CN217898186U

CN217898186U - Compressor pump body, compressor and temperature regulation system

Info

Publication number: CN217898186U
Application number: CN202221368094.4U
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: 2022-11-25
Anticipated expiration: 2032-06-02

Abstract

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

Description

Compressor pump body, compressor and temperature regulation system

Technical Field

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

Background

After the exhaust of the rotor compressor is finished, gaps, called clearances, are still formed among the eccentric rotor, the inner wall of the cylinder and the sliding vane, and the pressure of gas in the clearances is equivalent to the exhaust pressure of the compressor. When the highest point of the eccentric core rotor crosses the sliding sheet and rotates through an angle beta, the clearance is communicated with the air suction cavity behind the highest point, the high-pressure clearance air expands to the air suction pressure P0 again, and the sucked air is extruded out of the air suction port of the air 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 increasing the actual displacement volume, a compressor and a temperature adjusting system.

The embodiment of the invention provides a compressor pump body, which comprises an air cylinder, a main bearing, an auxiliary bearing, a compressor rotor and a slip sheet, wherein an air cylinder inner cavity and an air suction port communicated with the air cylinder inner cavity are formed in the air cylinder, the main bearing and the auxiliary bearing are respectively fixed at two sides of the air cylinder to seal the air cylinder inner cavity, the compressor rotor comprises a rotating shaft and an eccentric rotor connected with the rotating shaft, the eccentric rotor is contained in the air cylinder inner cavity, the rotating shaft is respectively in rotating fit with the main bearing and the auxiliary bearing and used for driving the eccentric rotor to rotate, the slip sheet is movably arranged in the air cylinder and movably matched with the eccentric rotor and used for separating the air cylinder inner cavity, and the eccentric rotor is driven by the rotating shaft to rotate relative to the air cylinder, the main bearing and the auxiliary bearing, the eccentric rotor is provided with a side surface extending along the circumferential direction of a rotating shaft and an end surface connected with the upper end and the lower end of the side surface, the end surface comprises an upper end surface and a lower end surface, the upper end surface and the lower end surface are parallel and are respectively contacted with the inner surfaces of the main bearing and the auxiliary bearing, the rotating shaft protrudes relative to the upper end surface and the lower end surface to respectively form a main shaft and an auxiliary shaft, the main shaft and the auxiliary shaft are integrally and coaxially arranged, the length of the main shaft is greater than that of the auxiliary shaft, the eccentric rotor is provided with an air guide channel 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, and the connecting line from the center of the rotating shaft to the center of the sliding blade is a zero line on the cross section of the compressor pump body, when the eccentric rotor rotates to the preset position between the exhaust end position and the zero line, the transition channel is communicated with the second cavity and the air guide channel at the same time, when the eccentric rotor rotates to the zero line and between the air inlet end position, the transition channel is not communicated with the second cavity and the air guide channel at the same time, when the eccentric rotor rotates to the preset position between the air inlet end position and the exhaust start position, the transition channel is communicated with the air guide channel and the second cavity at the same time.

As a further improvement of the above embodiment, when the eccentric rotor rotates to a position between the exhaust end position and the zero line and the transition channel is simultaneously communicated with the second cavity and the gas guide channel, the clearance compressed gas in the cylinder cavity sequentially passes through the gas guide channel and the transition channel and enters the second cavity, when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position, the transition channel is simultaneously communicated with the gas guide channel and the second cavity, and the gas in the second cavity sequentially passes through the transition channel and the gas guide channel and enters the cylinder cavity.

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 opening disposed on the side surface, the air guide opening is communicated with the cylinder inner 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 core-offset rotor, a connecting line from the center of the rotating shaft to the highest point of the core-offset portion of the core-offset rotor is used as a bus, second cavities are respectively formed on two sides of the bus, two adjacent second cavities are spaced 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 rib extends along the bus bar, and the air guide groove is opened on the second reinforcing rib;

the auxiliary channel is a conduction groove formed in the end face of the core-offset rotor, and the auxiliary channel 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

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 an eccentric portion away from the rotating shaft, the air guide groove is opened on a lower end surface of the eccentric rotor and is open at the top, and the air guide opening is opened on the eccentric portion of the eccentric rotor.

As a further improvement of the above embodiment, on the cross section of the core-shifted rotor, a connecting line from the center of the rotating shaft to the highest point of the core-shifted portion of the core-shifted rotor is used as a bus, the air guide groove includes an air guide starting section and an air guide connecting section, a first end of the air guide starting section faces the rotating shaft, a second end of the air guide starting section is connected with a first end of the air guide connecting section, a 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 in an egg shape, and has an egg head end and an egg tail end, the egg tail end is in contact with the cylinder, the curvature radius 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 egg tail end of the rotating shaft Zhou Cexiang, and the air guide opening is arranged at the egg tail end.

As a further improvement of the above embodiment, the egg head end and the egg tail end are both arc-shaped, and the egg head end and the egg tail end are connected by 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 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 arranged at an interval, and in the rotation direction of the eccentric rotor, the first transition channel is located between the exhaust groove 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 communicated with the second cavity and the air guide channel at the same time, 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 communicated with the second cavity and the air guide channel at the same time, when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position, the second transition channel is communicated with the air guide channel and the second cavity at the same time.

As a further improvement of the above embodiment, an exhaust passage is provided on the main bearing or the secondary bearing, when the compressor pump body is in a compressed state, the exhaust passage is communicated with the air guide passage, compressed air in the cylinder cavity is exhausted outside the compressor pump body through the air guide passage and the exhaust passage, and when the compressor pump body is in an air suction state, the exhaust passage is not communicated with the air guide passage.

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

As a further improvement of the above embodiment, the cylinder includes a cylinder outer wall and a cylinder inner wall, the cylinder inner wall is formed with a cylinder inner cavity, a gas-liquid separation cavity is formed between the cylinder outer wall and the cylinder inner wall, the exhaust passage is communicated with the gas-liquid separation cavity, the cylinder is further provided with a total exhaust port, and when the compressor pump body is in a compression state, compressed gas in the cylinder inner cavity is discharged outside the cylinder through the gas guide passage, the exhaust passage, the gas-liquid separation cavity and the total exhaust port.

As a further improvement of the above embodiment, the gas-liquid separation chamber includes one or more sub-separation chambers, adjacent sub-separation chambers are separated by a separation reinforcing rib arranged between the outer wall of the cylinder body and the inner wall of the cylinder body, the separation reinforcing rib, 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, a separation channel for communicating the adjacent sub-separation chambers is arranged on the separation reinforcing rib, and the cross-sectional area of the flow channel of the separation channel is smaller than that of the flow channel of the sub-separation chambers.

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 above 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 for communicating the adjacent buffer cavities are arranged on the buffer reinforcing ribs, the flow channel sectional area of each buffer channel is smaller than that of each buffer cavity, a total air inlet hole is arranged on the cylinder, the inner wall of the cylinder body is provided with the air suction port, and air sequentially passes through the total air inlet hole, the buffer cavities and the air suction port to enter the inner cavity of the cylinder.

The embodiment of the invention also provides a compressor, which comprises a compressor shell, a driving assembly and the compressor pump body in any embodiment, wherein the driving assembly and the compressor pump body are both arranged in the compressor shell, and the driving assembly is positioned on one side of the main bearing, which is far away from the 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 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 on one side of the main bearing, which is far away from the cylinder, and is connected with the rotating shaft and used for driving the rotating shaft to rotate; the compressor further comprises an oil discharge assembly, wherein the oil discharge assembly is connected with the gas-liquid separation cavity and 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 provided in the compressor housing, the oil sump is located below the auxiliary bearing, the oil discharge assembly includes a gap oil discharge structure, the gap oil discharge structure includes a mandrel and a mandrel mounting seat matched with the mandrel, a gap passage is formed between the mandrel and the mandrel mounting seat, and liquid in the gas-liquid separation cavity passes through the gap passage and is discharged into the oil sump.

The embodiment of the invention also provides a temperature adjusting system, which comprises the compressor, 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 adjusting 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 does not influence the air intake of the compressor pump body, and the actual displacement volume of the compressor is effectively increased.

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 intended to be drawn to scale in actual dimensions, emphasis instead being placed upon illustrating the principles of the invention.

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

Fig. 2 and 3 are a partial exploded view and an assembled view of a pump body of a compressor 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 structural view of the sub-bearing of fig. 2.

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

Fig. 12 is a partially 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 structural view of a sub-bearing correspondingly engaged with the compressor rotor of fig. 11.

FIG. 15 is a schematic comparison of the compressor pump body of FIG. 13 and 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 structural view of a compressor according to another embodiment of the present invention.

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

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

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

FIG. 27 is a schematic representation of the compression ratio versus generatrix angle for the compressor pump body of FIG. 13.

Detailed Description

To facilitate an understanding of the invention, the invention will now be described more fully 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 the other element and be integral therewith, 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. As used herein, the term "and/or" 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 both arranged in the compressor shell 1. The compressor pump body comprises a cylinder 4, a main bearing 5, an auxiliary bearing 6, a compressor rotor 3 and a sliding vane 7. The cylinder 4 has a cylinder chamber 41 and an intake port 48 communicating with the cylinder chamber 41 formed therein. 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 inner 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 an 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 rotating shaft 31 and the eccentric rotor 32 may be integrally formed or may be provided separately. The eccentric rotor 32 is accommodated in the cylinder chamber 41, and both ends of the rotary shaft 31 protrude with respect to the end faces of the eccentric rotor 32, respectively, and are rotatably engaged with the main bearing 5 and the sub-bearing 6, respectively. The eccentric rotor 32 is driven by the rotating shaft 31 to rotate relative to the cylinder 4, the main bearing 5 and the auxiliary bearing 6. The sliding vane 7 is movably arranged in the cylinder 4 and is movably matched with the eccentric rotor 32 for separating the cylinder inner cavity 41. The driving assembly 2 is located on a side (i.e. an upper side in fig. 2) of the main bearing 5 facing away from the cylinder 4, and is connected to the rotating shaft 31 for driving the rotating shaft 31 to rotate. The driving assembly 2 may be a motor, which includes a stator and a rotor, etc., and since the structure of the motor is a known structure, the description thereof is omitted.

Referring to fig. 4 to 6, the eccentric rotor 32 is cylindrical, such as a cylinder, an elliptic cylinder, etc. The eccentric rotor 32 has a side surface 3202 extending circumferentially around the rotary 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., a non-return thrust surface) and a lower end surface 3203 (i.e., a thrust surface), and the upper end surface 3204 and the lower end surface 3203 are arranged in parallel and are in contact with inner surfaces of the main bearing 5 and the sub-bearing 6, respectively. An air guide channel is arranged on the core-offset rotor 32, 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 the lower end surface 3203. The gas guide port 322 communicates with the cylinder chamber 41 so that the cylinder chamber 41 can communicate gas with the outside through the gas guide passage.

In the preferred embodiment, the eccentric rotor 32 has an eccentric portion that is remote from the rotating shaft 31. Since the rotating shaft 31 is disposed on the eccentric rotor 32 in an eccentric manner (i.e., the center of the rotating shaft 31 is not coincident with the center of the eccentric rotor 32), a distance between one part of the side surfaces 3202 of the eccentric rotor 32 and the center of the rotating shaft 31 is greater than a distance between the other part of the side surfaces 3202 and the center of the rotating shaft 31, which is an eccentric portion. In the present invention, on the cross section of the compressor pump body, a connecting 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 on the cross section of the eccentric rotor 32) is defined as a bus 3201, and an area where an angle formed by a connecting line between the corresponding point on the side surface 3202 and the center of the rotating shaft 31 and the bus 3201 is within 20 degrees is defined as the eccentric portion. A line connecting the center of the rotating shaft 3 to the center of the sliding piece 7 is taken as a zero line 3205, and an included angle between the bus 3201 and the zero line 3205 along the rotation direction of the eccentric rotor 32 is taken as a rotation angle of the eccentric rotor 32. The rotation shaft 31 protrudes from the upper end surface 3204 and the lower end surface 3203 to form a main shaft 311 and a sub shaft 312, respectively, the main shaft 311 is integrally and coaxially disposed with the sub shaft 312, and the length of the main shaft 311 is greater than that of the sub shaft 312. The main shaft 311 penetrates through the main bearing 5 and is connected with the driving assembly 2, and the main shaft 311 is in rotating fit with the main bearing. The secondary shaft 312 is in rotational engagement with the secondary bearing 6. The protruding length of the rotating shaft 31 (i.e., the length of the main shaft 311) with respect to the upper end surface 3204 is greater than the protruding length (i.e., the length of the sub shaft 312) with respect to the lower end surface 3203. The air guide groove 321 opens on the lower end surface 3203 of the eccentric rotor 32 and has an open top, and the air guide opening 322 opens 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 communicated with the oil guiding channel 313 is formed on a side surface of the rotating shaft 31. Specifically, the oil guide passage 313 may be opened from the bottom of the sub shaft 312 to the top of the main shaft 311, and oil outlet 3111 may be opened in both the main shaft 311 and the sub shaft 312 to guide lubricating oil into the compressor pump body through the bottom of the sub shaft 312, the oil guide passage 313, and the oil outlet 3111, thereby lubricating the space between the rotating shaft 31 and the main bearing 5, the sub bearing 6, and the space between 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 of the oil outlet hole 3111 to a space 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 starting section 3251 and an oil guide diffusing section 3252, and a first end of the oil guide starting section 3251 faces the rotation shaft 31 (i.e., faces the main shaft 311) and communicates with the oil outlet port 3111. Specifically, the upper end surface 3204 of the eccentric rotor 32 is provided with an annular oil collecting groove 328 surrounding the main shaft 311, the lubricating oil flowing out from the oil outlet 3111 falls into the oil collecting groove 328, and the first end of the oil guide start section 3251 is communicated with the oil collecting groove 328, so that the lubricating oil flowing out from the oil outlet 3111 flows into the oil guide groove 325 through the oil collecting groove 328. A second end of the oil guide starting section 3251 is connected to a first end of the oil guide diffusing section 3252, and the oil guide diffusing section 3252 is bent with respect to the oil guide starting section 3251 and extends in a 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 vane 7, the oil guide diffuser 3252 is bent in a direction away from the air inlet 48. By arranging the oil guide diffusion section 3252, a large lubricating oil dispersion 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 core-offset rotor 32, a connecting line from the center of the rotating shaft 31 to the highest point of the core-offset portion of the core-offset rotor 32 is taken as a bus 3201, two sides of the bus 3201 are respectively formed with one or more first cavities 326, a first reinforcing rib 327 extending along the bus 3201 is formed between two first cavities 326 closest to the bus 3201, and the oil guide groove 325 is opened 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 may also allow the side 3202 of the eccentric rotor 32 to deform slightly when the force is applied, so as to prevent the eccentric rotor 32 from being locked in the cylinder 4.

Referring to fig. 5 and 6, in the preferred embodiment, on the cross section of the core-offset rotor 32, a connecting line from the center of the rotating shaft 31 to the highest point of the core-offset portion of the core-offset rotor 32 is taken as a bus 3201, and an included angle between the connecting line from the center of the rotating shaft 31 to the center of the air guide opening 322 and the bus 3201 is 1-20 degrees, preferably 1-5 degrees. When the eccentric rotor 32 rotates in the cylinder 4, the cylinder 4 applies an acting force toward the center of the rotating shaft 31 to the eccentric portion, wherein the acting force applied to the highest point of the eccentric portion is the largest, and the air guide port 322 deviates 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, on the cross section of the eccentric rotor 32, a connecting 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 3201. The air guide groove 321 includes an air guide initial segment 3211 and an air guide connecting segment 3212, a first end of the air guide initial segment 3211 faces the rotating shaft 31, a second end of the air guide initial segment 3211 is connected with a first end of the air guide connecting segment 3212, and a second end of the air guide connecting segment 3212 is communicated with the air guide opening 322. Specifically, the bottom of the second end of the air guide connecting segment 3212 is provided with a connecting hole 3213, and the connecting hole 3213 connects the air guide connecting segment 3212 and the air guide opening 322. The air guide initiating segment 3211 extends along a bus bar, and the air guide connecting segment 3212 is bent with respect to the air guide initiating segment 3211. When the highest point of the eccentric portion of the eccentric rotor 32 abuts against the slide sheet 7, the air guide connecting section 3212 is bent in a direction away from the air inlet 48. Through the air guide connecting section 3212, the air guide opening 322 can be 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. In another embodiment, the air guide slots 321 may extend directly to the side 3202 of the core-offset rotor 32, forming the air guide ports 322 on the side 3202 of the core-offset rotor 32.

Referring to fig. 10, in the preferred embodiment, the auxiliary bearing 6 is provided with an exhaust channel 62, when the compressor pump body is in a compressed state, the exhaust channel 62 is communicated with the air guide channel on the eccentric rotor 32, the compressed air in the cylinder cavity 41 is exhausted outside the compressor pump body through the air guide channel and the exhaust channel 62, and when the compressor pump body is in an air suction state, the exhaust channel 62 is not communicated with the air guide channel. Specifically, the exhaust passage 62 is opened on the inner surface of the sub-bearing 6 facing 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 the compression state, the air guide groove 321 rotates to the position communicating with the exhaust passage 62, and at this time, the compressed air in the cylinder cavity 41 is exhausted out of the cylinder cavity 41 through the air guide port 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 exhaust channel 62, and the compressor pump body is in a suction state. In another embodiment, the exhaust channel may open on the inner surface of the main bearing 5 opposite the eccentric rotor 32, and correspondingly the air guide channel opens on the upper end surface 3202 of the eccentric rotor 32, the working principle being similar to the above-described embodiment. The compressed gas in the cylinder inner cavity 41 is discharged through the way that the gas guide channel is communicated with the exhaust channel 62, so that an exhaust valve does not need to be arranged on the auxiliary bearing 6, on one hand, the failure of the compressor caused by the damage of the exhaust valve can be avoided, and on the other hand, the production of the compressor is not limited by the material supply of the exhaust valve.

In a further preferred embodiment, the main bearing 5 or the auxiliary bearing 6 is further provided with an air supplement channel 63, when the compressor pump body is in an air suction state, the air supplement channel 63 is communicated with the air guide channel, and the compressor pump body supplements air to the cylinder inner cavity 41 through the air supplement channel 63 and the air guide channel. Specifically, the air supply channel 63 is communicated with a refrigerant pipeline outside the compressor, and is used for guiding the medium-pressure gaseous refrigerant which is compressed by the compressor and passes through the condenser or the flash evaporator into the cylinder inner cavity 41 of the compressor through the air supply channel 63, mixing the medium-pressure gaseous refrigerant with the low-pressure gaseous refrigerant sucked through the air suction port 48, and completing compression in the cylinder inner cavity 41 along with the rotation of the eccentric rotor 32, so that the enthalpy difference of the compressed refrigerant is increased, the efficiency of the compressor is improved, and the compressor with the air supply and enthalpy increasing structure is particularly suitable for being operated and used in a severe cold environment. When the air guide channel is opened on the lower end surface 3203 of the core-offset rotor 32, the air supplement channel 63 is opened on the auxiliary bearing 6, and when the air guide channel is opened on the upper end surface 3202 of the core-offset rotor 32, the air supplement channel 63 is opened on 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 rotatably engaged with the auxiliary bearing 6. The exhaust passage 62 and the air replenishing passage 63 are both provided on the sub-bearing 6. The exhaust passage 62 includes an exhaust groove 621 and an exhaust line 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 supplement groove 631 are both in the shape of an arc extending along the circumferential direction of the first shaft hole 61, the exhaust groove 621 and the air supplement groove 631 surround the first shaft hole 61 and are arranged at opposite intervals, that is, the inner arc surfaces of the exhaust groove 621 and the air supplement groove 631 are opposite to each other, and the exhaust groove 621 and the air supplement groove 631 are spaced at a certain distance. By controlling the arc length and angle of the exhaust groove 621 and the air supplement 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 supplement 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 and is not communicated with the air supplement groove 631, and the compressed air in the cylinder inner cavity 41 is discharged outwards through the air guide port 322, the air guide groove 321, the air discharge groove 621 and the air discharge pipeline 624 in sequence. Specifically, a first exhaust hole 622 is opened in the inner surface of the sub-bearing 6, the exhaust hole 622 communicates with an exhaust path in the cylinder 4, the exhaust path is isolated from the cylinder chamber 41, and the compressed gas flows from the exhaust line 624 and the first exhaust hole 622 into the exhaust path in the cylinder 4, and is finally discharged from the compressor pump body through the total exhaust port 45 of the cylinder 4. In another embodiment, a second exhaust hole 623 is opened on the side surface of the secondary bearing 6, and the compressed gas is directly exhausted from the exhaust pipe 624 and the second exhaust hole 623 outside the compressor pump body, for example, connected to the main exhaust pipe 92 of the compressor through a pipeline. The first and second exhaust holes 622 and 623 may not be opened at the same time. When the eccentric rotor 32 rotates to the air suction position, the air guide channel is communicated with the air supplement groove 631 and is not communicated with the exhaust groove 621, and the compressor pump body sequentially passes through the air supplement pipeline 63, the air supplement groove 631, the air guide groove 321 and the air guide port 322 to supplement air into the cylinder inner cavity 41. The air supply line 63 can 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 secondary bearing 6 is provided with a transition channel 65 (fig. 14), and the transition channel 65 is located on the inner surface of the secondary bearing 6 and corresponds to the air guide groove 321 of the air guide channel. The position of the transition passage 65 corresponds to the position of the air guide passage 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 with the second cavity 323 and the air guide channel, and at the same time, the clearance gas 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 intake end position, the transition passage 65 does not simultaneously communicate the second cavity 323 with the air guide passage, and at this time, 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 passage 65 simultaneously communicates with the air guide passage and the second cavity 323, and the gas in the second cavity 323 enters the cylinder inner cavity 41 through the transition passage 65 and the air guide passage.

In the preferred embodiment, the transition passage 65 includes a first transition passage 651 and a second transition passage 652 that are spaced apart. In the rotational direction of the eccentric rotor 32, the first transition passage 651 is located between the exhaust groove 62 and the second transition passage 652. Referring to FIG. 21, when the eccentric rotor 32 is rotated to 200 degrees, the compressor pump body begins to discharge air through the air guide and discharge passages 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 passes the exhaust end position and rotates to a preset position between the exhaust end position and the zero line 3205 (the rotation angle is 0 degrees), a clearance is formed among the eccentric rotor 32, the cylinder inner wall 422 and the sliding vane 7, and compressed gas still remains in the clearance. At this time, a part of the first transition passage 651 overlaps with the position of the gas guide groove 321, and the other part overlaps with the position of the second cavity 323, so that the second cavity 323 and the gas guide groove 321 are simultaneously communicated, and the compressed gas in the clearance passes through the gas guide opening 322, the gas guide groove 321, and the first transition passage 651 in sequence, enters the second cavity 323, and is equivalent to the gas intake of the second cavity 323. At this time, the gas in the second cavity 423 is formed by mixing the clearance compressed gas and the gas in the original second cavity 423, and the gas pressure of the gas in the second cavity 423 is larger than the gas pressure in the original second cavity 423 and is also larger than the gas pressure of the intake gas.

Referring to fig. 23, the core-shifted rotor 32 continues to rotate between the exhaust end position and the zero line 3205, at this time, the first transition passage 651 is communicated with the air guide groove 321, the first transition passage 651 is not communicated with the second cavity 323, the second transition passage 652 is not communicated with the air guide groove 321, and is communicated with the second cavity 323, and the second cavity 323 neither enters nor exhausts air, and no air is communicated with the cylinder cavity 41. The eccentric rotor 32 continues to rotate and cross the null line 3205, when the eccentric rotor rotates to a position between an air inlet starting position (namely, the head edge of the air inlet 48) and an air inlet ending position (namely, the tail edge of the air inlet 48), the air in the cylinder cavity 41 starts to be introduced through the air inlet 48, 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 this time, the second cavities 323 do not introduce air and exhaust air.

Referring to fig. 24, when the eccentric rotor 32 continues to rotate to a preset position (for example, a position where the rotation angle is 30 degrees) between the intake end position and the exhaust start position, the second transition channel 652 simultaneously communicates with the air guide groove 421 and the second cavity 423, and since the air pressure in the second cavity 423 is greater than the intake air pressure, at this time, the gas 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 core-shifting rotor 32 continues to rotate (for example, to the 52-degree position), at this time, the second transition passage 652 is not communicated with the air guide groove 421, the second cavity 423 does not exhaust the air to the cylinder cavity 41 any more, that is, the air exhausting process of the second cavity 423 is finished. Then the eccentric rotor 32 continues to rotate, and a cycle process of air intake and exhaust of the second cavity 423 is formed. In the present embodiment, the second cavity 423 functions as a transition air cavity in addition to the aforementioned weight reduction effect, which allows the eccentric rotor 32 to deform slightly, so that the clearance air does not affect the intake of the compressor, thereby improving the volumetric efficiency of the compressor.

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

Referring to fig. 14 and 21 to 25, in the present embodiment, the air guide groove 321 is arc-shaped and extends around the circumference of the auxiliary shaft 322, the air discharge groove 621 is arc-shaped and extends along the circumference of the first shaft hole 61, and the distance from the air guide groove 321 to the center of the auxiliary shaft 322 is substantially equal to the distance from the air discharge 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 core-offset portion along the second rib 324, and the two sides of the auxiliary air guide groove 3215 are not equidistant from the second cavities 323 at the two sides of the second rib 324. The auxiliary air guide groove 3215 is configured to communicate with the first and second transition passages 652, so that the first and

second transition passages

652, 652 communicate with the air guide groove 321. Because the distance between the two sides of the auxiliary air guide groove 3215 and the second cavities 323 at the two sides of the second reinforcing rib 324 is not equal, the first transition channel 652 can communicate the auxiliary air guide groove 3215 with the second cavities when being located at one side of the auxiliary air guide groove 3215, and can not communicate the auxiliary air guide groove 3215 with the second cavities when being located at the other side of the auxiliary air guide groove 3215.

Referring to fig. 21, when the eccentric rotor 32 rotates to 200 degrees (i.e. the included angle between the bus 3201 and the zero line 3205 is 200 degrees), the compressor pump body is in a compressed state, the positions of the air guide groove 321 and the air discharge groove 621 start to overlap, which is referred to as the initial conduction position of the air guide channel and the air discharge channel (i.e. the air discharge initial position), so that the air guide groove 321 is conducted with the air discharge groove 621, and at this time, the compressed air in the cylinder inner cavity 41 enters the gas-liquid separation chamber 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 continues to be vented. Referring to fig. 2, when the eccentric rotor 32 rotates to 335 degrees, the compressor body is still in a compressed state, and the air guiding slot 321 and the air discharging slot 621 do not overlap (i.e. the air discharging end position), i.e. the air guiding slot 321 and the air discharging slot 621 are not connected, and the air discharging is ended. For the compressor pump body of the embodiment of the invention, the rotation angle corresponding to the exhaust starting position is directly related to the compression ratio of the compressor. FIG. 27 illustrates a simulated curve of bus bar angle (i.e., rotational angle) versus compression ratio in one embodiment. For air conditioning compressors, the compression ratio is typically around 3-4, so the rotation angle of the discharge start position is preferably between 220 and 250 degrees. For a refrigerator compressor, the compression ratio is generally about 5-10 depending on the refrigerant, and thus the rotation angle of the discharge start position is preferably between 260 and 310 degrees. The discharge end position of the compressor is generally set between 330 degrees and 340 degrees.

Referring to fig. 5 and 6, in the preferred embodiment, on the cross section of the core-offset rotor 32, a connecting line from the center of the rotating shaft 31 to the highest point of the core-offset portion of the core-offset rotor 32 is used as a bus 3201, second cavities 323 are respectively formed at two sides of the bus 3201, two adjacent second cavities 323 are spaced by the second reinforcing rib 324, and the air guide groove 321 is opened on the second reinforcing rib 324. The second cavity 323 may be integral with (i.e., the same as) the first cavity 326, or may be separate from the first cavity 326, which may also reduce the weight of the eccentric rotor 32 and cause the side 3202 of the eccentric rotor 32 to deform slightly when the force is applied thereto, thereby preventing the eccentric rotor 32 from being locked in the cylinder 4. The second ribs 324 can ensure the eccentric rotor 32 to have sufficient strength, and can reasonably set the position of the air guide groove 321. It should be noted that, the phrase "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 cross the bus bar 3201, but means that the second cavities 323 are formed on both sides of the bus bar 3201. Taking the embodiment shown in fig. 22 and 23 as an example, the cross-sectional areas of the second cavities 323 at both sides of the reinforcing rib 324 are different, wherein a part of the second cavity 323 with a larger cross-sectional area crosses the bus bar 3201, i.e., the main part of the second cavity 323 is located at one side of the bus bar 3201, and the other side of the bus bar 3201 has a small part of the second cavity 323 and another second cavity 323 with a smaller cross-sectional area. One or more second cavities 323 may be provided on the bus 3201 side.

Referring to fig. 11 and 12, in a further preferred embodiment, the second cavities 323 at both sides of the bus 3201 are communicated through the auxiliary channel 3241 opened on the second reinforcing rib 324, so that the two second cavities 323 together form a transition air cavity. In this embodiment, the off-center rotor 32 is egg-shaped in cross-section. 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 conduction 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 another end surface opposite to the air guide groove 321. Specifically, the auxiliary passage 3241 may be opened on the upper end surface 3204 or the lower end surface 3203 of the core-offset rotor 32. In the present embodiment, the auxiliary passage 3241 and the air guide groove 321 are both located on the lower end surface 3203 of the eccentric rotor 32. The auxiliary channel 3241 may also be a through hole penetrating the second reinforcing rib 324.

Referring to fig. 11 to 15, in another preferred embodiment, the eccentric rotor 32 has an egg-shaped cross section having an egg-shaped head end (i.e., an upper end in fig. 15) and an egg-shaped tail end (i.e., a lower end in fig. 15), the egg-shaped tail end has a smaller radius of curvature than the egg-shaped head end, the egg-shaped tail end is spaced apart from the center of the rotary shaft 31 by a distance greater than the egg-shaped head end and the center of the rotary shaft 31, and the air guide grooves 321 extend from the periphery of the rotary shaft 31 toward the egg-shaped tail end. Referring to fig. 15, the outline of the shaded area a is a side projection of the circular eccentric rotor 32, the inner outline of the shaded area a is a side projection of the egg-shaped eccentric rotor 32 of this embodiment, and when the eccentric rotors 32 have the same maximum outer diameter, the cross-sectional area (i.e., the occupied whole volume) occupied by the egg-shaped eccentric rotor 32 is smaller than the cross-sectional area occupied by the circular eccentric rotor 32, so that the effective volume of the cylinder inner cavity 41 is larger.

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

Referring to fig. 16 to 18, in a preferred embodiment, the cylinder 4 includes an outer cylinder wall 421 and an inner cylinder wall 422, the inner cylinder wall 200 is disposed in the outer cylinder wall 100, the inner cylinder wall 422 forms the inner cylinder cavity 41 therein, a gas-liquid separation cavity 43 is formed between the outer cylinder wall 421 and the inner cylinder wall 422, and the exhaust channel 62 is communicated with the gas-liquid separation cavity 43. As described in the above embodiment, the exhaust passage 62 may communicate with the gas-liquid separation chamber 43 through the first exhaust hole 622 opened in the inner surface of the sub-bearing 6. The cylinder 4 is also provided with a main exhaust port 45, and when the pump body of the compressor is in a compressed state, compressed gas in the inner cavity 41 of the cylinder is exhausted out of the cylinder through the gas guide channel, the exhaust channel 62, the gas-liquid separation cavity 43 and the main exhaust port 45. Due to the existence of the gas-liquid separation cavity 43, the cylinder inner wall 422 realizes slight 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, leakage in the compression process is reduced, and the occurrence of the condition that the eccentric rotor 32 is blocked by the cylinder inner wall 422 can be reduced. Meanwhile, as the lubricating oil is arranged in the cylinder inner cavity 41, the compressed gas discharged from the cylinder inner cavity 41 carries lubricating oil droplets, and the compressed gas is led into the gas-liquid separation cavity 43, so that the gaseous refrigerant can be separated from the lubricating oil, the lubricating oil can be conveniently recycled, and the lubricating oil is prevented from entering the refrigeration pipeline. In addition, the gas-liquid separation chamber 43 can also have the functions of noise reduction, turbulence 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, and adjacent sub-separation chambers 431 are separated by separation ribs 432 provided between the cylinder outer wall 421 and the cylinder inner wall 422. The separation rib 432, 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 reinforcing 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 that of the sub-separation chambers 431. Since the flow path sectional area of the separation passage 49 is smaller than that of the sub-separation chamber 431, the flow velocity of the compressed gas in the sub-separation chamber 431 is decreased, so that the lubricant oil contained in the compressed gas is settled in the sub-separation chamber 431, thereby performing gas-liquid separation. The compressed gas flows through the sub-separation chambers 431 and the separation passages 49 therebetween and is finally discharged from the main exhaust port 45, which can improve the silencing effect and the gas-liquid separation effect.

Referring to fig. 18, in a further preferred embodiment, the separating channel 49 comprises an upper channel 491 and a lower channel 492, the upper channel 491 being disposed relatively close to or at the top end of the separating stiffener 432, the lower channel 492 being disposed at the bottom end of the separating stiffener 432, there being a spacing 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 flows through the upper passage 491 and the liquid mainly flows through the lower passage 492, so that the gas-liquid separation effect can be enhanced.

In a further preferred embodiment, the flow passage sectional area of the sub-separation chamber 431: flow passage sectional area of the separation passage 49: the ratio of the flow passage sectional areas of the total exhaust port 45 is: 3-30:1-1.8:1. Flow passage sectional area of the separation passage 49: the ratio of the flow passage sectional area of the main exhaust port 45 is 1 to 1.8, so that the gas flow rate of the separation passage 49 and the flow rate of the main exhaust port 45 can be made close to each other, and if the ratio of the flow passage sectional area of the sub-separation chamber 431 to the flow passage sectional area of the separation passage 49 is too small, the gas-liquid separation effect is not good, and if too large, the strength of the cylinder 4 is easily affected.

Referring to fig. 17, in a further preferred embodiment, a plurality of buffer cavities 441 are further formed between the cylinder outer wall 421 and the cylinder inner wall 422, adjacent buffer cavities 441 are separated by buffer ribs 442 disposed between the cylinder outer wall 421 and the cylinder inner wall 422, buffer channels for communicating the adjacent buffer cavities 441 are disposed on the buffer ribs 442, and a cross-sectional flow area of the buffer channels is smaller than a cross-sectional flow area of the buffer cavities 441. The cylinder 4 is provided with a main air inlet hole 46, the inner wall 422 of the cylinder body is provided with an air suction port 48, and low-pressure air sequentially enters the inner cavity 41 of the cylinder through the main air inlet hole 46, the plurality of buffer cavities 441 and the air suction port 48. An air inlet channel can be arranged on the auxiliary bearing 6 and connected with the main air inlet pipe 91, the main air inlet hole 46 can be communicated with the air inlet channel on the auxiliary bearing 6, and low-pressure air entering from the main air inlet pipe 91 enters the cylinder 4 through the air inlet channel on the auxiliary bearing 6 and the main air inlet hole 46. The low pressure gas may reduce noise of the suction gas when passing through the plurality of buffer chambers 441 and the buffer passage disposed therebetween. The low pressure gas entering through the main inlet port 46 often also contains liquid refrigerant that is not completely vaporized, and in the prior art cylinder, the low pressure gas and the liquid refrigerant enter the cylinder chamber 41 directly from the suction port, and the liquid refrigerant cannot be compressed, thereby reducing the compression efficiency of the compressor, and if it exits from the discharge valve, the discharge valve may be damaged due to its excessive velocity. In the embodiment of the present invention, by providing a plurality of buffer cavities 441 and buffer channels, the liquid refrigerant needs to pass through the plurality of buffer cavities 441 between the cylinder outer wall 421 and the cylinder inner wall 422, and then enter the cylinder inner cavity 41 through the 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 chambers 441, the liquid refrigerant is heated and gasified, and turns into a gas state to enter the cylinder cavity 41, and the problem caused by the liquid refrigerant entering the cylinder cavity 41 does not exist.

Referring to fig. 13, in a preferred embodiment, the cylinder 4 further has a sliding vane slot 47 communicating with the cylinder cavity 41, the sliding vane 7 is movably installed in the sliding vane slot 47 and can extend out of or retract into the sliding vane slot 47, and the tail end of the sliding vane 7 is in rolling 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 discharge assembly 94, wherein the oil discharge assembly 94 is connected to the gas-liquid separation chamber 43, and is configured to discharge the liquid (specifically, the lubricating oil) in the gas-liquid separation chamber 43 to the outside of the compressor pump body.

In a further preferred embodiment, an oil sump 8 is further disposed in the compressor housing 1, the oil sump 8 is located below the secondary bearing 6, and the oil drain assembly 94 can drain the liquid in the gas-liquid separation chamber 43 into the oil sump 8. The oil discharge assembly 9 includes a gap oil discharge structure 941, and the gap oil discharge structure 941 includes a mandrel 9411 and a mandrel mounting base 9412 matched with the mandrel 9411, and an inner hole is formed in the mandrel mounting base 9412, and the mandrel 9411 is inserted into the inner hole and is in clearance fit with the inner hole. A gap channel is formed between the spindle 9411 and the inner wall of the installation through hole of the spindle installation seat 9412, and the liquid in the gas-liquid separation chamber 43 passes through the gap channel and is discharged into the oil sump 8. To facilitate the passage of oil through the clearance, the top of the bore is tapered (as shown in fig. 21), which also facilitates the installation of the spindle 9411 into the spindle mount 9412. The gas-liquid separation cavity 43 and the oil pool 8 have a gas pressure difference therebetween, and in this embodiment, the lubricating oil separated by the gas-liquid separation cavity 43 passes through the gap passage between the spindle 9411 and the spindle mount 9412 under the effect of the gas pressure difference, and is discharged into the oil pool 8, so that gas-liquid separation is achieved.

In a further preferred embodiment, the width of the clearance channel is 0.001mm-0.020mm, i.e. the width of the clearance between the spindle 9411 and the inner wall of the inner bore in the radial direction of the spindle 9411 is 0.001mm-0.020mm. In the compressor industry, different refrigerants, such as common R22 and R134a, can be selected according to different use conditions of temperature regulation system requirements, different refrigerants need to be selected and matched with different lubricating oil and pre-packaged in a compressor shell, and the characteristics of viscosity, density, intersolubility with the refrigerant, fluidity and the like of different lubricating oil also have great difference, so that the width of a gap channel needs to be matched with the selected lubricating oil. The lubricant oil No. 68 is taken as an example for explanation; when lubricant oil # 68 is used, the fit clearance between the spindle 9411 and the inner hole of the spindle attachment 9412 is 0.002mm. The oil discharge assembly 94 further includes a first oil passage 942 and a second oil passage 943. The first oil passing passage 942 is opened on the auxiliary bearing 6, and an inlet of the first oil passing 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 clearance passage. The second oil passing channel 943 may be provided in the silencing cover 93, and is configured to communicate the outlet of the gap channel with the oil sump 8, and to guide oil from the outlet of the gap channel into the oil sump 8. The oil in the gas-liquid separation chamber 43 sequentially passes through the first oil passage 942, the gap passage, and the second oil passage 943, and is discharged to the oil sump 8.

In a further preferred embodiment, the first oil passing channel 942 and/or the second oil passing channel 943 are disposed offset from the spindle 9411 to retain the spindle 9411 in the inner hole. In order to prevent the spindle 9411 from falling off from the spindle mounting seat 9412 during operation of the compressor, one or both of the first oil passing channel 942 and the second oil passing channel 943 are dislocated with the spindle 9411 to form a stop, i.e., the first oil passing channel 942 and the second oil passing channel 943 are not coaxial with the spindle 9411.

In a further preferred embodiment, the oil discharge assembly 9 further includes a filtering structure 944, an oil discharge hole is provided in the gas-liquid separation chamber 43, the first oil passing channel 942 is provided on the secondary bearing 6, the filtering structure 944 is provided in the oil discharge hole or between the oil discharge 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 filtering structure 944. A magnetic block is arranged in the filter structure 944, and the filter pores of the filter structure 944 are smaller than 0.005mm. The compressor can produce the metal wearing and tearing at the during operation, forms some metal debris, and these metal debris can block up clearance oil extraction structure 941, for the filter effect that improves filtration 944, increase a magnetism piece on filtration 944 to the metallic impurity in the adsorption lubricating oil prevents that metallic impurity from blockking up filtration 944.

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

The embodiment of the invention also provides a temperature adjusting system which can be used for refrigeration or heating, and particularly can be applied to air conditioners, refrigerators and other electrical appliances. The temperature adjusting system comprises the compressor in any embodiment, and further comprises an evaporator and a condenser, wherein refrigerant circularly flows among the compressor, the evaporator and the condenser. The cooling and heating principles of the temperature regulation system are common knowledge in the art and are not described herein. In a preferred embodiment, the refrigerant is a carbon dioxide refrigerant.

According to the compressor pump body, the compressor and the temperature adjusting 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 does not influence the air inlet of the compressor pump body, and the actual displacement volume of the compressor is effectively increased.

The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only express the specific embodiments of the invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.

Claims

1. A compressor pump body comprises an air cylinder, a main bearing, an auxiliary bearing, a compressor rotor and a slip sheet, wherein an air cylinder inner cavity and an air suction port communicated with the air cylinder inner cavity are formed in the air cylinder, the main bearing and the auxiliary bearing are respectively fixed on two sides of the air cylinder to seal the air cylinder inner cavity, the compressor rotor comprises a rotating shaft and a core-biased rotor connected with the rotating shaft, the core-biased rotor is accommodated in the air cylinder inner cavity, the rotating shaft is respectively in rotating fit with the main bearing and the auxiliary bearing and used for driving the core-biased rotor to rotate, the slip sheet is movably arranged in the air cylinder and movably matched with the core-biased rotor and used for separating the air cylinder inner cavity, the core-biased rotor is driven by the rotating shaft to rotate relative to the air cylinder, the main bearing and the auxiliary bearing, the core-biased 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, the end face comprises an upper end face and a lower end face which are parallel and are respectively contacted with the inner surfaces of the main bearing and the auxiliary bearing, the rotating shaft protrudes relative to the upper end face and the lower end face to respectively form a main shaft and an auxiliary shaft, the main shaft and the auxiliary shaft are integrally and coaxially arranged, and the length of the main shaft is greater than that of the auxiliary shaft, the end face is characterized in that an air guide channel is arranged on the eccentric rotor and is communicated with the inner cavity of the cylinder, a second cavity is arranged on the eccentric rotor, a transition channel is arranged on the main bearing and/or the auxiliary bearing, the position of the transition channel corresponds to the positions of the air guide channel and the second cavity, and a connecting line from the center of the rotating shaft to the center of the slip sheet is a zero line on the cross section of the compressor pump body, when eccentric rotor rotates to the preset position between exhaust end position and the zero line, the transition channel communicates simultaneously second cavity and air guide channel, when eccentric rotor rotates to the zero line and admits air between the end position, the transition channel communicates second cavity and air guide channel simultaneously, when eccentric rotor rotates to the preset position between end position and the exhaust start position of admitting air, the transition channel communicates simultaneously air guide channel and second cavity.

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

3. The compressor pump body of claim 1, wherein the air guide channel comprises an air guide groove formed in the end face and an air guide opening formed in the side face, the air guide opening is communicated with the cylinder cavity and the air guide groove, and the transition channel corresponds to the air guide groove.

4. The compressor pump body according to claim 3, wherein a connecting 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 on the cross section of the eccentric rotor, second cavities are formed on two sides of the bus respectively, two adjacent second cavities are spaced by a second reinforcing rib, and an auxiliary channel for communicating the two adjacent second cavities is formed in the second reinforcing rib.

5. The compressor pump body of claim 4, wherein said second rib extends along said generatrix, and said air guide groove opens on said second rib;

6. The compressor pump body of claim 3, wherein the eccentric rotor has an eccentric portion away from the rotational axis, the air guide groove opens on a lower end surface of the eccentric rotor and is open at a top, and the air guide opening opens on the eccentric portion of the eccentric rotor.

7. The compressor pump body according to claim 3, wherein a connecting line from a center of the rotating shaft to a highest point of the eccentric portion of the eccentric rotor is used as a bus on a cross section of the eccentric rotor, the air guide groove includes an air guide starting section and an air guide connecting section, a first end of the air guide starting section faces the rotating shaft, a second end of the air guide starting section is connected with a first end of the air guide connecting section, a 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.

8. The compressor pump body of claim 3, wherein the cross-section of the eccentric rotor is egg-shaped having an egg head end and an egg tail end, the egg tail end contacting the cylinder, the egg tail end having a radius of curvature less than the egg head end, the egg tail end being spaced from the center of the shaft by a distance greater than the egg head end to the center of the shaft, the air guide slot extending from the shaft Zhou Cexiang, the air guide opening being located at the egg tail end.

9. The compressor pump body of claim 8, wherein the egg head end and the egg tail end are each in the shape of a circular arc and are connected by a tangent or an arc, the ratio of the radius of curvature of the egg head end to the radius of curvature of the egg tail end is between 1.3 and 2.5, and the ratio of the distance between the center of the circle of the egg head end and the radius of curvature of the egg tail end is between 1.5 and 3.

10. The compressor pump body of claim 1, wherein the transition channel includes a first transition channel and a second transition channel disposed at an interval, the first transition channel communicates with the second cavity and the air guide channel simultaneously when the eccentric rotor rotates to a preset position between the exhaust end position and the zero line, the first transition channel and the second transition channel both communicate with the second cavity and the air guide channel simultaneously when the eccentric rotor rotates to a position between the zero line and the intake end position, and the second transition channel communicates with the air guide channel and the second cavity simultaneously when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position.

11. The compressor pump body according to claim 1, wherein the main bearing or the secondary bearing is provided with an exhaust passage, when the compressor pump body is in a compressed state, the exhaust passage is communicated with the air guide passage, compressed air in the cylinder cavity is exhausted out of the compressor pump body through the air guide passage and the exhaust passage, and when the compressor pump body is in an air suction state, the exhaust passage is not communicated with the air guide passage.

12. The compressor pump body of claim 11, wherein the rotation angle of the initial conducting position of the air guide channel and the air discharge channel is between 220 degrees and 250 degrees or between 260 degrees and 310 degrees.

13. The compressor pump body according to claim 11, wherein the cylinder includes a cylinder outer wall and a cylinder inner wall, the cylinder inner wall forms the cylinder inner cavity, a gas-liquid separation chamber is formed between the cylinder outer wall and the cylinder inner wall, the exhaust passage communicates with the gas-liquid separation chamber, the cylinder is further provided with a main exhaust port, and when the compressor pump body is in a compressed state, compressed gas in the cylinder inner cavity is exhausted outside the cylinder through the gas guide passage, the exhaust passage, the gas-liquid separation chamber and the main exhaust port.

14. The compressor pump body according to claim 13, wherein the gas-liquid separation chamber includes one or more sub-separation chambers, adjacent sub-separation chambers are separated by a separation rib provided between the cylinder outer wall and the cylinder inner wall, the separation rib and an inner side of the cylinder outer wall and an outer side of the cylinder inner wall define the sub-separation chambers, the separation rib is provided with a separation channel for communicating the adjacent sub-separation chambers, and a flow path sectional area of the separation channel is smaller than a flow path sectional area of the sub-separation chambers.

15. The compressor pump body of claim 14, wherein the separation channel includes an upper channel and a lower channel, the upper channel being disposed relatively close to or at the top end of the separating stiffener, the lower channel being disposed at the bottom end of the separating stiffener, there being a gap 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 buffer reinforcing ribs arranged between the outer wall of the cylinder body and the inner wall of the cylinder body, buffer channels for communicating the adjacent buffer cavities are arranged on the buffer reinforcing ribs, the flow channel sectional area of the buffer channels is smaller than that of the buffer cavities, a main air inlet hole is arranged on the cylinder, the inner wall of the cylinder body is provided with the air suction port, and air enters the inner cavity of the cylinder through the main air inlet hole, the buffer cavities and the air suction port in sequence.

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

18. A compressor comprising a compressor housing, a drive assembly and a compressor pump body according to any one of claims 13 to 16, the drive assembly and the compressor pump body being 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 in rotation; the compressor also comprises an oil discharge assembly, wherein the oil discharge assembly is connected with the gas-liquid separation cavity and used for discharging the 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 disposed in the compressor housing, the oil sump is located below the secondary bearing, the oil drain assembly includes a clearance oil drain structure, the clearance oil drain structure includes a mandrel and a mandrel mounting seat engaged with the mandrel, a clearance passage is formed between the mandrel and the mandrel mounting seat, and the liquid in the gas-liquid separation chamber passes through the clearance passage and is drained into the oil sump.

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.