the air guide groove.

As a further improvement of the above embodiment, on the cross section of the eccentric rotor, a connection line from the center of the rotating shaft to the highest point of the eccentric portion of the eccentric rotor is used as a bus, two sides of the bus are respectively formed with second cavities, two adjacent second cavities are separated by a second reinforcing rib, and an auxiliary channel for communicating the two adjacent second cavities is arranged on the second reinforcing rib.

As a further improvement of the above embodiment, the second reinforcing ribs extend along the bus, and the air guide grooves are formed in the second reinforcing ribs;

the auxiliary channel is a conducting groove formed in the end face of the eccentric rotor, and is positioned on the same end face as the air guide groove or on the other end face opposite to the air guide groove; or alternatively

The auxiliary channel is a through hole penetrating through the second reinforcing rib.

As a further improvement of the above embodiment, the eccentric rotor has a eccentric portion far away from the rotating shaft, the end faces include an upper end face and a lower end face, the rotating shaft protrudes relative to the upper end face and the lower end face, the protruding length of the rotating shaft relative to the upper end face is greater than the protruding length relative to the lower end face, the air guide groove is formed in the lower end face of the eccentric rotor and is open at the top, and the air guide opening is formed in the eccentric portion of the eccentric rotor.

As a further improvement of the above embodiment, on the cross section of the eccentric rotor, a line from the center of the rotating shaft to the highest point of the eccentric portion of the eccentric rotor is used as a bus, the air guide groove includes an air guide starting section and an air guide connecting section, the first end of the air guide starting section faces the rotating shaft, the second end of the air guide starting section is connected with the first end of the air guide connecting section, the second end of the air guide connecting section is communicated with the air guide opening, the air guide starting section extends along the bus, and the air guide connecting section is bent relative to the air guide starting section.

As a further improvement of the above embodiment, the cross section of the eccentric rotor is egg-shaped, and has an egg head end and an egg tail end, the egg tail end contacts with the cylinder, the radius of curvature of the egg tail end is smaller than that of the egg head end, the distance from the egg tail end to the center of the rotating shaft is greater than that from the egg head end to the center of the rotating shaft, the air guide groove extends from the periphery of the rotating shaft to the egg tail end, and the air guide opening is formed in the egg tail end.

As a further improvement of the embodiment, the egg head end and the egg tail end are arc-shaped, the egg head end and the egg tail end are connected through a tangent line or an arc line, the ratio of the curvature radius of the egg head end to the curvature radius of the egg tail end is 1.3-2.5, and the ratio of the center distance of the egg head end to the center distance of the egg tail end to the curvature radius of the egg tail end is 1.5-3.

As a further improvement of the above embodiment, the transition channel includes a first transition channel and a second transition channel that are disposed at intervals, in a rotation direction of the eccentric rotor, the first transition channel is located between the exhaust slot and the second transition channel, when the eccentric rotor rotates to a preset position between the exhaust end position and the zero line, the first transition channel is simultaneously communicated with the second cavity and the air guide channel, when the eccentric rotor rotates to a position between the zero line and the intake end position, the first transition channel and the second transition channel are not simultaneously communicated with the second cavity and the air guide channel, and when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position, the second transition channel is simultaneously communicated with the air guide channel and the second cavity.

As a further improvement of the embodiment, the main bearing or the auxiliary bearing is provided with an exhaust channel, when the compressor pump body is in a compressed state, the exhaust channel is communicated with the air guide channel, compressed gas in the inner cavity of the cylinder is discharged out of the compressor pump body through the air guide channel and the exhaust channel, and when the compressor pump body is in an air suction state, the exhaust channel is not communicated with the air guide channel.

As a further improvement of the above embodiment, the rotation angle corresponding to the initial conduction position of the air guide channel and the exhaust channel is between 220 degrees and 250 degrees or between 260 degrees and 310 degrees.

As a further improvement of the embodiment, the cylinder comprises a cylinder outer wall and a cylinder inner wall, wherein the cylinder inner wall is internally provided with the cylinder inner cavity, a gas-liquid separation cavity is formed between the cylinder outer wall and the cylinder inner wall, the exhaust channel is communicated with the gas-liquid separation cavity, the cylinder is also provided with a total exhaust port, and when the compressor pump body is in a compressed state, compressed gas in the cylinder inner cavity is exhausted out of the cylinder through the gas guide channel, the exhaust channel, the gas-liquid separation cavity and the total exhaust port.

As a further improvement of the above embodiment, the gas-liquid separation cavity includes one or more sub-separation cavities, adjacent sub-separation cavities are separated by a separation reinforcing rib disposed between the cylinder outer wall and the cylinder inner wall, the separation reinforcing rib encloses the sub-separation cavities with the inner side of the cylinder outer wall and the outer side of the cylinder inner wall, a separation channel for communicating the adjacent sub-separation cavities is disposed on the separation reinforcing rib, and a flow passage sectional area of the separation channel is smaller than that of the sub-separation cavities.

As a further improvement of the above embodiment, the separation channel includes an upper channel and a lower channel, the upper channel is disposed relatively close to or at the top end of the separation reinforcing rib, the lower channel is disposed at the bottom end of the separation reinforcing rib, and a space exists between the upper channel and the lower channel.

As a further improvement of the embodiment, a plurality of buffer cavities are further formed between the outer wall of the cylinder body and the inner wall of the cylinder body, adjacent buffer cavities are separated by buffer reinforcing ribs arranged between the outer wall of the cylinder body and the inner wall of the cylinder body, buffer channels which enable the adjacent buffer cavities to be communicated are arranged on the buffer reinforcing ribs, the flow passage sectional area of each buffer channel is smaller than that of each buffer cavity, a total air inlet is arranged on the cylinder, the air suction inlet is arranged on the inner wall of the cylinder body, and air sequentially enters the inner cavity of the cylinder through the total air inlet, the buffer cavities and the air suction inlet.

The embodiment of the invention also provides a compressor, which comprises a compressor shell, a driving assembly and the compressor pump body of any embodiment, wherein the driving assembly and the compressor pump body are both arranged in the compressor shell, and the driving assembly is positioned at one side of the main bearing, which is away from the air cylinder, and is connected with the rotating shaft and used for driving the rotating shaft to rotate.

The embodiment of the invention also provides a compressor, which comprises a compressor shell, a driving assembly and the compressor pump body, wherein the driving assembly and the compressor pump body are arranged in the compressor shell, and the driving assembly is positioned at one side of the main bearing, which is away from the cylinder, and is connected with the rotating shaft and used for driving the rotating shaft to rotate; the compressor also comprises an oil discharging assembly, wherein the oil discharging assembly is connected with the gas-liquid separation cavity and is used for discharging liquid in the gas-liquid separation cavity out of the compressor pump body.

As a further improvement of the above embodiment, an oil sump is further disposed in the compressor housing, the oil sump is located below the auxiliary bearing, the oil drain assembly includes a gap oil drain structure, the gap oil drain structure includes a mandrel and a mandrel mounting seat matched with the mandrel, a gap channel is formed between the mandrel and the mandrel mounting seat, and liquid in the gas-liquid separation cavity passes through the gap channel and is discharged into the oil sump.

The embodiment of the invention also provides a temperature regulating system, which comprises the compressor according to any one of the embodiments, an evaporator and a condenser, wherein refrigerant circularly flows among the compressor, the evaporator and the condenser.

According to the compressor pump body, the compressor and the temperature regulating system provided by the embodiment of the invention, the cavity for temporarily storing the clearance gas is arranged on the eccentric rotor, so that the clearance gas can not influence the air inlet of the compressor pump body, and the actual displacement volume of the compressor is effectively improved.

Drawings

The foregoing and other objects, features and advantages of the invention will be apparent from the following more particular description of preferred embodiments of the invention, as illustrated in the accompanying drawings. Like reference numerals refer to like parts throughout the drawings, and the drawings are not intentionally drawn to scale on actual size or the like, with emphasis on illustrating the principles of the invention.

Fig. 1 is a schematic view of a compressor according to an embodiment of the present invention.

Fig. 2 and 3 are partial exploded and assembled views of a compressor pump body according to an embodiment of the present invention.

Fig. 4 to 9 are schematic structural views of the compressor rotor of fig. 2.

Fig. 10 is a schematic view of the structure of the sub-bearing in fig. 2.

Fig. 11 is a schematic structural view of a compressor rotor according to another embodiment.

Fig. 12 is a partial enlarged view of fig. 11.

Fig. 13 is a partial schematic view of a compressor pump body having the compressor rotor of fig. 11.

Fig. 14 is a schematic view of a structure of a sub-bearing correspondingly engaged with the compressor rotor of fig. 11.

Fig. 15 is a schematic diagram of a comparison of the compressor pump body of fig. 13 with the compressor pump body of fig. 3.

Fig. 16 to 18 are schematic structural views of the cylinder in fig. 3.

Fig. 19 is a schematic view showing a structure of a compressor according to another embodiment of the present invention.

Fig. 20 is a partial enlarged view of fig. 19.

Fig. 21 to 25 are schematic views showing respective states of the compressor pump body of fig. 13.

FIG. 26 is a dimensional schematic of a compressor rotor according to an embodiment.

Fig. 27 is a schematic view of the compression ratio versus busbar angle relationship of the compressor pump body of fig. 13.

Detailed Description

In order that the invention may be understood more fully, the invention will be described with reference to the accompanying drawings.

It will be understood that when an element is referred to as being "connected" to another element, it can be directly connected to and integrated with the other element or intervening elements may also be present. The terms "mounted," "one end," "the other end," and the like are used herein for illustrative purposes only.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used in the description herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and/or" as used herein includes any and all combinations of one or more of the associated listed items.

Referring to fig. 1 to 27, an embodiment of the present invention provides a compressor, which may be a rotor compressor, also called a rotary compressor. The compressor comprises a compressor shell 1, a driving assembly 2 and a compressor pump body, wherein the driving assembly 2 and the compressor pump body are arranged in the compressor shell 1. The compressor pump body comprises a cylinder 4, a main bearing 5, a secondary bearing 6, a compressor rotor 3 and a sliding vane 7. The cylinder 4 has a cylinder chamber 41 formed therein and an intake port 48 communicating with the cylinder chamber 41. The main bearing 5 and the auxiliary bearing 6 are respectively fixed on the upper side and the lower side of the cylinder 4 to seal the cylinder cavity 41. In the present embodiment, the main bearing 5 is integrally formed with a part of the compressor housing 1. The compressor rotor 3 includes a rotating shaft 31 and a eccentric rotor 32 connected to the rotating shaft 31, and the rotating shaft 31 is used for driving the eccentric rotor 32 to rotate. The eccentric rotor 32 is accommodated in the cylinder chamber 41, and both ends of the rotating shaft 31 protrude with respect to the end faces of the eccentric rotor 32, respectively, and are in running fit with the main bearing 5 and the sub bearing 6, respectively. The eccentric rotor 32 rotates relative to the cylinder 4, the main bearing 5 and the auxiliary bearing 6 under the drive of the rotating shaft 31. The slide 7 is movably mounted in the cylinder 4 and is in movable engagement with the eccentric rotor 32 for separating the cylinder chamber 41. The drive assembly 2 is located on the side of the main bearing 5 facing away from the cylinder 4 (i.e. the upper side in fig. 2) and is connected to the rotation shaft 31 for driving the rotation shaft 31 in rotation. The driving assembly 2 may be a motor, which includes a stator, a rotor, etc., and is not described herein because the motor structure is a well-known structure.

Referring to fig. 4 to 6, the eccentric rotor 32 has a cylindrical shape, which may be a cylindrical shape, an elliptic cylindrical shape, or the like. The eccentric rotor 32 has a side surface 3202 extending circumferentially around the rotation shaft 31 and end surfaces connecting upper and lower ends of the side surface 3202, specifically, the end surfaces include an upper end surface 3204 (i.e., thrust surface) and a lower end surface 3203 (i.e., thrust surface), and the upper end surface 3204 and the lower end surface 3203 are disposed in parallel. The eccentric rotor 32 is provided with an air guide channel, and the air guide channel comprises an air guide groove 321 arranged on the end surface and an air guide opening 322 arranged on the side surface 3202, and the air guide opening 322 is communicated with the air guide groove 321. The air guide groove 321 may be provided on the upper end surface 3204 or may be provided on the lower end surface 3203. The air guide opening 322 communicates with the cylinder chamber 41 so that the cylinder chamber 41 can communicate with the outside through an air guide passage.

In a preferred embodiment, the eccentric rotor 32 has an eccentric portion remote from the rotational axis 31. Since the rotating shaft 31 is eccentrically disposed on the eccentric rotor 32, a portion of the side surface 3202 of the eccentric rotor 32 is farther from the center of the rotating shaft 31 than the other portion of the side surface 3202, which is the eccentric portion, is. In the present invention, a line from the center of the rotating shaft 31 to the highest point of the eccentric portion of the eccentric rotor 32 (i.e., the point farthest from the center of the rotating shaft 31 in the cross section of the eccentric rotor 32) is defined as a bus bar 3201 in the cross section of the eccentric rotor 32, and a region in which an included angle formed between the line of the corresponding point on the side surface 3202 and the center of the rotating shaft 31 and the bus bar 3201 is within 20 degrees is defined as the eccentric portion. The rotary shaft 31 protrudes with respect to the upper end surface 3204 and the lower end surface 3203, forming the main shaft 311 and the sub shaft 312, respectively. The main shaft 311 passes through the main bearing 5 and is connected with the driving assembly 2, and the main shaft 311 is in running fit with the main bearing. The auxiliary shaft 312 is in rotational engagement with the auxiliary bearing 6. The length of the projection of the rotating shaft 31 relative to the upper end surface 3204 (i.e., the length of the primary shaft 311) is greater than the length of the projection relative to the lower end surface 3203 (i.e., the length of the secondary shaft 312). The air guide groove 321 is formed on the lower end surface 3203 of the eccentric rotor 32, the top of the air guide groove is open, and the air guide opening 322 is formed on the eccentric portion of the eccentric rotor 32.

Referring to fig. 7 to 9, in a further preferred embodiment, an oil guiding channel 313 is formed in the rotating shaft 31, and an oil outlet 3111 communicating with the oil guiding channel 313 is formed on a side surface of the rotating shaft 31. Specifically, the oil guide channel 313 may be opened from the bottom of the auxiliary shaft 312 to the top of the main shaft 311, and the main shaft 311 and the auxiliary shaft 312 may be provided with oil outlet 3111 for guiding the lubricating oil into the compressor pump body through the bottom of the auxiliary shaft 312, the oil guide channel 313 and the oil outlet 3111, so as to lubricate the rotating shaft 31, the main bearing 5, the auxiliary bearing 6 and the eccentric rotor 32 and the cylinder 4. An oil guide groove 325 with an open top is formed in the upper end surface 3204 of the eccentric rotor 32, and is used for conveying the lubricating oil flowing out from the oil outlet 3111 between the upper end surface 3204 of the eccentric rotor and the inner surface of the main bearing 5. The oil guide groove 325 includes an oil guide start section 3251 and an oil guide diffusion section 3252, and a first end of the oil guide start section 3251 faces the rotation shaft 31 (i.e., faces the main shaft 311) and communicates with the oil outlet 3111. Specifically, the upper end surface 3204 of the eccentric rotor 32 is provided with an annular oil sump 328 surrounding the main shaft 311, the lubricating oil flowing out of the oil outlet 3111 falls into the oil sump 328, and the first end of the oil guiding start section 3251 communicates with the oil sump 328, so that the lubricating oil flowing out of the oil outlet 3111 flows into the oil guiding groove 325 through the oil sump 328. The second end of the oil guiding start section 3251 is connected to the first end of the oil guiding diffusion section 3252, and the oil guiding diffusion section 3252 is bent with respect to the oil guiding start section 3251 and extends in the circumferential direction of the eccentric rotor 32. When the highest point of the eccentric portion of the eccentric rotor 32 is in contact with the slide 7, the oil guiding diffusion section 3252 is bent in a direction facing away from the air inlet 48. By arranging the oil guiding diffusion section 3252, a larger lubricating oil scattering surface is formed on the eccentric rotor 32, and the lubricating effect is better.

Referring to fig. 8, in a further preferred embodiment, on the cross section of the eccentric rotor 32, a line from the center of the rotating shaft 31 to the highest point of the eccentric portion of the eccentric rotor 32 is taken as a bus bar 3201, two sides of the bus bar 3201 are respectively formed with one or more first cavities 326, a first reinforcing rib 327 extending along the bus bar 3201 is formed between two first cavities 326 nearest to the bus bar 3201, and the oil guiding groove 325 is formed on the first reinforcing rib 327. By providing the first cavity 326, the weight of the eccentric rotor 32 can be reduced and the energy efficiency of the compressor can be improved. In addition, the first cavity 326 can slightly deform the side surface 3202 of the eccentric rotor 32 when the force is applied to the side surface 3202, so as to avoid the eccentric rotor 32 from being blocked in the cylinder 4.

Referring to fig. 5 and 6, in the preferred embodiment, in the cross section of the eccentric rotor 32, a line from the center of the rotating shaft 31 to the highest point of the eccentric portion of the eccentric rotor 32 is taken as a bus bar 3201, and an included angle of 1-20 degrees, preferably 1-5 degrees, is formed between the line from the center of the rotating shaft 31 to the center of the air guide port 322 and the bus bar 3201. When the eccentric rotor 32 rotates in the cylinder 4, the cylinder 4 applies a force towards the center of the rotating shaft 31 to the eccentric portion, wherein the force applied to the highest point of the eccentric portion is the largest, and the air guide opening 322 is deviated from the highest point of the eccentric portion, so that the strength of the eccentric rotor 32 is not greatly affected, and the service life of the eccentric rotor 32 is ensured.

Referring to fig. 5 and 6, in the preferred embodiment, a line from the center of the rotation shaft 31 to the highest point of the eccentric portion of the eccentric rotor 32 is taken as a bus bar 3201 in the cross section of the eccentric rotor 32. The air guide groove 321 comprises an air guide initial section 3211 and an air guide connecting section 3212, a first end of the air guide initial section 3211 faces the rotating shaft 31, a second end of the air guide initial section 3211 is connected with a first end of the air guide connecting section 3212, and a second end of the air guide connecting section 3212 is communicated with the air guide opening 322. Specifically, a connection hole 3213 is formed at the bottom of the second end of the air guide connection section 3212, and the connection hole 3213 communicates the air guide connection section 3212 with the air guide opening 322. The air guide initial section 3211 extends along a bus, and the air guide connecting section 3212 is bent relative to the air guide initial section 3211. When the highest point of the eccentric portion of the eccentric rotor 32 is abutted against the slide 7, the bending direction of the air guide connection section 3212 is directed away from the air inlet 48. By the air guide connection segment 3212, the air guide opening 322 deviates from the highest point of the eccentric part, so that the strength of the eccentric rotor 32 is not greatly affected, and the service life of the eccentric rotor 32 is ensured. In another embodiment, the air guide grooves 321 may extend directly onto the side 3202 of the eccentric rotor 32, forming the air guide openings 322 on the side 3202 of the eccentric rotor 32.

Referring to fig. 10, in the preferred embodiment, the auxiliary bearing 6 is provided with an exhaust passage 62, when the compressor pump body is in a compressed state, the exhaust passage 62 is communicated with the air guide passage on the eccentric rotor 32, the compressed air in the cylinder cavity 41 is discharged out of the compressor pump body through the air guide passage and the exhaust passage 62, and when the compressor pump body is in an air suction state, the exhaust passage 62 is not communicated with the air guide passage. Specifically, the exhaust passage 62 is opened on the inner surface of the sub-bearing 6 opposite to the lower end surface 3203 of the eccentric rotor 32, the air guide groove 321 is opened on the lower end surface 3203 of the eccentric rotor 32, when the eccentric rotor 32 rotates to the compression position, the compressor pump body is in a compressed state, the air guide groove 321 rotates to a position communicating with the exhaust passage 62, and at this time, the compressed air in the cylinder chamber 41 is discharged out of the cylinder chamber 41 through the air guide opening 322, the air guide groove 321, and the exhaust passage 62. When the eccentric rotor 32 continues to rotate to the suction position, the air guide groove 321 is not communicated with the air discharge channel 62, and the compressor pump body is in a suction state. In another embodiment, the exhaust passage may be formed on the inner surface of the main bearing 5 opposite to the eccentric rotor 32, and correspondingly, the air guide passage is formed on the upper end surface 3202 of the eccentric rotor 32, and the working principle is similar to that of the above embodiment. By discharging the compressed gas in the cylinder chamber 41 in such a way that the gas guide channel communicates with the gas discharge channel 62, it is not necessary to provide a gas discharge valve on the auxiliary bearing 6, on the one hand, it is possible to avoid failure of the compressor due to damage of the gas discharge valve, and on the other hand, the production of the compressor is not limited by the supply of the gas discharge valve material.

In a further preferred embodiment, the main bearing 5 or the auxiliary bearing 6 is further provided with an air supplementing channel 63, and when the compressor pump body is in an air suction state, the air supplementing channel 63 is communicated with the air guiding channel, and the compressor pump body supplements air into the inner cavity 41 of the cylinder through the air supplementing channel 63 and the air guiding channel. Specifically, the air compensating channel 63 is communicated with a refrigerant pipeline outside the compressor, and is used for introducing medium-pressure gaseous refrigerant compressed by the compressor and passing through a condenser or a flash evaporator into the cylinder cavity 41 of the compressor through the air compensating channel 63, mixing the medium-pressure gaseous refrigerant with low-pressure gaseous refrigerant sucked through the air suction port 48, and then completing compression in the cylinder cavity 41 along with rotation of the eccentric rotor 32, so that enthalpy difference of the compressed refrigerant is increased, efficiency of the compressor is improved, and the compressor with the air compensating enthalpy increasing structure is more suitable for running in severe cold environment. When the air guide channel is opened at the lower end surface 3203 of the eccentric rotor 32, the air supplementing channel 63 is opened at the auxiliary bearing 6, and when the air guide channel is opened at the upper end surface 3202 of the eccentric rotor 32, the air supplementing channel 63 is opened at the main bearing 5.

In a further preferred embodiment, the auxiliary bearing 6 is provided with a first shaft hole 61, the first shaft hole 61 is a through hole, and the auxiliary shaft 312 of the rotating shaft 31 is inserted into the first shaft hole 61 and is in a rotating fit with the auxiliary bearing 6. The exhaust passage 62 and the air supply passage 63 are provided on the sub-bearing 6. The exhaust passage 62 includes an exhaust groove 621 and an exhaust pipe 624 communicating with the exhaust groove 621. The air supply passage 63 includes an air supply groove 631 and an air supply line 632 communicating with the air supply groove 631. The exhaust groove 621 and the air supplementing groove 631 are arc-shaped extending along the circumferential direction of the first shaft hole 61, the exhaust groove 621 and the air supplementing groove 631 surround the first shaft hole 61 and are arranged in opposite directions at intervals, namely, the intrados of the exhaust groove 621 and the air supplementing groove 631 are opposite to each other, and the exhaust groove 621 and the air supplementing groove 631 are spaced at intervals. By controlling the arc length and angle of the discharge groove 621 and the air supply groove 631, the pressure and compression ratio of the compressed air discharged from the cylinder 4 can be controlled, and the amount and time of air supply can also be controlled. When the eccentric rotor 32 rotates to the compression position, the air guide channel is communicated with the air discharge groove 621, is not communicated with the air supplementing groove 631, and compressed air in the cylinder inner cavity 41 is discharged outwards through the air guide opening 322, the air guide groove 321, the air discharge groove 621 and the air discharge pipeline 624 in sequence. Specifically, the first exhaust hole 622 is formed in the inner surface of the sub-bearing 6, and the exhaust hole 622 communicates with an exhaust path in the cylinder 4, which is isolated from the cylinder chamber 41, and the compressed gas flows from the exhaust pipe 624 and the first exhaust hole 622 into the exhaust path in the cylinder 4, and finally is discharged from the total exhaust port 45 of the cylinder 4 to the outside of the compressor pump. In another embodiment, a second exhaust hole 623 is provided on the side surface of the sub-bearing 6, and compressed gas is directly exhausted from the exhaust pipe 624, the second exhaust hole 623, and is connected to the main exhaust pipe 92 of the compressor, for example, through a pipe. The first and second exhaust holes 622 and 623 may not be simultaneously opened. When the eccentric rotor 32 rotates to the air suction position, the air guide channel is communicated with the air supplementing groove 631, is not communicated with the air exhausting groove 621, and the compressor pump body sequentially passes through the air supplementing pipeline 63, the air supplementing groove 631, the air guide groove 321 and the air guide port 322 to supplement air to the inner cavity 41 of the cylinder. The air supply line 63 may communicate with the outside through a line outside the compressor pump body.

Referring to fig. 4 to 14, in the preferred embodiment, the eccentric rotor 32 is provided with a second cavity 323, the auxiliary bearing 6 is provided with a transition channel 65 (fig. 14), and the transition channel 65 is located on the inner surface of the auxiliary bearing 6 and corresponds to the air guide groove 321 of the air guide channel. The position of the transition channel 65 corresponds to the position of the air guide channel and the second cavity 323. When the eccentric rotor 32 rotates to a preset position between the exhaust end position and the zero line 3205, the transition channel 65 simultaneously communicates the second cavity 323 and the air guide channel, and at this time, the clearance air enters the second cavity 323 through the air guide channel and the transition channel 65. When the eccentric rotor 32 rotates to a position between the zero line 3205 and the air intake end position, the transition passage 65 does not simultaneously communicate the second cavity 323 with the air guide passage, and no air flows between the cylinder inner cavity 41 and the second cavity 323. When the eccentric rotor 32 rotates to a preset position between the air inlet end position and the air outlet start position, the transition channel 65 is simultaneously communicated with the air guide channel and the second cavity 323, and the air in the second cavity 323 enters the inner cavity 41 of the cylinder through the transition channel 65 and the air guide channel.

In a preferred embodiment, the transition channel 65 includes a first transition channel 651 and a second transition channel 652 that are spaced apart. In the rotational direction of the eccentric rotor 32, the first transition channel 651 is located between the exhaust slot 62 and the second transition channel 652. Referring to fig. 21, when the eccentric rotor 32 rotates to 200 degrees, the compressor pump body starts to exhaust through the air guide passage and the exhaust passage 62. Referring to fig. 22, when the eccentric rotor 32 rotates to 335 degrees, the air guide groove 321 and the air discharge groove 621 do not overlap (this position is referred to as an air discharge end position), and the air discharge ends. When the eccentric rotor 32 is rotated to a preset position between the exhaust end position and the zero line 3205 (rotation angle is 0 degrees) beyond the exhaust end position, a clearance is formed between the eccentric rotor 32, the cylinder inner wall 422 and the vane 7, and compressed gas remains in the clearance. At this time, a part of the first transition channel 651 overlaps with the position of the air guide groove 321, and the other part overlaps with the position of the second cavity 323, so that the second cavity 323 and the air guide groove 321 are simultaneously communicated, and the compressed air in the clearance sequentially passes through the air guide opening 322, the air guide groove 321 and the first transition channel 651, and enters the second cavity 323, which corresponds to air intake of the second cavity 323. At this time, the gas in the second cavity 423 is formed by mixing the clearance compressed gas with the gas in the original second cavity 423, and the gas pressure thereof is greater than the gas pressure in the original second cavity 423 and also greater than the intake gas pressure.

Referring to fig. 23, the eccentric rotor 32 continues to rotate between the exhaust end position and the zero line 3205, at this time, the first transition channel 651 is not in communication with the air guide groove 321, the first transition channel 651 is not in communication with the second cavity 323, the second transition channel 652 is not in communication with the air guide groove 321, the second cavity 323 is not in communication with the air guide groove 323, the second cavity 323 is neither air-in nor air-out, and no air is in communication with the cylinder cavity 41. When the eccentric rotor 32 continues to rotate and passes over the zero line 3205 and rotates between the air intake start position (i.e., the first side of the air intake 48) and the air intake end position (i.e., the trailing side of the air intake 48), the cylinder inner cavity 41 starts to intake air through the air intake 48, and the first transition channel 651 and the second transition channel 652 are respectively communicated with the two second cavities 323, but are not communicated with the air guide groove 321, and at the moment, the second cavities 323 are likewise neither air-intake nor air-exhaust.

Referring to fig. 24, when the eccentric rotor 32 continues to rotate to a preset position (e.g., a position with a rotation angle of 30 degrees) between the intake end position and the exhaust start position, the second transition channel 652 simultaneously connects the air guide groove 421 and the second cavity 423, and the air pressure in the second cavity 423 is greater than the intake air pressure, so that the air in the second cavity 423 sequentially passes through the second transition channel 652, the air guide groove 421 and the air guide port 422, and enters the cylinder inner cavity 41, that is, the second cavity 423 is exhausted. Referring to fig. 25, the eccentric rotor 32 continues to rotate (e.g., to a 52 degree position), at this time, the second transition channel 652 is not in communication with the air guide groove 421, and the second cavity 423 is no longer exhausted to the cylinder cavity 41, i.e., the exhaust process of the second cavity 423 is ended. The eccentric rotor 32 then continues to rotate, forming a cycle of air intake and exhaust from the second cavity 423. In this embodiment, the second cavity 423 functions as a transitional air chamber in addition to the aforementioned weight reduction and slight deformation of the eccentric rotor 32, so that the clearance gas does not affect the intake of the compressor, thereby improving the volumetric efficiency of the compressor.

In other embodiments, the transition passage may also be provided on the inner surface of the main bearing 5, and correspondingly, the air guide groove 321 is provided on the upper end surface 3204 of the eccentric rotor 32. Even the inner surfaces of main bearing 5 and auxiliary bearing 6 may be provided with transition passages, and upper end surface 3204 and lower end surface 3203 of eccentric rotor 32 may be provided with air guide grooves 321, respectively.

Referring to fig. 14 and 21 to 25, in the present embodiment, the air guiding groove 321 is arc-shaped and extends around the circumference of the auxiliary shaft 322, the air discharging groove 621 is arc-shaped and extends along the circumference of the first shaft hole 61, and the distance from the air guiding groove 321 to the center of the auxiliary shaft 322 is substantially equal to the distance from the air discharging groove 621 to the center of the first shaft hole 61. In a further preferred embodiment, the air guide groove 321 is further provided with an auxiliary air guide groove 3215 extending toward the eccentric portion along the second reinforcing rib 324, and both sides of the auxiliary air guide groove 3215 are not equidistant from the second cavities 323 at both sides of the second reinforcing rib 324. The auxiliary air guide groove 3215 is configured to communicate with the first transition passage 652 and the second transition passage 652, so that the first transition passage 652 and the second transition passage 652 communicate with the air guide groove 321. Because the two sides of the auxiliary air guide groove 3215 are not equidistant from the second cavities 323 on two sides of the second reinforcing rib 324, when the first transition channel 652 is located on one side of the auxiliary air guide groove 3215, the auxiliary air guide groove 3215 and the second cavities can be communicated, and when the first transition channel is located on the other side of the auxiliary air guide groove 3215, the auxiliary air guide groove 3215 and the second cavities cannot be communicated.

On the cross section of the compressor pump body, a connecting line from the center of the rotating shaft 3 to the center of the sliding vane 7 is taken as a zero line 3205, and an included angle between the bus 3201 and the zero line 3205 along the rotating direction of the eccentric rotor 32 is taken as the rotating angle of the eccentric rotor 32. Referring to fig. 21, when the eccentric rotor 32 rotates to 200 degrees (i.e. the included angle between the bus bar 3201 and the zero line 3205 is 200 degrees), the compressor pump body is in a compressed state, and the positions of the air guide groove 321 and the air discharge groove 621 start to overlap, which is herein denoted as the initial conducting position (i.e. the air discharge starting position) of the air guide channel and the air discharge channel, so that the air guide groove 321 and the air discharge groove 621 are conducted, at this time, the compressed air in the cylinder inner cavity 41 enters the air-liquid separation cavity 43 through the air guide opening 322, the air guide groove 321 and the air discharge channel 62. As the eccentric rotor 32 continues to rotate, the compressor pump body continues to exhaust. Referring to fig. 2, when the eccentric rotor 32 rotates to 335 degrees, the compressor pump body is still in a compressed state, and the air guide groove 321 and the air discharge groove 621 are not overlapped (i.e. the air discharge end position), i.e. the air guide groove 321 and the air discharge groove 621 are not conducted, and the air discharge is ended. For the compressor pump body of the embodiment of the invention, the magnitude of the rotation angle corresponding to the exhaust starting position is directly related to the compression ratio of the compressor. Fig. 27 shows a simulated curve of the busbar angle (i.e., rotation angle) versus compression ratio in one embodiment. For an air conditioning compressor, the compression ratio is generally around 3-4, so the rotation angle of the discharge start position is preferably between 220 degrees and 250 degrees. For the refrigerator compressor, the compression ratio thereof is generally about 5 to 10 depending on the refrigerant, and thus the rotation angle of the discharge start position is preferably between 260 degrees and 310 degrees. The discharge end position of the compressor is typically set between 330 and 340 degrees.

Referring to fig. 5 and 6, in the preferred embodiment, on the cross section of the eccentric rotor 32, a connection line from the center of the rotating shaft 31 to the highest point of the eccentric portion of the eccentric rotor 32 is used as a bus 3201, two sides of the bus 3201 are respectively formed with second cavities 323, two adjacent second cavities 323 are separated by a second reinforcing rib 324, and the air guide groove 321 is arranged on the second reinforcing rib 324. The second cavity 323 may be integral with the first cavity 326 (i.e., the same cavity) or may be separate from the first cavity 326, which may also reduce the weight of the eccentric rotor 32, and slightly deform the side 3202 of the eccentric rotor 32 when the force is applied to the side 3202 of the eccentric rotor 32, so as to avoid the eccentric rotor 32 from being locked in the cylinder 4. The second reinforcing ribs 324 can ensure that the eccentric rotor 32 has enough strength and the position of the air guide groove 321 can be reasonably set. It should be noted that, herein, the "the second cavities 323 are formed on both sides of the bus bar 3201" does not mean that each second cavity 323 is strictly located on one side of the bus bar 3201 and does not span the bus bar 3201, but means that both sides of the bus bar 3201 have the second cavities 323. Taking the embodiment shown in fig. 22 and 23 as an example, the cross-sectional areas of the second cavities 323 on both sides of the stiffener 324 are different, wherein a portion of the second cavity 323 with a larger cross-sectional area passes over the busbar 3201, i.e. the main body portion of the second cavity 323 is located on one side of the busbar 3201, and a small portion of the second cavity 323 and another second cavity 323 with a smaller cross-sectional area are located on the other side of the busbar 3201. The second cavity 323 on the bus bar 3201 side may be one or a plurality of second cavities.

Referring to fig. 11 and 12, in a further preferred embodiment, the second cavities 323 on both sides of the bus bar 3201 are conducted through the auxiliary channels 3241 formed on the second reinforcing ribs 324, so that the two second cavities 323 are jointly formed into a transitional air cavity. In this embodiment, the cross section of the eccentric rotor 32 is egg-shaped. The second reinforcing rib 324 may extend along the bus bar 3201, and the air guide groove 321 may be opened on the second reinforcing rib 324.

In a further preferred embodiment, the auxiliary channel 3241 may be a conducting groove opened on an end surface of the eccentric rotor 32, and the auxiliary channel 3241 is located on the same end surface as the air guide groove 321 or on the other end surface opposite to the air guide groove 321. Specifically, the auxiliary passage 3241 may be provided on the upper end surface 3204 of the core barrel 32 or on the lower end surface 3203. In the present embodiment, the auxiliary passage 3241 and the air guide groove 321 are both located on the lower end face 3203 of the core shift rotor 32. The auxiliary passage 3241 may also be a through hole penetrating the second reinforcing bead 324.

Referring to fig. 11 to 15, in another preferred embodiment, the cross section of the eccentric rotor 32 is egg-shaped, which has an egg-head end (i.e. the upper end in fig. 15) and an egg-tail end (i.e. the lower end in fig. 15), the radius of curvature of the egg-tail end is smaller than that of the egg-head end, the distance from the egg-tail end to the center of the rotating shaft 31 is greater than that from the egg-head end to the center of the rotating shaft 31, and the air guide groove 321 extends from the periphery of the rotating shaft 31 to the egg-tail end. Referring to fig. 15, the outline of the hatched area a is a side projection of the circular eccentric rotor 32, the inner outline of the hatched area a is a side projection of the egg-shaped eccentric rotor 32 of the present embodiment, and when the eccentric rotors 32 have the same maximum outer diameter, the cross-sectional area occupied by the egg-shaped eccentric rotor 32 (i.e. the occupied overall volume) is smaller than the cross-sectional area occupied by the circular eccentric rotor 32, so that the effective volume of the cylinder inner chamber 41 is larger.

Referring to fig. 26, in a further preferred embodiment, the head end and the tail end of the egg are rounded, and are connected by a tangent line or an arc. In some embodiments, both sides of the head end and the tail end of the egg may be connected with a tangent line, and the tangent line is tangent to the circular arcs of the head end and the tail end of the egg. In other embodiments, the two sides of the head end and the tail end are connected by an outer arc, and the radius of curvature of the two outer arcs is much larger than that of the head end and the tail end, for example, may be 5-10 times that of the head end. The ratio of the curvature radius of the head end to the curvature radius of the tail end of the egg is 1.3-2.5, and the ratio of the center distance of the head end to the tail end of the egg to the curvature radius of the tail end of the egg is 1.5-3. In the embodiment, the curvature radius of the head end of the egg is 14mm, the curvature radius of the tail end of the egg is 7.5mm, and the center distance between the head end of the egg and the tail end of the egg is 15.5mm.

Referring to fig. 16 to 18, in the preferred embodiment, the cylinder 4 includes a cylinder outer wall 421 and a cylinder inner wall 422, the cylinder inner wall 200 is disposed within the cylinder outer wall 100, a cylinder inner chamber 41 is formed in the cylinder inner wall 422, a gas-liquid separation chamber 43 is formed between the cylinder outer wall 421 and the cylinder inner wall 422, and the exhaust passage 62 communicates with the gas-liquid separation chamber 43. As in the above-described embodiment, the exhaust passage 62 may communicate with the gas-liquid separation chamber 43 through the first exhaust hole 622 opened at the inner surface of the sub-bearing 6. The cylinder 4 is also provided with a total exhaust port 45, and when the compressor pump body is in a compressed state, compressed gas in the cylinder inner cavity 41 is exhausted out of the cylinder through the gas guide channel, the exhaust channel 62, the gas-liquid separation cavity 43 and the total exhaust port 45. Due to the existence of the gas-liquid separation cavity 43, the cylinder inner wall 422 realizes fine stress following deformation under the acting force of the eccentric rotor 32, the tightness of the eccentric rotor 32 and the cylinder inner wall 422 is ensured, the leakage in the compression process is reduced, and the situation that the eccentric rotor 32 is blocked by the cylinder inner wall 422 can be reduced. Meanwhile, since the lubricant is contained in the cylinder chamber 41, the compressed gas discharged from the cylinder chamber 41 carries lubricant droplets, so that the compressed gas is guided into the gas-liquid separation chamber 43 to separate the gaseous refrigerant from the lubricant, thereby facilitating recovery of the lubricant and preventing the lubricant from entering the refrigeration line. In addition, the gas-liquid separation cavity 43 can also have the effects of silencing, turbulent flow and the like on the suction and exhaust actions of the compressor pump body, so that the noise generated when the compressor pump body operates is reduced.

In a further preferred embodiment, the gas-liquid separation chamber 43 includes a plurality of sub-separation chambers 431, with adjacent sub-separation chambers 431 separated by separation ribs 432 provided between the cylinder outer wall 421 and the cylinder inner wall 422. The separation rib 432 and the inner side of the cylinder outer wall 421 and the outer side of the cylinder inner wall 422 enclose a sub-separation chamber 431. The separation rib 432 is provided with a separation channel 49 for communicating the adjacent sub-separation chambers 431, and the flow passage sectional area of the separation channel 49 is smaller than the flow passage sectional area of the sub-separation chamber 431. Since the flow passage sectional area of the separation passage 49 is smaller than that of the sub-separation chamber 431, the flow rate of the compressed gas in the sub-separation chamber 431 is reduced, so that the lubricating oil contained in the compressed gas is settled in the sub-separation chamber 431, thereby achieving gas-liquid separation. The compressed gas flows through the sub-separation chambers 431 and the separation channels 49 therebetween and is finally discharged from the main exhaust port 45, so that the noise reduction effect can be improved and the gas-liquid separation effect can be improved.

Referring to fig. 18, in a further preferred embodiment, the separation channel 49 comprises an upper channel 491 and a lower channel 492, the upper channel 491 being arranged relatively close to the top end of the separation stiffener 432 or at the top end of the separation stiffener 432, the lower channel 492 being arranged at the bottom end of the separation stiffener 432, a space being provided between the upper channel 491 and the lower channel 492. Since there is a space between the upper passage 491 and the lower passage 492, when the gas-liquid mixture passes through the separation passage 49, the gas mainly circulates from the upper passage 491 and the liquid mainly from the lower passage 492, so that the effect of gas-liquid separation can be enhanced.

In a further preferred embodiment, the flow path cross-sectional area of the sub-separation chamber 431: flow passage cross-sectional area of separation channel 49: the ratio of the flow path sectional areas of the total exhaust ports 45 is: 3-30:1-1.8:1. Flow passage cross-sectional area of separation channel 49: the ratio of the flow path sectional area of the total exhaust port 45 is 1-1.8:1, so that the flow rate of the gas in the separation channel 49 is close to the flow rate of the total exhaust port 45, and if the ratio of the flow path sectional area of the sub-separation chamber 431 to the flow path sectional area of the separation channel 49 is too small, the gas-liquid separation effect is poor, and if it is too large, the strength of the cylinder 4 is easily affected.

Referring to fig. 17, in a further preferred embodiment, a plurality of buffer chambers 441 are further formed between the cylinder outer wall 421 and the cylinder inner wall 422, adjacent buffer chambers 441 are separated by buffer reinforcing ribs 442 disposed between the cylinder outer wall 421 and the cylinder inner wall 422, and buffer channels for communicating the adjacent buffer chambers 441 are disposed on the buffer reinforcing ribs 442, and the flow channel cross-sectional area of the buffer channels is smaller than that of the buffer chambers 441. The cylinder 4 is provided with a total air inlet 46, the inner wall 422 of the cylinder is provided with an air suction port 48, and low-pressure air sequentially enters the inner cavity 41 of the cylinder through the total air inlet 46, the plurality of buffer cavities 441 and the air suction port 48. The auxiliary bearing 6 may be provided with an intake passage and connected to the main intake pipe 91, and the main intake hole 46 may be communicated with the intake passage on the auxiliary bearing 6, and low-pressure gas entering from the main intake pipe 91 passes through the intake passage on the auxiliary bearing 6 and the main intake hole 46 and enters the cylinder 4. When the low pressure gas passes through the plurality of buffer chambers 441 and the buffer channels disposed therebetween, the noise of the suction can be reduced. The low pressure gas entering from the main intake port 46 often also contains incompletely vaporized liquid refrigerant, which in prior art cylinders is introduced directly into the cylinder chamber 41 from the intake port, and the liquid refrigerant cannot be compressed, thus reducing the compression efficiency of the compressor, and if it is discharged from the discharge valve, the discharge valve may be damaged due to its excessively high velocity. In the embodiment of the present invention, by providing a plurality of buffer chambers 441 and buffer channels, the liquid refrigerant needs to pass through the plurality of buffer chambers 441 between the outer wall 421 and the inner wall 422 of the cylinder, and then enters the inner chamber 41 of the cylinder through the air suction port 48. Since the cylinder 4 generates a certain temperature during the operation of the compressor, when the liquid refrigerant passes through the plurality of buffer cavities 441, the liquid refrigerant is heated and gasified, and becomes gaseous into the cylinder cavity 41, so that the problem caused by the liquid refrigerant entering the cylinder cavity 41 does not exist.

Referring to fig. 13, in the preferred embodiment, the cylinder 4 is further provided with a slide slot 47 in communication with the cylinder cavity 41, the slide 7 is movably mounted in the slide slot 47, and can be extended or retracted into the slide slot 47, and the tail end of the slide 7 is in rolling fit or sliding fit with the side surface 3202 of the eccentric rotor 32 to separate the cylinder cavity 41.

Referring to fig. 19 and 20, the compressor according to the preferred embodiment of the present invention further includes an oil drain assembly 94, where the oil drain assembly 94 is connected to the gas-liquid separation chamber 43, and is used for draining the liquid (specifically, the lubricating oil) in the gas-liquid separation chamber 43 out of the compressor pump body.

In a further preferred embodiment, an oil sump 8 is also provided in the compressor housing 1, the oil sump 8 being located below the secondary bearing 6, and an oil drain assembly 94 may drain liquid in the gas-liquid separation chamber 43 into the oil sump 8. The drain assembly 9 includes a gap drain 941, the gap drain 941 including a spindle 9411 and a spindle mount 9412 that mates with the spindle 9411, the spindle mount 9412 having an internal bore formed therein into which the spindle 9411 is inserted and is in gap-fit with the internal bore. A clearance passage is formed between the spindle 9411 and the inner wall of the mounting through hole of the spindle mount 9412, through which the liquid in the gas-liquid separation chamber 43 passes, and is discharged into the oil pool 8. To facilitate clearance passage oil feed, the top of the bore is tapered (as shown in FIG. 21), which also facilitates mounting of the spindle 9411 into the spindle mount 9412. The air pressure difference is arranged between the air-liquid separation cavity 43 and the oil pool 8, and the lubricating oil separated by the air-liquid separation cavity 43 passes through a gap channel between the mandrel 9411 and the mandrel mounting seat 9412 under the action of the air pressure difference and is discharged into the oil pool 8, so that the real air-liquid separation is realized.

In a further preferred embodiment, the width of the gap channel is 0.001mm-0.020mm, i.e. the width of the gap between the spindle 9411 and the inner wall of the inner bore is 0.001mm-0.020mm in the radial direction of the spindle 9411. In the compressor industry, according to different working conditions required by a temperature regulating system, different refrigerants, such as common R22, R134a and the like, are selected, different lubricating oils are required to be selected and pre-packaged in a compressor shell, and the viscosity, density, intersolubility with the refrigerant, flowability and other characteristics of the different lubricating oils are also greatly different, so that the width of a clearance channel is required to be matched with the selected lubricating oil. Taking 68# lubricating oil as an example for illustration; when No. 68 lubricating oil is used, the fit clearance between the spindle 9411 and the bore of the spindle mount 9412 is 0.002mm. Oil drain assembly 94 also includes a first oil passage 942 and a second oil passage 943. The first oil passage 942 is formed on the auxiliary bearing 6, and an inlet of the first oil passage 942 is communicated with the gas-liquid separation chamber 43, and oil is guided from the gas-liquid separation chamber 43 to an inlet of the gap passage. The second oil passage 943 may be provided on the muffler cover 93, and is used for communicating the outlet of the gap passage with the oil pool 8, and guiding the oil from the outlet of the gap passage to the oil pool 8. The oil in the gas-liquid separation chamber 43 passes through the first oil passage 942, the gap passage and the second oil passage 943 in this order, and is discharged to the oil pool 8.

In a further preferred embodiment, the first oil passage 942 and/or the second oil passage 943 are offset from the spindle 9411 to enable the spindle 9411 to be confined within the bore. To prevent the spindle 9411 from falling out of the spindle mount 9412 during operation of the compressor, one or both of the first and

second oil passages

942, 943 are offset from the spindle 9411 to form a blocking position, i.e. the first and

second oil passages

942, 943 are not coaxial with the spindle 9411.

In a further preferred embodiment, the oil drain assembly 9 further comprises a filter structure 944, an oil drain hole is provided in the gas-liquid separation chamber 43, a first oil passing channel 942 is provided on the auxiliary bearing 6, the filter structure 944 is provided in the oil drain hole or between the oil drain hole and the first oil passing channel 942, and an inlet of the first oil passing channel 942 is communicated with an outlet of the filter structure 944. The filter structure 944 is provided with magnetic blocks therein, and the filter pores of the filter structure 944 are smaller than 0.005mm. The compressor will produce metal abrasion when working, forms some metal fragments, and these metal fragments can plug clearance oil extraction structure 941, in order to improve the filter effect of filter structure 944, adds a magnetism piece on filter structure 944 to adsorb the metallic impurity in the lubricating oil, prevent metallic impurity from blockking up filter structure 944.

In a preferred embodiment, an oil sump 8 is also provided in the compressor housing 1, the oil sump 8 being located below the auxiliary bearing 6, and an oil supply device (not shown) is connected to the oil sump 8 for delivering oil from the oil sump 8 into the cylinder 4, which oil supply device is also provided in the compressor housing 1 below the auxiliary bearing 6. The oil supply device may be an oil pump, which may be connected to the rotating shaft 31, and may deliver oil to the oil guide channel 313 in the rotating shaft 31, and further, the oil guide channel 313 may enter the cylinder inner cavity 41 and between the cylinder 4 and the main bearing 5 and the auxiliary bearing 6, so as to implement circulation supply of lubricating oil. In this embodiment, since the gas-liquid separation chamber 43 can settle the lubricating oil, the gas-liquid separation is performed, the lubricating oil in the gas-liquid separation chamber 43 is truly separated from the gaseous refrigerant by the oil discharging assembly 94, and enters the oil sump 8, and then is conveyed from the oil sump 8 to the cylinder cavity 41 of the cylinder 4 and between the cylinder 4 and the main bearing 5 and the auxiliary bearing 6 by the oil supplying device, the oil supplying system has a very simple and compact structure, and the circulation is completed directly in the compressor housing 1.

The embodiment of the invention also provides a temperature regulating system which can be used for refrigerating or heating, and particularly can be applied to electric appliances such as air conditioners, refrigerators and the like. The temperature regulating system comprises the compressor of any embodiment, an evaporator and a condenser, and refrigerant circulates among the compressor, the evaporator and the condenser. The cooling and heating principle of the temperature adjusting system is common knowledge in the art, and is not described herein. In a preferred embodiment, the refrigerant is a carbon dioxide refrigerant.

The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The above examples merely represent specific embodiments of the invention, which are described in more detail and are not to be construed as limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.

Claims

1. The compressor pump body comprises a cylinder, a main bearing, an auxiliary bearing, a compressor rotor and a sliding vane, wherein a cylinder cavity and an air suction port communicated with the cylinder cavity are formed in the cylinder, the main bearing and the auxiliary bearing are respectively fixed on two sides of the cylinder to seal the cylinder cavity, the compressor rotor comprises a rotating shaft and a eccentric rotor connected with the rotating shaft, the eccentric rotor is accommodated in the cylinder cavity, the rotating shaft is respectively in rotary fit with the main bearing and the auxiliary bearing and is used for driving the eccentric rotor to rotate, the sliding vane is movably arranged in the cylinder and is in movable fit with the eccentric rotor and is used for separating the cylinder cavity, the eccentric rotor rotates relative to the cylinder, the main bearing and the auxiliary bearing under the driving of the rotating shaft, the eccentric rotor is provided with a side surface extending along the circumferential direction of the rotating shaft and an end surface connecting the upper end and the lower end of the side surface, the eccentric rotor is provided with an air guide channel, the air guide channel is communicated with the inner cavity of the cylinder, the eccentric rotor is provided with a second cavity, the main bearing and/or the auxiliary bearing is provided with a transition channel, the position of the transition channel corresponds to the positions of the air guide channel and the second cavity, a connecting line from the center of the rotating shaft to the center of the sliding vane is taken as a zero line, when the eccentric rotor rotates to a preset position between an exhaust end position and the zero line, the transition channel is simultaneously communicated with the second cavity and the air guide channel, when the eccentric rotor rotates to a preset position between the zero line and the air inlet end position, the transition channel is not simultaneously communicated with the second cavity and the air guide channel, and when the eccentric rotor rotates to a preset position between the air inlet end position and the exhaust start position, the transition channel is simultaneously communicated with the air guide channel and the second cavity.

2. The compressor pump body of claim 1, wherein when the eccentric rotor rotates to a preset position between an exhaust end position and a zero position and the transition channel is simultaneously communicated with the second cavity and the air guide channel, the clearance compressed air in the inner cavity of the cylinder sequentially passes through the air guide channel and the transition channel and enters the second cavity, and when the eccentric rotor rotates to a preset position between an intake end position and an exhaust start position, the transition channel is simultaneously communicated with the air guide channel and the second cavity and the air in the second cavity sequentially passes through the transition channel and the air guide channel and enters the inner cavity of the cylinder.

3. The compressor pump body of claim 1, wherein the air guide channel comprises an air guide groove arranged on the end surface and an air guide opening arranged on the side surface, the air guide opening is communicated with the inner cavity of the cylinder and the air guide groove, and the position of the transition channel corresponds to the position of the air guide groove.

4. A compressor pump body according to claim 3, wherein, on the cross section of the eccentric rotor, a connection line from the center of the rotating shaft to the highest point of the eccentric portion of the eccentric rotor is used as a bus, two sides of the bus are respectively formed with second cavities, two adjacent second cavities are separated by a second reinforcing rib, and an auxiliary channel for communicating the two adjacent second cavities is arranged on the second reinforcing rib.

5. The compressor pump body of claim 4, wherein the second stiffener extends along the bus bar, the air guide groove being open on the second stiffener;

6. The compressor pump body of claim 3, wherein the eccentric rotor has an eccentric portion remote from the shaft, the end surfaces include an upper end surface and a lower end surface, the shaft projects relative to the upper end surface and the lower end surface, the shaft projects a greater length relative to the upper end surface than the lower end surface, the air guide slot is open on the lower end surface of the eccentric rotor and has an open top, and the air guide opening is open on the eccentric portion of the eccentric rotor.

7. A compressor pump body according to claim 3, wherein, on the cross section of the eccentric rotor, a line from the center of the rotating shaft to the highest point of the eccentric portion of the eccentric rotor is taken as a bus, the air guide groove comprises an air guide starting section and an air guide connecting section, the first end of the air guide starting section faces the rotating shaft, the second end of the air guide starting section is connected with the first end of the air guide connecting section, the second end of the air guide connecting section is communicated with the air guide port, the air guide starting section extends along the bus, and the air guide connecting section is bent relative to the air guide starting section.

8. The compressor pump body of claim 3, wherein the cross section of the eccentric rotor is egg-shaped and has an egg head end and an egg tail end, the egg tail end is in contact with the cylinder, the radius of curvature of the egg tail end is smaller than that of the egg head end, the distance from the egg tail end to the center of the rotating shaft is greater than that from the egg head end to the center of the rotating shaft, the air guide groove extends from the periphery of the rotating shaft to the egg tail end, and the air guide opening is formed in the egg tail end.

9. The compressor pump body of claim 8, wherein the egg head end and the egg tail end are arc-shaped, and are connected through a tangent line or an arc line, the ratio of the curvature radius of the egg head end to the curvature radius of the egg tail end is between 1.3 and 2.5, and the ratio of the center distance of the egg head end to the curvature radius of the egg tail end is between 1.5 and 3.

10. The compressor pump body of claim 1, wherein the transition passage includes a first transition passage and a second transition passage disposed in spaced relation, the first transition passage simultaneously communicates the second cavity with the air guide passage when the eccentric rotor rotates to a preset position between the exhaust end position and the zero line, the first transition passage and the second transition passage both do not simultaneously communicate the second cavity with the air guide passage when the eccentric rotor rotates to a preset position between the zero line and the intake end position, and the second transition passage simultaneously communicates the air guide passage with the second cavity when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position.

11. The compressor pump body of claim 1, wherein an exhaust channel is formed on the main bearing or the auxiliary bearing, when the compressor pump body is in a compressed state, the exhaust channel is communicated with the air guide channel, compressed gas in the inner cavity of the cylinder is discharged out of the compressor pump body through the air guide channel and the exhaust channel, and when the compressor pump body is in an air suction state, the exhaust channel is not communicated with the air guide channel.

12. The compressor pump body of claim 11, wherein the initial on position of the air guide passage and the air discharge passage corresponds to a rotation angle between 220 degrees and 250 degrees or between 260 degrees and 310 degrees.

13. The compressor pump body of claim 11, wherein the cylinder includes an outer cylinder wall and an inner cylinder wall, the inner cylinder wall having the cylinder cavity formed therein, a gas-liquid separation chamber formed between the outer cylinder wall and the inner cylinder wall, the exhaust passage communicating with the gas-liquid separation chamber, and a total exhaust port provided on the cylinder, the compressed gas in the cylinder cavity being exhausted out of the cylinder through the gas guide passage, the exhaust passage, the gas-liquid separation chamber, and the total exhaust port when the compressor pump body is in a compressed state.

14. The compressor pump body of claim 13, wherein the gas-liquid separation chamber comprises one or more sub-separation chambers, adjacent sub-separation chambers are separated by separation reinforcing ribs arranged between the outer wall of the cylinder body and the inner wall of the cylinder body, the separation reinforcing ribs, the inner side of the outer wall of the cylinder body and the outer side of the inner wall of the cylinder body enclose the sub-separation chambers, separation channels for communicating the adjacent sub-separation chambers are arranged on the separation reinforcing ribs, and the flow passage sectional area of the separation channels is smaller than that of the sub-separation chambers.

15. The compressor pump body of claim 14, wherein the separation channel includes an upper channel disposed relatively near or at a top end of the separation stiffener and a lower channel disposed at a bottom end of the separation stiffener, a space being present between the upper channel and the lower channel.

16. The compressor pump body of claim 13, wherein a plurality of buffer cavities are further formed between the outer wall of the cylinder body and the inner wall of the cylinder body, adjacent buffer cavities are separated by a buffer reinforcing rib arranged between the outer wall of the cylinder body and the inner wall of the cylinder body, buffer channels for enabling the adjacent buffer cavities to be communicated are arranged on the buffer reinforcing rib, the flow passage sectional area of each buffer channel is smaller than that of each buffer cavity, a total air inlet hole is formed in the cylinder, the air inlet hole is formed in the inner wall of the cylinder body, and air sequentially enters the inner cavity of the cylinder through the total air inlet hole, the buffer cavities and the air inlet hole.

17. A compressor comprising a compressor housing, a drive assembly and a compressor pump body according to any one of claims 1-16, both of which are disposed in the compressor housing, the drive assembly being located on a side of the main bearing facing away from the cylinder and being connected to the shaft for driving the shaft to rotate.

18. A compressor, comprising a compressor housing, a driving assembly and a compressor pump body according to any one of claims 13-16, wherein the driving assembly and the compressor pump body are both arranged in the compressor housing, and the driving assembly is positioned at one side of the main bearing, which is away from the cylinder, and is connected with the rotating shaft, so as to drive the rotating shaft to rotate; the compressor also comprises an oil discharging assembly, wherein the oil discharging assembly is connected with the gas-liquid separation cavity and is used for discharging liquid in the gas-liquid separation cavity out of the compressor pump body.

19. The compressor of claim 18, wherein an oil sump is further provided in the compressor housing, the oil sump being located below the secondary bearing, the oil drain assembly including a gap oil drain structure including a mandrel and a mandrel mount mated with the mandrel, a gap passage being formed between the mandrel and the mandrel mount, the liquid in the gas-liquid separation chamber being drained into the oil sump through the gap passage.

20. A temperature regulation system comprising a compressor as claimed in any one of claims 17 to 19, and further comprising an evaporator and a condenser, wherein refrigerant circulates between the compressor, the evaporator and the condenser.