CN217898187U

CN217898187U - Compressor rotor, compressor pump body, compressor and temperature regulation system

Info

Publication number: CN217898187U
Application number: CN202221377253.7U
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 rotor, a compressor pump body, a compressor and a temperature adjusting system. This compressor rotor include the pivot and with the eccentric rotor that the pivot is connected, the pivot is used for driving eccentric rotor rotates, eccentric rotor has the side of revolving the extension of rotation circumference and connects the terminal surface of side upper end and lower extreme, be provided with the air guide passageway on the eccentric rotor, the air guide passageway including set up in air guide groove on the terminal surface and set up in air guide port on the side, the air guide port with air guide groove intercommunication. According to the compressor rotor, the compressor pump body, the compressor and the temperature adjusting system, the air guide channel is arranged on the compressor rotor, so that compressed air in the inner cavity of the air cylinder can be discharged out of the air cylinder through the compressor rotor, and the structure of the compressor is simpler and more reliable.

Description

Compressor rotor, compressor pump body, compressor and temperature regulation system

Technical Field

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

Background

Referring to fig. 1, in the prior art, a rotor compressor includes a compressor housing 1', a motor 2' and a compressor pump body, wherein the motor 2 'and the compressor pump body are both disposed in the compressor housing 1'. The compressor pump body comprises a cylinder 4', a main bearing 5', an auxiliary bearing 6' and a compressor rotor 3. The compressor rotor 3' includes a rotating shaft 31' and an eccentric rotor 32' connected to the rotating shaft 31', and a cylinder cavity is formed in the cylinder 4 '. 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 inner cavity of the cylinder. The rotating shaft 31 'drives the eccentric rotor 32' to rotate in the inner cavity of the cylinder, so that gas is compressed. When the gas in the cylinder cavity reaches the preset pressure, the gas is exhausted out of the compressor pump body from the exhaust valve 61 'in the auxiliary bearing 6'. In the prior art, the eccentric rotor 32' of the compressor has a single function, only used for compressing gas, and has no functions of exhausting gas, intaking gas, etc., so that the structure of the compressor is relatively complex, for example, an exhaust valve 61' and an exhaust valve seat, etc. need to be arranged, the cost of the compressor is high, and the exhaust valve 61' is easy to damage, which causes the compressor to fail.

Disclosure of Invention

Based on the defects of the prior art, the invention provides a multifunctional compressor rotor, a compressor pump body, a compressor and a temperature adjusting system.

The embodiment of the invention provides a compressor rotor, which comprises a rotating shaft and an eccentric rotor connected with the rotating shaft, wherein the rotating shaft is used for driving the eccentric rotor to rotate, the rotating shaft is eccentrically arranged on the eccentric rotor, the eccentric rotor is provided with a side surface extending circumferentially around the rotating shaft and end surfaces connected with the upper end and the lower end of the side surface, the end surfaces comprise an upper end surface and a lower end surface, the upper end surface and the lower end surface are parallel, 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 coaxially arranged into a whole, the length of the main shaft is greater than that of the auxiliary shaft, an air guide channel is arranged on the eccentric rotor, the air guide channel comprises an air guide groove arranged on the end surface and an air guide port arranged on the side surface, and the air guide port is communicated with the air guide groove.

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, an oil guide channel is provided in the rotating shaft, an oil outlet communicated with the oil guide channel is provided on a side surface of the rotating shaft, an oil guide groove with an open top is provided on an upper end surface of the eccentric rotor, the oil guide groove includes an oil guide starting section and an oil guide diffusion section, a first end of the oil guide starting section faces the rotating shaft and is communicated with the oil outlet, a second end of the oil guide starting section is connected with a first end of the oil guide diffusion section, and the oil guide diffusion section is bent with respect to the oil guide starting section and extends in the circumferential direction of the eccentric rotor.

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, first cavities are respectively formed on two sides of the bus, a first reinforcing rib is formed between adjacent first cavities, and the oil guide groove is opened on the first reinforcing rib.

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, and an included angle of 1-20 degrees is formed between the connecting line from the center of the rotating shaft to the center of the air guide port and the bus.

As a further improvement of the above embodiment, on the cross section of the core-shifted rotor, a connection 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, 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 at two sides of the bus, a second reinforcing rib extending along the bus is formed between the two second cavities, and the air guide groove is opened on the second reinforcing rib.

As a further improvement of the above embodiment, the second cavities on both sides of the bus bar are communicated through auxiliary channels opened on the second reinforcing ribs.

As a further improvement of the above embodiment, the auxiliary channel is a conduction groove opened on an end surface of the core-shifted rotor, and the auxiliary channel is located on an end surface same as the air guide groove or on another end surface 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 cross section of the eccentric rotor is egg-shaped, and has an egg head end and an egg tail end, 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, and the air guide grooves extend from the periphery of the rotating shaft to the egg tail end.

The compressor rotor according to any one of the embodiments of the present invention is configured in such a manner that the eccentric rotor is accommodated in the cylinder cavity, the air guide port is communicated with the cylinder cavity, two ends of the rotating shaft respectively protrude from end surfaces of the eccentric rotor and are respectively in rotational fit with the main bearing and the auxiliary bearing, the slide sheet is movably installed in the cylinder and is in movable fit with the eccentric rotor to partition the cylinder cavity, and the eccentric rotor is driven by the rotating shaft to rotate relative to the cylinder, the main bearing and the auxiliary bearing.

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, an air supply channel is further formed in the main bearing or the auxiliary bearing, when the compressor pump body is in an air suction state, the air supply channel is communicated with the air guide channel, and the compressor pump body supplies air to the inner cavity of the air cylinder through the air supply channel and the air guide channel.

As a further improvement of the above embodiment, a first shaft hole is formed in the secondary bearing, the rotating shaft is inserted into the first shaft hole and is in running fit with the secondary bearing, the exhaust channel and the air supply channel are both arranged on the secondary bearing, the exhaust channel comprises an exhaust groove and an exhaust pipeline communicated with the exhaust groove, the air supply channel comprises an air supply groove and an air supply pipeline communicated with the air supply groove, the exhaust groove and the air supply groove are both arc-shaped and extend along the circumferential direction of the first shaft hole, the exhaust groove and the air supply groove surround the first shaft hole and are arranged at opposite intervals, when the eccentric rotor rotates to the compression position, the air guide channel is communicated with the exhaust groove and is not communicated with the air supply groove, compressed air in the cylinder cavity is discharged outwards through the air guide port, the air guide groove, the exhaust groove and the exhaust pipeline, when the eccentric rotor rotates to the air suction position, the air guide channel is communicated with the air supply groove and is not communicated with the exhaust groove, and the compressor pump body, the air supply pump body, the air guide channel, the air supply port and the air supply pump body sequentially pass through the air supply channel and the air supply port in the cylinder cavity.

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 the 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 disposed between the outer wall of the cylinder body and the inner wall of the cylinder body, the separation reinforcing rib and 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 disposed on the separation reinforcing rib, and a cross-sectional area of a flow channel of the separation channel is smaller than a cross-sectional area of a 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, the flow passage sectional area of the sub-separation chamber is: flow passage sectional area of the separation passage: the ratio of the flow passage sectional areas of the total exhaust port is: 3-30:1-1.8:1.

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.

As a further improvement of the above embodiment, the cylinder is further provided with a slide sheet groove communicated with the cylinder inner cavity, the slide sheet is movably installed in the slide sheet groove and can extend out of or retract into the slide sheet groove, and the tail end of the slide sheet is in rolling fit or sliding fit with the side surface of the eccentric rotor to separate the cylinder inner cavity.

As a further improvement of the above embodiment, a second cavity is formed in the eccentric rotor, a transition channel is formed in the main bearing and/or the auxiliary bearing, the transition channel is communicated with the second cavity and the air guide groove at the same time when the eccentric rotor rotates to a position between the exhaust end position and the zero line, the clearance compressed air in the cylinder cavity sequentially passes through the air guide port, the air guide groove and the transition channel and enters the second cavity, the transition channel is not communicated with the second cavity and the air guide groove at the same time when the eccentric rotor rotates to a position between the zero line and the intake end position, the transition channel is communicated with the air guide groove and the second cavity simultaneously when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position, and the air in the second cavity sequentially passes through the transition channel, the air guide groove and the air guide port and enters the cylinder cavity.

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

As a further improvement of the above embodiment, the rotation angle corresponding to 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.

In another aspect, an embodiment of the present invention provides a compressor, which includes a compressor housing, a driving assembly, and the compressor pump body according to any of the above embodiments, where the driving assembly and the compressor pump body are both disposed in the compressor housing, and the driving assembly is located on a side of the main bearing away from the cylinder, and is connected to the rotating shaft, and is used to drive 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 the 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 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.

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.

As a further improvement of the above embodiment, the oil discharge assembly further includes a first oil passing channel and a second oil passing channel, the first oil passing channel is opened on the auxiliary bearing, an inlet of the first oil passing channel is communicated with the gas-liquid separation cavity, and oil is guided from the gas-liquid separation cavity to an inlet of the gap channel; the oil passing channel II is communicated with an outlet of the gap channel and the oil pool, and oil is led into the oil pool from the outlet of the gap channel; and the oil in the gas-liquid separation cavity sequentially passes through the oil passage I, the gap passage and the oil passage II and is discharged to the oil pool.

As a further improvement of the above embodiment, the width of the gap channel is 0.001mm to 0.020mm, the mandrel mounting seat is provided with an inner hole, the mandrel is assembled in the inner hole of the mandrel mounting seat, and the first oil passage and/or the second oil passage are distributed with the mandrel in a staggered manner, so that the mandrel can be limited in the inner hole.

As a further improvement of the above embodiment, the oil discharge assembly further includes a filtering structure, an oil discharge hole is formed in the gas-liquid separation cavity, the first oil passing channel is arranged on the auxiliary bearing, the filtering structure is arranged in the oil discharge hole or between the oil discharge hole and the first oil passing channel, an inlet of the first oil passing channel is communicated with an outlet of the filtering structure, a magnetic block is arranged in the filtering structure, and a filtering pore size of the filtering structure is smaller than 0.005mm.

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 compressor further includes an oil supply device, the oil supply device is connected to the oil sump and is configured to deliver oil of the oil sump to the cylinder, and the oil supply device is also disposed in the compressor housing and is located below the auxiliary bearing.

The embodiment of the invention also provides a temperature adjusting system, which comprises the compressor, an evaporator and a condenser, wherein a refrigerant circularly flows among the compressor, the evaporator and the condenser.

As a further improvement of the above embodiment, the refrigerant is a carbon dioxide refrigerant.

According to the compressor rotor, the compressor pump body, the compressor and the temperature adjusting system, the air guide channel is arranged on the compressor rotor, so that compressed air in the inner cavity of the air cylinder can be discharged out of the air cylinder through the compressor rotor, and the structure of the compressor is simpler and more reliable.

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 size, emphasis instead being placed upon illustrating the subject matter.

Fig. 1 is a schematic structural view of a compressor in the prior art.

Fig. 2 is a schematic structural diagram of a compressor according to an embodiment of the present invention.

Fig. 3 and 4 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. 5 to 10 are schematic structural views of a compressor rotor according to an embodiment of the present invention.

Fig. 11 is a schematic structural view of the sub-bearing in fig. 3.

Fig. 12 and 13 are a partial exploded view and an assembled view of a pump body of a compressor according to another embodiment of the present invention.

Fig. 14 to 16 are schematic structural views of a compressor rotor according to another embodiment of the present invention.

Fig. 17 to 19 are schematic structural views of the cylinder in fig. 3.

Fig. 20 is a schematic structural view of a compressor according to another embodiment of the present invention.

Fig. 21 is a partially enlarged view of fig. 20.

Fig. 22 is a schematic structural view of a compressor rotor according to still another embodiment.

Fig. 23 is a partially enlarged view of fig. 22.

FIG. 24 is a partial schematic view of a compressor pump body having the compressor rotor of FIG. 22.

Fig. 25 is a schematic view of the structure of a sub-bearing that is correspondingly fitted to the compressor rotor of fig. 22.

Fig. 26 to 30 are schematic views of the compressor pump body of fig. 24 in various states.

FIG. 31 is a schematic representation of the compression ratio versus generatrix angle for the compressor pump body of FIG. 24.

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 as used herein are 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. 2 to 21, an embodiment of the present invention provides a compressor, which may be 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 portion 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, the rotating shaft 31 is used for driving the eccentric rotor 32 to rotate, and the rotating shaft 31 and the eccentric rotor 32 may be integrally formed or may be separately disposed. 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. 5 to 7, the eccentric rotor 32 is cylindrical, and may be cylindrical, elliptical, or the like. 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 push 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. 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 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 (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 a region 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. The rotation shaft 31 protrudes with respect to the upper end surface 3204 and the lower end surface 3203 to form the main shaft 311 and the sub shaft 312, respectively. The main shaft 311 and the sub shaft 312 are coaxially arranged integrally. 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. 8 to 10, in a further preferred embodiment, an oil guiding passage 313 is formed in the rotating shaft 31, and an oil outlet 3111 communicated with the oil guiding passage 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 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 hole 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. 9, in a further preferred embodiment, on a cross section of the core-offset rotor 32, a connecting line from a center of the rotating shaft 31 to a highest point of a 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 nearest 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 can also make the side 3202 of the eccentric rotor 32 slightly deform when the force is applied to the side 3202, so as to prevent the eccentric rotor 32 from being locked in the cylinder 4.

Referring to fig. 6 and 7, 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. 6 and 7, 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 initiation section 3211 extends along a generatrix, and the air guide connection section 3212 is bent with respect to the air guide initiation section 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. 6 and 7, 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, a second reinforcing rib 324 extending along the bus 3201 is formed between the two second cavities 323, 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 cavity 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 allow the side 3202 of the eccentric rotor 32 to deform slightly under a larger force, 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.

Referring to fig. 22 and 23, 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 form a transition air cavity together. In this embodiment, the off-center rotor 32 is egg-shaped in cross-section.

In a further preferred embodiment, the auxiliary channel 3241 is 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 the other 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. 12 to 16, in another preferred embodiment, the eccentric rotor 32 has an egg-shaped cross section having an egg-head end (i.e., an upper end in fig. 16) and an egg-tail end (i.e., a lower end in fig. 16), the egg-tail end has a smaller radius of curvature than the egg-head end, the distance from the egg-tail end to the center of the rotary shaft 31 is greater than the distance from the egg-head end to the center of the rotary shaft 31, and the air guide grooves 321 extend from the periphery of the rotary shaft 31 to the egg-tail end. Referring to fig. 16, the outline of the shaded area a is the side projection of the circular eccentric rotor 32, the outline of the shaded area a is the 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 overall volume) occupied by the egg-shaped eccentric rotor 32 is smaller than that occupied by the circular eccentric rotor 32, so the effective volume of the cylinder cavity 41 is larger.

Referring to fig. 11, 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 be opened on the inner surface of the main bearing 5 opposite to the eccentric rotor 32, and correspondingly, the air guide channel is opened on the upper end surface 3202 of the eccentric rotor 32, the operation principle is similar to that of the above 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 eccentric rotor 32, the air supplement channel 63 is opened on the secondary bearing 6, and when the air guide channel is opened on the upper end surface 3202 of the eccentric 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 formed on a 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. 22 to 25, in the present embodiment, the air guide slots 321 are arc-shaped and extend around the circumference of the auxiliary shaft 322, the air discharge slots 621 are also arc-shaped and extend along the circumference of the first shaft hole 61, and the distance from the air guide slots 321 to the center of the auxiliary shaft 322 is substantially equal to the distance from the air discharge slots 621 to the center of the first shaft hole 61. Referring to fig. 26, in the cross section of the pump body of the compressor, a line connecting the center of the rotating shaft 3 to the center of the sliding vane 7 is 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 a rotation angle of the eccentric rotor 32. When the eccentric rotor 32 rotates to 200 degrees, the compressor 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 an initial conduction position (i.e., an air discharge starting position) of the air guide channel and the air discharge channel, 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 port 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. 27, when the eccentric rotor 32 rotates to 335 degrees, the compressor body is still in a compressed state, and the air guide groove 321 and the air discharge groove 621 do not overlap (i.e. the air discharge end position), i.e. the air guide groove 321 and the air discharge groove 621 are not in conduction, and at this time, the air discharge ends. 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. 31 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 and 340 degrees.

Referring to fig. 17 to 19, 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 cylinder inner cavity 41, a gas-liquid separation cavity 43 is formed between the outer cylinder wall 421 and the inner cylinder wall 422, and the exhaust passage 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 further provided with a main exhaust port 45, and when the pump body of the compressor 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 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 the 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. 19, 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.

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 reinforcing ribs 442 arranged between the cylinder outer wall 421 and the cylinder inner wall 422, buffer channels for communicating the adjacent buffer cavities 441 are arranged on the buffer reinforcing ribs 442, and the flow channel sectional area of the buffer channels is smaller than the flow channel sectional 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. The auxiliary bearing 6 may be provided with an air inlet channel and connected with the main air inlet pipe 91, the main air inlet hole 46 may be communicated with the air inlet channel on the auxiliary bearing 6, and the low-pressure gas entering from the main air inlet pipe 91 passes through the air inlet channel on the auxiliary bearing 6 and the main air inlet hole 46 and enters the cylinder 4. 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. Because 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 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. 17 and 18, 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 mounted 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 partition the cylinder cavity 41.

Referring to fig. 20 and 21, 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 discharge assembly 94 can discharge 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 sump 8 have a gas pressure difference therebetween, and in this embodiment, the lubricating oil separated from the gas-liquid separation cavity 43 passes through the gap between the spindle 9411 and the spindle mount 9412 under the action of the gas pressure difference, and is discharged into the oil sump 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 the lubricating oil # 68 is used, the fit clearance between the spindle 9411 and the inner hole of the spindle mount 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 passage 942 is opened in the auxiliary bearing 6, and an inlet of the first oil passage 942 communicates with the gas-liquid separation chamber 43, and leads oil 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 from 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 filtering structure 944, and the filtering pore of the filtering structure 944 is 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.

Referring to fig. 22 to fig. 30, in another embodiment, the eccentric rotor 32 is provided with a second cavity 323, the auxiliary bearing 6 is provided with a transition passage 65 (fig. 25), and the transition passage 65 is located on the inner surface of the auxiliary bearing 6 and corresponds to the air guide groove 321. Specifically, 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. When the eccentric rotor 32 rotates to 200 degrees, the compressor pump body begins to discharge air through the air guide and discharge passages 62. Referring to fig. 27, 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 position between the exhaust end position and the zero line 3205 (the rotation angle is 0 degrees), a clearance is formed between the eccentric rotor 32, the cylinder inner wall 422 and the sliding piece 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. 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. 28, the core-shift 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, and the second cavity 323 neither enters nor exhausts air. The eccentric rotor 32 continues to rotate and cross the zero line 3205, when the eccentric rotor rotates to a position between an air inlet starting position (i.e. the head edge of the air inlet 48) and an air inlet ending position (i.e. the tail edge of the air inlet 48), the cylinder cavity 41 starts to intake air through the air inlet 48, the transition channel 65 is not communicated with the second cavity 323 and the air guide groove 321, and at this time, the second cavity 323 is not communicated with air inlet and air exhaust.

Referring to fig. 29, 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. 30, 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 circulation 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.

Referring to fig. 6, 7, 22 and 23, 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, second cavities 323 are respectively formed on both sides of the bus 3201, and adjacent second cavities 323 are spaced by the second reinforcing rib 324. The second cavity 323 may be integral with (i.e., the same as) the first cavity 326 described above, or may be separate from the first cavity 326. The second cavities 323 at two sides of the second reinforcing rib 324 are communicated through the auxiliary channel 3241 opened on the second reinforcing rib 324, so that the two second cavities 323 form a transition air cavity together. In this embodiment, the off-center rotor 32 is egg-shaped in cross-section.

In a further preferred embodiment, the second reinforcing rib 324 extends along the bus 3201, and the air guide groove 321 opens on the second reinforcing rib 324. The auxiliary channel 3241 is a conduction groove opened on an end surface of the core-offset 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 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.

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, 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.

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 embodiments only express specific embodiments of the invention, and the description is specific and detailed, but not construed as limiting the scope of the invention. It should be noted that various changes and modifications can be made by those skilled in the art without departing from the spirit of the invention, and these changes and modifications are all within the scope of the invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.

Claims

1. A compressor rotor comprises a rotating shaft and an eccentric rotor connected with the rotating shaft, wherein the rotating shaft is used for driving the eccentric rotor to rotate, the rotating shaft is arranged on the eccentric rotor in an eccentric mode, the eccentric rotor is provided with a side surface extending in the circumferential direction of the rotating shaft and end surfaces connected with the upper end and the lower end of the side surface, the end surfaces comprise an upper end surface and a lower end surface, the upper end surface and the lower end surface are parallel, 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 larger than that of the auxiliary shaft, the compressor rotor is characterized in that an air guide channel is arranged on the eccentric rotor, the air guide channel comprises an air guide groove arranged on the end surface and an air guide opening arranged on the side surface, and the air guide opening is communicated with the air guide groove.

2. The compressor rotor as in claim 1, wherein the eccentric rotor has an eccentric portion away from the rotating shaft, 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.

3. The compressor rotor according to claim 2, wherein an oil guiding channel is formed in the rotating shaft, an oil outlet hole is formed in a side surface of the rotating shaft and is communicated with the oil guiding channel, an oil guiding groove with an open top is formed in an upper end surface of the eccentric rotor, the oil guiding groove includes an oil guiding initial section and an oil guiding diffusion section, a first end of the oil guiding initial section faces the rotating shaft and is communicated with the oil outlet hole, a second end of the oil guiding initial section is connected with a first end of the oil guiding diffusion section, and the oil guiding diffusion section is bent with respect to the oil guiding initial section and extends in a circumferential direction of the eccentric rotor.

4. The compressor rotor 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 taken as a bus bar on the cross section of the eccentric rotor, first cavities are respectively formed on both sides of the bus bar, first reinforcing ribs are formed between adjacent first cavities, and the oil guide groove is formed in the first reinforcing ribs.

5. The compressor rotor as claimed in claim 1, wherein a line connecting the center of the rotating shaft to the highest point of the eccentric portion of the eccentric rotor is taken as a bus in the cross section of the eccentric rotor, and an included angle of 1-20 degrees is formed between the line connecting the center of the rotating shaft to the center of the air guide port and the bus.

6. The compressor rotor as claimed in claim 1, wherein, in the cross section of the eccentric rotor, a connecting 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 includes an air guide initial section and an air guide connecting section, a first end of the air guide initial section faces the rotating shaft, a second end of the air guide initial 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 initial section extends along the bus, and the air guide connecting section is bent relative to the air guide initial section.

7. The compressor rotor according to claim 1, wherein a connection line from the center of the rotation shaft to a highest point of the eccentric portion of the eccentric rotor is taken as a bus bar on a cross section of the eccentric rotor, second cavities are respectively formed on two sides of the bus bar, a second reinforcing rib extending along the bus bar is formed between the two second cavities, and the air guide groove is opened on the second reinforcing rib.

8. The compressor rotor as claimed in claim 7, wherein the second cavities on both sides of the bus bar are communicated through auxiliary channels opened on the second reinforcing ribs.

9. The compressor rotor as claimed in claim 8, wherein the auxiliary passage is a conduction groove opened on an end surface of the eccentric rotor, and the auxiliary passage is located on the same end surface as the air guide groove or on the other end surface opposite to the air guide groove; or

10. The compressor rotor as claimed in any one of claims 1 to 9, wherein the eccentric rotor has an egg-shaped cross section having an egg-head end and an egg-tail end, the egg-tail end having a smaller radius of curvature than the egg-head end, the egg-tail end being spaced apart from the center of the rotation shaft by a distance greater than the egg-head end, the air guide groove extending from the circumference of the rotation shaft toward the egg-tail end.

11. A compressor pump body, it includes the air cylinder, main bearing, secondary bearing, compressor rotor and gleitbretter, there are air cylinder cavity and air suction inlet communicating with said air cylinder cavity in the said air cylinder, said main bearing and secondary bearing are fixed on both sides of the said air cylinder respectively, seal the said air cylinder cavity, characterized by that, the said compressor rotor is the compressor rotor of any claim 1 to 6, the said eccentric rotor is held in the said air cylinder cavity, the said air guide port communicates with said air cylinder cavity, both ends of the said spindle are projected relative to the end face of the said eccentric rotor respectively, and cooperate with said main bearing and secondary bearing rotation separately, the said gleitbretter is installed in the said air cylinder movably, and cooperate with the said eccentric rotor activity, used for separating the said air cylinder cavity, the said eccentric rotor rotates relative to the said air cylinder, main bearing, secondary bearing under the drive of the said spindle.

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

13. The compressor pump body of claim 12, wherein the main bearing or the secondary bearing is further provided with an air supply channel, when the compressor pump body is in an air suction state, the air supply channel is communicated with the air guide channel, and the compressor pump body supplies air to the cylinder inner cavity through the air supply channel and the air guide channel.

14. The compressor pump body according to claim 13, wherein the sub-bearing has a first shaft hole, the shaft is inserted into the first shaft hole and rotatably engaged with the sub-bearing, the exhaust passage and the air supply passage are both disposed on the sub-bearing, the exhaust passage includes an exhaust groove and an exhaust passage communicated with the exhaust groove, the air supply passage includes an air supply groove and an air supply passage communicated with the air supply groove, the exhaust groove and the air supply groove are both arc-shaped and extend along the circumferential direction of the first shaft hole, the exhaust groove and the air supply groove surround the first shaft hole and are disposed at opposite intervals, when the eccentric rotor rotates to the compression position, the air guide passage is communicated with the exhaust groove and is not communicated with the air supply groove, compressed air in the cylinder cavity is discharged outward through the air guide port, the air guide groove, the exhaust groove and the exhaust passage, when the eccentric rotor rotates to the air suction position, the air guide passage is communicated with the air supply groove and is not communicated with the exhaust groove, and the compressor pump body sequentially passes through the air supply passage, the air supply groove and the air guide port into the cylinder cavity.

15. The compressor pump body of claim 12, wherein the cylinder includes an outer cylinder wall and an inner cylinder wall, the inner cylinder cavity is formed in the inner cylinder wall, a gas-liquid separation cavity is formed between the outer cylinder wall and the inner cylinder wall, the exhaust passage is communicated with the gas-liquid separation cavity, 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 inner cylinder cavity is exhausted out of the cylinder through the gas guide passage, the exhaust passage, the gas-liquid separation cavity and the main exhaust port.

16. The compressor pump body according to claim 15, 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, a separation passage for communicating the adjacent sub-separation chambers is provided on the separation rib, and a flow passage sectional area of the separation passage is smaller than a flow passage sectional area of the sub-separation chambers.

17. The compressor pump body of claim 16, 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.

18. The compressor pump body of claim 16, wherein the sub-separation chambers have a cross-sectional flow area of: flow passage sectional area of the separation passage: the ratio of the flow passage sectional areas of the total exhaust port is: 3-30:1-1.8:1.

19. The compressor pump body of claim 15, 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.

20. The compressor pump body of claim 11, wherein the cylinder further defines a vane slot communicating with the cylinder cavity, the vane is movably mounted in the vane slot and can extend out of or retract into the vane slot, and a tail end of the vane is in rolling or sliding engagement with a side surface of the eccentric rotor to separate the cylinder cavity.

21. The compressor pump body according to claim 11, wherein a second cavity is formed in the eccentric rotor, a transition passage is formed in the main bearing and/or the auxiliary bearing, the transition passage simultaneously communicates with the second cavity and the air guide groove when the eccentric rotor rotates to a position between an exhaust end position and a zero line, clearance compressed air in the cylinder cavity sequentially passes through the air guide port, the air guide groove and the transition passage and enters the second cavity, the transition passage does not simultaneously communicate with the second cavity and the air guide groove when the eccentric rotor rotates to a position between the zero line and an intake end position, the transition passage simultaneously communicates with the air guide groove and the second cavity when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position, and air in the second cavity sequentially passes through the transition passage, the air guide groove and the air guide port and enters the cylinder cavity.

22. The compressor pump body according to claim 21, wherein a connecting line from the center of the rotating shaft to a highest point of the eccentric portion of the eccentric rotor is taken as a bus on a 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.

23. The compressor pump body of claim 22, wherein said second reinforcing bead extends along said generatrix, and said air guide groove opens onto said second reinforcing bead;

24. The compressor pump body according to claim 12, 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.

25. A compressor comprising a compressor housing, a drive assembly and a compressor pump body according to any one of claims 11 to 24, both 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.

26. A compressor comprising a compressor housing, a drive assembly and a compressor pump body according to any one of claims 15 to 19, 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; 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.

27. The compressor of claim 26, 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 gap oil drain structure, the gap oil drain structure includes a mandrel and a mandrel mounting seat engaged with the mandrel, a gap passage is formed between the mandrel and the mandrel mounting seat, and the liquid in the gas-liquid separation chamber passes through the gap passage and is drained into the oil sump.

28. The compressor of claim 27, wherein the oil discharge assembly further comprises a first oil passing passage and a second oil passing passage, the first oil passing passage is opened on the auxiliary bearing, an inlet of the first oil passing passage is communicated with the gas-liquid separation chamber, and oil is guided from the gas-liquid separation chamber to an inlet of the clearance passage; the oil passing channel II is communicated with the outlet of the gap channel and the oil pool, and oil is guided into the oil pool from the outlet of the gap channel; and the oil in the gas-liquid separation cavity sequentially passes through the oil passage I, the gap passage and the oil passage II and is discharged to the oil pool.

29. The compressor of claim 28, wherein the width of the clearance channel is 0.001mm to 0.020mm, the mandrel seat is provided with an inner hole, the mandrel is assembled in the inner hole of the mandrel seat, and the first oil passage and/or the second oil passage are/is distributed in a staggered manner with the mandrel so as to limit the mandrel in the inner hole.

30. The compressor of claim 28, wherein the oil discharge assembly further comprises a filtering structure, an oil discharge hole is formed in the gas-liquid separation cavity, the first oil passing channel is disposed on the secondary bearing, the filtering structure is disposed in the oil discharge hole or between the oil discharge hole and the first oil passing channel, an inlet of the first oil passing channel is communicated with an outlet of the filtering structure, a magnetic block is disposed in the filtering structure, and a filtering pore size of the filtering structure is less than 0.005mm.

31. The compressor of claim 26, wherein an oil sump is further provided within the compressor housing, the oil sump being located below the secondary bearing, the compressor further comprising an oil supply connected to the oil sump for delivering oil from the oil sump into the cylinder, the oil supply also being located in the compressor housing and below the secondary bearing.

32. A temperature regulation system comprising a compressor as claimed in any one of claims 25 to 31, and further comprising an evaporator and a condenser, wherein refrigerant circulates between the compressor, the evaporator and the condenser.

33. A temperature conditioning system of claim 32, wherein the refrigerant is a carbon dioxide refrigerant.