CN113482932A - Rotary compressor and refrigeration equipment - Google Patents
Rotary compressor and refrigeration equipment Download PDFInfo
- Publication number
- CN113482932A CN113482932A CN202110973442.4A CN202110973442A CN113482932A CN 113482932 A CN113482932 A CN 113482932A CN 202110973442 A CN202110973442 A CN 202110973442A CN 113482932 A CN113482932 A CN 113482932A
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- Prior art keywords
- eccentric
- shaft
- oil
- hole
- eccentric shaft
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- 238000005057 refrigeration Methods 0.000 title abstract description 12
- 230000006835 compression Effects 0.000 claims abstract description 22
- 238000007906 compression Methods 0.000 claims abstract description 22
- 230000002093 peripheral effect Effects 0.000 claims description 10
- 239000003921 oil Substances 0.000 description 142
- 239000010687 lubricating oil Substances 0.000 description 47
- 239000000314 lubricant Substances 0.000 description 12
- 238000005461 lubrication Methods 0.000 description 7
- 230000013011 mating Effects 0.000 description 4
- 239000003507 refrigerant Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a rotary compressor and refrigeration equipment, wherein the rotary compressor comprises: the oil storage tank is arranged at the bottom of the shell; the compression assembly is arranged in the shell and provided with an auxiliary bearing and an eccentric shaft, and the eccentric shaft is provided with a shaft center hole; the auxiliary bearing is provided with an eccentric cavity, and an oil suction hole for communicating the eccentric cavity with the oil storage tank is formed in the auxiliary bearing; one end of the eccentric shaft extends into the eccentric cavity, the eccentric shaft and the eccentric cavity are eccentrically arranged, and the eccentric shaft is provided with a bypass hole for communicating the eccentric cavity and the shaft center hole; the eccentric shaft is provided with a sliding groove communicated with the outer periphery of the eccentric shaft, a sliding valve is arranged in the sliding groove, and the sliding valve rotates along with the eccentric shaft and is always abutted against the inner wall of the eccentric cavity. The invention can improve the reliability and performance of the compressor.
Description
Technical Field
The invention relates to the field of refrigeration equipment, in particular to a rotary compressor and refrigeration equipment.
Background
The amount of lubricant injected into a rotary compressor mounted in a refrigeration apparatus such as an air conditioner is determined by the displacement (cooling capacity) of the compressor, that is, the amount of refrigerant sealed in the compressor. The insufficient amount of the lubricant oil sealed into the compressor causes a failure of the compressor due to wear of the eccentric shaft of the sliding part, and the high-pressure gas leaking from the piston or the vane for compressing the refrigerant gas also increases, thereby reducing the cooling capacity of the refrigeration equipment. In a conventional screw plate pump (spray lubrication system), the oil pumping capacity varies depending on the height of the oil surface, and when the oil surface is lowered, the capacity of the compressor to suck lubricating oil into the eccentric shaft is lowered.
Disclosure of Invention
The invention mainly aims to provide a rotary compressor and refrigeration equipment, and aims to solve the problem that the oil pumping capacity of the conventional compressor is influenced by the oil level.
In order to achieve the above object, the present invention provides a rotary compressor, comprising:
the oil storage tank is arranged at the bottom of the shell; and
the compression assembly is arranged in the shell and provided with an auxiliary bearing and an eccentric shaft, and the eccentric shaft is provided with a shaft center hole;
the auxiliary bearing is provided with an eccentric cavity, and an oil suction hole for communicating the eccentric cavity with the oil storage tank is formed in the auxiliary bearing;
one end of the eccentric shaft extends into the eccentric cavity, the eccentric shaft and the eccentric cavity are eccentrically arranged, and the eccentric shaft is provided with a bypass hole for communicating the eccentric cavity and the shaft center hole;
the eccentric shaft is provided with a sliding groove communicated with the outer periphery of the eccentric shaft, a sliding valve is arranged in the sliding groove, and the sliding valve rotates along with the eccentric shaft and is always abutted against the inner wall of the eccentric cavity.
Optionally, the auxiliary bearing is provided with an oil supply cover towards one end of the oil storage tank, the oil supply cover and the auxiliary bearing are enclosed to form an oil supply cavity, the oil supply cover is provided with a connecting pipe for communicating the oil supply cavity and the oil storage tank, and the oil suction hole is communicated with the oil supply cavity.
Optionally, the oil supply cover comprises:
the connecting pipe is arranged on the bottom plate; and
one end of the connecting plate is connected with the auxiliary bearing, the other end of the connecting plate is connected with the outer periphery of the bottom plate, and the bottom plate, the connecting plate and the auxiliary bearing are enclosed to form the oil supply cavity; and peripheral holes for communicating the oil supply cavity and the oil suction hole are formed in the peripheral wall of the auxiliary bearing in the oil supply cover.
Optionally, the length direction of the sliding groove is arranged along the radial direction of the eccentric shaft, and the included angle between the length direction of the sliding groove and the axial direction of the bypass hole is not more than 90 °.
Optionally, the sliding chute has an outer end communicated with the outer periphery of the eccentric shaft and an inner end far away from the outer periphery of the eccentric shaft, and the inner end of the sliding chute is provided with an elastic member which is elastically abutted against one end of the sliding valve far away from the inner wall of the eccentric cavity.
Optionally, the surface hardness Hv of the spool valve is not less than 800.
Optionally, the compressing assembly comprises a compressing mechanism part and a motor, the motor is used for driving the eccentric shaft, the eccentric shaft is provided with an oil spitting hole communicated with the shaft center hole, and the eccentric shaft comprises a main shaft, an eccentric part and an auxiliary shaft which are connected in sequence;
the compression mechanism part comprises an air cylinder, a main shaft plate and an auxiliary shaft plate are respectively arranged at two ends of the air cylinder, a main bearing is arranged between the main shaft plate and the eccentric shaft, the auxiliary bearing is arranged between the auxiliary shaft plate and the eccentric shaft, a compression cavity is formed between the main shaft plate and the auxiliary shaft plate, and a piston for eccentric rotation and a sliding sheet abutted to the piston are arranged in the compression cavity;
the main shaft penetrates through the main bearing, the piston is sleeved on the periphery of the eccentric portion, and one end, far away from the eccentric portion, of the auxiliary shaft extends into the eccentric cavity.
Optionally, the number of the oil spitting holes is at least three; at least one oil spitting hole is communicated with the shaft center hole and the outer wall surface of the main shaft respectively, and/or at least one oil spitting hole is communicated with the shaft center hole and the outer wall surface of the eccentric shaft respectively, and/or at least one oil spitting hole is communicated with the shaft center hole and the outer wall surface of the auxiliary shaft respectively.
Optionally, the main shaft plate is provided with an oil discharge passage communicating with an inner wall surface of the main bearing.
Optionally, the main shaft is provided with a pressure equalizing hole communicating the spindle hole and the outer periphery of the main shaft.
The invention also provides a refrigerating device which comprises the rotary compressor.
The technical scheme of the invention realizes that the lubricating oil is sucked into the shaft center hole by the movement of the slide valve to supply the lubricating oil required by the eccentric shaft; the oil pumping capacity of the lubricating oil is not influenced by the change of the oil level, so that the reliability and the performance of the compressor can be improved, and the amount of the enclosed lubricating oil can be reduced.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic structural diagram illustrating an embodiment of an internal usage state of a rotary compressor according to the present invention;
FIG. 2 is a schematic structural diagram of an embodiment of a partial structure of an eccentric cavity according to the present invention;
FIG. 3 is a schematic view of the spool valve of the present invention in a rotated state;
FIG. 4 is a schematic structural view illustrating another embodiment of an internal use state of a rotary compressor according to the present invention;
FIG. 5 is a schematic structural diagram of another embodiment of a partial structure of an eccentric cavity according to the present invention.
The reference numbers illustrate:
the implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that, if directional indications (such as up, down, left, right, front, and back … …) are involved in the embodiment of the present invention, the directional indications are only used to explain the relative positional relationship between the components, the movement situation, and the like in a specific posture (as shown in the drawing), and if the specific posture is changed, the directional indications are changed accordingly.
In addition, if there is a description of "first", "second", etc. in an embodiment of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
The invention provides a rotary compressor 1, and the rotary compressor 1 can be used for refrigeration equipment such as a refrigerator. In the invention, the rotary compressor 1 comprises a shell 2 and a compression assembly arranged in the shell 2, wherein an oil storage tank 9 is arranged at the bottom of the shell 2, and the oil storage tank 9 is used for containing lubricating oil 8. The compression assembly comprises a compression mechanism part 5 and a motor 4, the motor 4 drives the compression mechanism part 5 through an eccentric shaft 30, the eccentric shaft 30 is provided with a shaft center hole 30A, the motor 4 is used for driving the eccentric shaft 30, the eccentric shaft 30 is provided with an oil spitting hole 30C communicated with the shaft center hole 30A, and the eccentric shaft 30 comprises a main shaft (not shown in the figure), an eccentric part (not shown in the figure) and an auxiliary shaft 33 which are connected in sequence; the compression mechanism part 5 comprises a cylinder 15, a main shaft plate 10 and an auxiliary shaft plate 20 are respectively arranged at two ends of the cylinder 15, a main bearing 10A is arranged between the main shaft plate 10 and the eccentric shaft 30, the auxiliary bearing 20A is arranged between the auxiliary shaft plate 20 and the eccentric shaft 30, a compression cavity 15A is formed between the main shaft plate 10 and the auxiliary shaft plate 20, and a piston 16 which eccentrically rotates and a sliding vane 18 which is abutted to the piston 16 are arranged in the compression cavity 15A; the oil spouting hole 30C communicates the axial hole 30A and an outer peripheral edge of the eccentric shaft 30, which is an outer surface of the eccentric shaft 30, for supplying oil to at least one of components that are engaged with the main shaft, the eccentric portion, and the auxiliary shaft 33. Fig. 1 to 5 are corresponding drawings of an embodiment of the present invention.
Referring to fig. 1 and fig. 2, in an embodiment, the auxiliary bearing 20A has an eccentric cavity 25, an oil suction hole 25A communicating the eccentric cavity 25 and the oil storage tank 9 is disposed on the auxiliary bearing 20A, and the oil suction hole 25A is located below an oil level of the oil storage tank 9; the eccentric cavity 25 is formed at an end of the sub-bearing 20A remote from the motor 4, i.e., a lower end of the sub-bearing 20A in fig. 1. The oil suction hole 25A is used for allowing the lubricating oil 8 in the oil storage tank 9 to enter the eccentric cavity 25. The oil suction hole 25A may be a through hole radially disposed along the secondary bearing 20A.
One end of the eccentric shaft 30 extends into the eccentric cavity 25, the eccentric shaft 30 and the eccentric cavity 25 are eccentrically arranged, and the eccentric shaft 30 is provided with a bypass hole 33C for communicating the eccentric cavity 25 and the shaft center hole 30A; the main shaft of the eccentric shaft 30 is inserted into the main bearing 10A, the piston 16 is sleeved on the periphery of the eccentric portion, and one end of the auxiliary shaft 33, which is far away from the eccentric portion, extends into the eccentric cavity 25. As shown in fig. 1, the lower end of the eccentric shaft 30 extends to the thrust plate 22, and the lower end of the auxiliary shaft 33 of the eccentric shaft 30 can relatively rotate above the thrust plate 22.
The eccentric shaft 30 is provided with a sliding groove 33A communicated with the outer periphery of the eccentric shaft, a sliding valve 33B is arranged in the sliding groove 33A, and the sliding valve 33B rotates along with the eccentric shaft 30 and is always abutted against the inner wall of the eccentric cavity 25. The slide valve 33B is capable of rotating synchronously with the eccentric shaft 30, and when the eccentric shaft 30 rotates, the slide valve 33B can revolve synchronously, and when the slide valve 33B revolves along with the eccentric shaft 30, the slide valve 33B abuts against the inner wall of the eccentric cavity 25 by a centrifugal force.
The eccentric cavity 25 is cylindrical, and the eccentric cavity 25 at the bottom of the auxiliary bearing 20A and the center of the eccentric shaft 30 are in an eccentric position. The bypass hole 33C is a radial hole provided on the peripheral side of the eccentric shaft 30, and communicates with the axial hole 30A and the eccentric cavity 25, and a slide groove 33A is formed by opening the outer periphery of the eccentric shaft 30, and a slide valve 33B is fitted into the slide groove 33A, and the slide valve 33B can slide along the slide groove 33A. When eccentric shaft 30 rotates, spool valve 33B revolves while contacting the inner wall of eccentric chamber 25, and the inner volume of eccentric chamber 25 changes. An oil suction hole 25A is opened in the sub-bearing 20A, and the lubricating oil 8 in the oil reservoir 9 flows into the eccentric chamber 25 through the oil suction hole 25A. Due to the revolution of the slide valve 33B, the compressed lubricating oil 8 flows into the spindle hole 30A from the bypass hole 33C, and the lubricating oil in the spindle hole 30A can be branched into the oil spouting hole 30C of the eccentric shaft 30 for lubrication with the eccentric shaft 30 and the mating parts. Since the oil suction hole 25A of the sub bearing 20A extends below the oil level of the oil reservoir 9, when the spool 33B revolves relatively, the lubricating oil 8 can be sucked into the axial hole 30A, and the lubricating oil 8 can be gradually fed upward as the eccentric shaft 30 rotates, thereby realizing continuous oil supply.
In one embodiment, when installed, the end of the secondary bearing 20A facing the oil reservoir 9 is closed; as shown in fig. 1, a thrust plate 22 is disposed at a lower end of the secondary bearing 20A, the thrust plate 22 closes an end of the secondary bearing 20A facing the oil storage tank 9, and the thrust plate 22 extends below an oil surface of the oil storage tank 9 so that the lubricating oil 8 enters the eccentric cavity 25 from the oil suction hole 25A.
As shown in fig. 1, the rotary compressor 1 includes a sealed high-pressure casing 2, a motor 4 is fixed to the casing 2, the motor 4 includes a stator 4A and a rotor 4B, a compression mechanism 5 driven by the rotor 4B of the motor 4, and a lubricant oil 8 is sealed in an oil reservoir 9 provided in the bottom of the casing 2. The oil reservoir 9 is defined as a length from the lower end surface of the cylinder 15 to the bottom surface of the housing 2. The oil surface position of the lubricating oil 8 is OL. The compression mechanism 5 is configured to: a cylinder 15 is fixed in the housing 2, the cylinder 15 includes a main shaft plate 10 and a sub shaft plate 20 fixed up and down respectively, a main bearing 10A and a sub bearing 20A are provided in the center of the main shaft plate 10 and the sub shaft plate 20, an eccentric shaft 30 includes a main shaft and a sub shaft 33 engaged with the main bearing 10A and the sub bearing 20A, the eccentric shaft 30 further includes an eccentric portion, a piston 16 eccentrically rotating in a compression cavity 15A of the cylinder 15 is driven by the eccentric portion, and the piston 16 pushes against a sliding piece 18 to reciprocate.
During operation of the compression mechanism 5, low-pressure gas sucked from the suction pipe 7 flows into the compression chamber 15A, and compressed high-pressure gas is discharged from the discharge hole formed in the main shaft plate 10 into the muffler 12, and then discharged into the lower space of the motor 4. The high-pressure gas continues to be discharged into the upper space of the motor 4, and is discharged from the discharge pipe 3 to the refrigeration cycle apparatus 6.
Referring to fig. 2, the eccentric shaft 30 is driven by the motor 4 to rotate, the sliding valve 33B in the auxiliary shaft 33 revolves around the inner circumference of the eccentric cavity 25, the eccentric cavity 25 sucks the lubricating oil 8 from the oil suction hole 25A formed in the side surface of the auxiliary bearing 20A, and the lubricating oil 8 enters the axial hole 30A through the bypass hole 33C formed in the eccentric shaft 30. The lubricating oil 8 flowing into the axial hole 30A is discharged from an oil discharge hole 30C communicating with the axial hole 30A in the eccentric shaft 30 to lubricate the outer peripheral surfaces of the sub shaft 33, the eccentric shaft 30, and the main shaft.
Referring to fig. 3, a cylindrical eccentric cavity 25 is formed at the bottom of the inner circumference of the auxiliary bearing 20A, and the eccentric cavity 25 is eccentric to the center of the auxiliary bearing 20A. The bypass hole 33C is a radial hole formed in the side surface of the eccentric shaft 30, and the bypass hole 33C communicates the eccentric cavity 25 and the axial hole 30A. The slide groove 33A may be a U-shaped groove provided on the eccentric shaft 30, an opening end of the slide groove 33A communicates with an outer periphery of the eccentric shaft 30, and the slide valve 33B is provided in the slide groove 33A to be slidable along a track formed by the slide groove 33A. When eccentric shaft 30 rotates, slide valve 33B revolves while contacting the inner wall of eccentric chamber 25, and the inner volume of eccentric chamber 25 changes.
When the counter shaft 33 rotates, the lubricating oil 8 in the oil reservoir 9 is sucked into the eccentric chamber 25 through the oil suction hole 25A formed in the outer periphery of the eccentric chamber 25, and the lubricating oil 8 flows into the axial hole 30A of the eccentric portion through the bypass hole 33C. The lubricating oil 8 flowing into the axial hole 30A flows to the upper portion of the eccentric shaft 30 and is branched into the oil discharge hole 30C to lubricate the sliding surface of the eccentric shaft 30.
Referring to fig. 3, the eccentric cavity 25 in the auxiliary bearing 20A is eccentric from the center of the auxiliary shaft 33 by an eccentric length e. A slide valve 33B is fitted into a slide groove 33A formed by opening an outer periphery of the counter shaft 33, and as shown in (1) to (2) of fig. 3, the slide valve 33B has a top dead center where θ is 0. When the bypass hole 33C is at a position where θ is 90 ° from the center of the slide valve 33B to a position where α is 35 °, the oil suction hole 25A communicates with the eccentric chamber 25. When eccentric shaft 30 rotates, slide valve 33B slides in contact with the inner wall of eccentric cavity 25 by centrifugal force.
As shown in fig. 3 (2), when the counter shaft 33 is rotated to a position where θ is 100 °, the spool 33B passes through the oil suction hole 25A to divide the eccentric chamber 25 into the a chamber and the B chamber. At this time, the a chamber expands, so that the lubricating oil 8 flows into the chamber through the oil suction hole 25A. The volume of the B chamber is reduced, and therefore the lubricating oil 8 in the B chamber flows out to the bypass hole 33C.
When the rotation of the counter shaft 33 proceeds to (3) in fig. 3, the lubricating oil 8 entering the a chamber increases, and the outflow from the B chamber to the bypass hole 33C increases. As shown in fig. 3 (4) to (6), the volume of the B chamber is reduced, the outflow of the lubricant oil 8 from the bypass hole 33C is reduced, and the inflow of the lubricant oil 8 into the a chamber is increased.
Further, as shown in fig. 3, (6) to (1) continue to rotate, the inflow of the lubricating oil 8 from the bypass hole 33C decreases, and the supply of the oil from the oil suction hole 25A to the chamber B is stopped. The oil volume in the cavity B is maximum. Alternatively, the length direction of the sliding groove 33A is arranged along the radial direction of the eccentric shaft 30, and the included angle α between the length direction of the sliding groove 33A and the axial direction of the bypass hole 33C is not more than 90 °. If α is too large, the displacement of the lubricating oil 8 is reduced, and therefore, is not more than 90 °. By the rotation of the eccentric shaft 30, the lubricating oil 8 is sucked into the eccentric cavity 25, and the sucked lubricating oil 8 is discharged to the axial hole 30A. The slide valve 33B revolving from a low speed to a high speed of 10 to 120rps is a sliding part requiring centrifugal force and abrasion resistance, and optionally, the surface hardness Hv of the slide valve 33B is not less than 800.
Compared with the conventional spray lubrication design of the lubricant oil 8, the rotary compressor 1 of the present embodiment can continue the fluid lubrication even if the amount of the lubricant oil 8 injected is reduced or the oil level varies. Compared with the conventional design using a spiral plate as an oil supply device, the oil supply amount to the eccentric shaft 30 does not change even if the Oil Level (OL) changes. Therefore, it is not necessary to inject an excessive amount of the lubricant oil 8 into the compressor, and the amount of the lubricant oil 8 injected into the casing 2 can be reduced. Since the lubrication of eccentric shaft 30 is fluid lubrication, the oil film structure of eccentric shaft 30 can be effectively improved, and the wear reliability of eccentric shaft 30 and main bearing 10A and sub bearing 20A engaged with eccentric shaft 30 is improved. Leakage of high-pressure gas from the sliding surface of the piston 16 or the like can be improved by the necessary and sufficient oil supply. When the eccentric shaft 30 is manufactured, the inner diameter of the center hole 30A of the eccentric shaft 30 can be designed to be relatively small, so that the rigidity of the eccentric shaft 30 can be improved. When the eccentric shaft 30 is used for a double-cylinder or three-cylinder compressor with a relatively long eccentric shaft, the performance of the compressor can be effectively improved. Since the amount of the lubricating oil 8 injected into the oil reservoir 9 can be reduced, the amount of the refrigerant sealed is reduced, and the environmental pollution caused by the refrigerant is reduced.
In an embodiment, the sliding groove 33A has an outer end communicating with the outer periphery of the eccentric shaft 30 and an inner end away from the outer periphery of the eccentric shaft 30, the inner end of the sliding groove 33A is provided with an elastic member (not shown in the figure) elastically abutting against an end of the sliding valve 33B away from the inner wall of the eccentric cavity 25, and the elastic member may be a plate spring for increasing the pressing force of the sliding valve 33B against the inner periphery of the eccentric cavity 25.
Referring to fig. 1 and 4, in an embodiment, the main shaft plate 10 is provided with an oil discharge passage 10b communicating with an inner wall surface of the main bearing 10A. The excessive lubricating oil 8 in the spindle hole 30A can be discharged through the oil discharge passage 10 b. The oil discharge passage 10b is for communicating with the spindle hole 30A, and a gap is provided between the oil discharge passage 30 and the bypass hole 33C so that the lubricating oil 8 can enter the oil discharge hole 30C when flowing along the spindle hole 30A. As shown in fig. 1, the oil discharge passage 10b is located above at least one of the oil discharge holes 30C, and optionally, the oil discharge passage 10b on the main shaft plate 10 may communicate with the compression chamber 15A to lubricate the sliding surface of the sliding vane 18. The oil discharge passage 10b is used for discharging the excessive lubricating oil 8 in the spindle hole 30A, so that one end of the spindle hole 30A away from the bypass hole 33C can be in a negative pressure state, and the lubricating oil 8 can be sucked into the spindle hole 30A during the rotation of the eccentric shaft 30. The oil discharge passage 10b may be provided to penetrate through the sidewall of the spindle plate 10, and may be a through hole extending in the radial direction of the spindle plate 10. The number of the oil discharge passages 10b may be plural, and the position and the sectional area of the oil discharge passage 10b may be determined according to the arrangement of the eccentric shaft 30.
In another embodiment, the main shaft is provided with a pressure equalizing hole 30B communicating the spindle hole 30A and the outer periphery of the main shaft. The pressure equalizing hole 30B communicates with the spindle hole 30A to discharge the excessive lubricating oil 8 in the spindle hole 30A, so that the inside of the spindle hole 30A is maintained in a negative pressure state. The position of the pressure equalizing hole 30B may be determined according to the arrangement of the eccentric shaft 30. Optionally, the pressure equalizing hole 30B is located above the oil spouting hole 30C, and the pressure equalizing hole 30B may be located above the main shaft plate 10, so that the upper end of the spindle hole 30A is in a negative pressure state, and further more lubricating oil 8 may be sucked into the spindle hole 30A. The pressure equalizing hole 30B may be a through hole radially disposed along the eccentric shaft 30, or may be an inclined hole. The number of the pressure equalizing holes 30B may be plural.
The main shaft plate 10 may be provided with the oil discharge passage 10B so that the excessive lubricating oil 8 flowing into the axial hole 30A can be discharged into the casing 2 from the oil discharge passage 10B and the pressure equalizing hole 30B, respectively, and join with the lubricating oil 8 in the casing 2 and flow to the oil reservoir 9.
Referring to fig. 4 and 5, in an embodiment, an oil supply cover 40 is disposed at an end of the secondary bearing 20A facing the oil storage tank 9, the oil supply cover 40 and the secondary bearing 20A enclose to form an oil supply cavity, a connection pipe 40B communicating the oil supply cavity and the oil storage tank 9 is disposed on the oil supply cover 40, and the oil suction hole 25A communicates with the oil supply cavity.
In the rotary compressor 1, the lubricating oil 8 is sucked from the lower end of the connecting pipe 40B fixed at the center of the oil feed cover 40 and the oil is fed to the eccentric chamber 25, so that the oil can be sufficiently fed to the eccentric shaft 30 even if the oil level OL is greatly lowered.
The oil supply cover 40 may be formed by shaping a flat plate having elasticity, and optionally, the oil supply cover 40 includes: the bottom plate 40A, the said joint pipe 40B locates the said bottom plate 40A; one end of the connecting plate is connected with the auxiliary bearing 20A, the other end of the connecting plate is connected with the outer periphery of the bottom plate 40A, and the bottom plate 40A, the connecting plate and the auxiliary bearing 20A enclose to form the oil supply cavity; the peripheral wall of the auxiliary bearing 20A in the oil supply cover 40 is provided with an outer peripheral hole 22A communicating the oil supply chamber and the oil suction hole 25A. The connecting plate is substantially annular, and the outer periphery thereof is fixed to the sub-bearing 20A by a screw 2 b. An oil supply chamber in which the lubricating oil 8 flows is formed between the bottom plate 40A of the oil supply cover 40 and the thrust plate 22, and a connection pipe 40B is provided in the bottom plate 40A, and one end of the connection pipe 40B remote from the bottom plate 40A extends below the oil surface of the oil reservoir 9.
When the motor 4 rotates the eccentric shaft 30, the slide valve 33B of the eccentric chamber 25 synchronously revolves, and the lubricant oil 8 sucked into the connecting pipe 40B enters the outer peripheral hole 22A through the oil supply chamber of the oil supply cover 40, and further starts to flow out from the oil suction hole 25A of the eccentric chamber 25 toward the eccentric chamber 25.
Optionally, the number of the oil spouting holes 30C is at least three; at least one of the oil spouting holes 30C communicates with the spindle hole 30A and the outer wall surface of the main shaft, respectively, and supplies oil to the mating surface between the main shaft and the main bearing 10A. Alternatively, at least one of the oil spouting holes 30C communicates with the axial hole 30A and the outer wall surface of the eccentric shaft 30, respectively, for supplying oil to the mating surface between the eccentric shaft 30 and the piston 16. Alternatively, at least one of the oil spouting holes 30C communicates with the axial hole 30A and the outer wall surface of the auxiliary shaft 33, respectively, for supplying oil to the mating surface between the auxiliary shaft 33 and the auxiliary bearing 20A.
In the present invention, an eccentric cavity 25 is provided at the bottom of a sub bearing 20A of a rotary compressor 1, and an end of a slide valve 33B provided on a sub shaft 33 is abutted against the inner wall of the eccentric cavity 25, so that the slide valve 33B sucks a lubricant 8 in an oil reservoir 9 into the eccentric cavity 25 when the slide valve revolves with the eccentric shaft, and the lubricant 8 entering the eccentric cavity 25 is sucked into an axial hole 30A of an eccentric shaft 30, thereby supplying oil to an oil discharge hole 30C. Because the oil suction hole 25A is arranged below the oil level OL of the lubricating oil 8, the redundant lubricating oil 8 can be output through the oil discharge channel 10B and the pressure equalizing hole 30B, the eccentric shaft 25 is lubricated by the lubricating oil 8, meanwhile, the redundant lubricating oil 8 is added for circulation again, the using amount of the lubricating oil 8 is reduced, the lubricating oil 8 does not need to be excessively injected into the oil storage tank 9, and the using amount of the lubricating oil 8 can be reduced. Through the arrangement, the inner diameter of the shaft center hole 30A can be effectively reduced, so that the strength of the eccentric shaft 30 can be improved, and the safety of the rotary compressor 1 is improved.
The present invention further provides an embodiment of a refrigeration device, which may be a refrigerator or an air conditioner, on the basis of the rotary compressor 1, and the refrigeration device includes the rotary compressor according to any of the above embodiments. By adopting the rotary compressor 1, the utilization rate of the lubricating oil 8 can be improved, the amount of the lubricating oil 8 sealed in the shell 2 can be reduced, the lubrication of the assembly surface of the eccentric shaft 30 of the rotary compressor 1 can be realized, and the running noise of the rotary compressor 1 can be effectively reduced.
The above description is only an alternative embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (11)
1. A rotary compressor comprising:
the oil storage tank is arranged at the bottom of the shell; and
the compression assembly is arranged in the shell and provided with an auxiliary bearing and an eccentric shaft, and the eccentric shaft is provided with an axial hole;
one end of the eccentric shaft extends into the eccentric cavity, the eccentric shaft and the eccentric cavity are eccentrically arranged, and the eccentric shaft is provided with a bypass hole for communicating the eccentric cavity and the shaft center hole;
the eccentric shaft is provided with a sliding groove communicated with the outer periphery of the eccentric shaft, a sliding valve is arranged in the sliding groove, and the sliding valve rotates along with the eccentric shaft and is always abutted against the inner wall of the eccentric cavity.
2. The rotary compressor of claim 1, wherein an oil supply cover is disposed at an end of the auxiliary bearing facing the oil storage tank, the oil supply cover and the auxiliary bearing enclose to form an oil supply chamber, a connection pipe is disposed on the oil supply cover to connect the oil supply chamber and the oil storage tank, and the oil suction hole is communicated with the oil supply chamber.
3. The rotary compressor of claim 2, wherein the oil supply cover comprises:
the connecting pipe is arranged on the bottom plate; and
one end of the connecting plate is connected with the auxiliary bearing, the other end of the connecting plate is connected with the outer periphery of the bottom plate, and the bottom plate, the connecting plate and the auxiliary bearing are enclosed to form the oil supply cavity; and peripheral holes for communicating the oil supply cavity and the oil suction hole are formed in the peripheral wall of the auxiliary bearing in the oil supply cover.
4. The rotary compressor of claim 1, wherein a length direction of the sliding groove is disposed in a radial direction of the eccentric shaft, and an angle between the length direction of the sliding groove and an axial direction of the bypass hole is not more than 90 °.
5. The rotary compressor of claim 1, wherein the sliding groove has an outer end communicating with the outer circumference of the eccentric shaft and an inner end distant from the outer circumference of the eccentric shaft, and the inner end of the sliding groove is provided with an elastic member elastically abutting on an end of the sliding valve distant from the inner wall of the eccentric chamber.
6. The rotary compressor of claim 1, wherein the slide valve has a surface hardness Hv of not less than 800.
7. The rotary compressor of any one of claims 1 to 6, wherein the compressing assembly comprises a compressing mechanism part and a motor for driving the eccentric shaft, the eccentric shaft being provided with an oil spouting hole communicating with the shaft center hole, the eccentric shaft comprising a main shaft, an eccentric part and a sub shaft connected in sequence;
the compression mechanism part comprises an air cylinder, a main shaft plate and an auxiliary shaft plate are respectively arranged at two ends of the air cylinder, a main bearing is arranged between the main shaft plate and the eccentric shaft, the auxiliary bearing is arranged between the auxiliary shaft plate and the eccentric shaft, a compression cavity is formed between the main shaft plate and the auxiliary shaft plate, and a piston for eccentric rotation and a sliding sheet abutted to the piston are arranged in the compression cavity;
the main shaft penetrates through the main bearing, the piston is sleeved on the periphery of the eccentric portion, and one end, far away from the eccentric portion, of the auxiliary shaft extends into the eccentric cavity.
8. The rotary compressor of claim 7, wherein the number of the oil spouting holes is at least three; at least one oil spitting hole is communicated with the shaft center hole and the outer wall surface of the main shaft respectively, and/or at least one oil spitting hole is communicated with the shaft center hole and the outer wall surface of the eccentric shaft respectively, and/or at least one oil spitting hole is communicated with the shaft center hole and the outer wall surface of the auxiliary shaft respectively.
9. The rotary compressor of claim 7, wherein the main shaft plate is provided with an oil discharge passage communicating with an inner wall surface of the main bearing.
10. The rotary compressor of claim 7, wherein the main shaft is provided with a pressure equalizing hole communicating the axial hole and an outer circumference of the main shaft.
11. A refrigerating apparatus comprising the rotary compressor of any one of claims 1 to 10.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110973442.4A CN113482932B (en) | 2021-08-23 | 2021-08-23 | Rotary compressor and refrigeration equipment |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110973442.4A CN113482932B (en) | 2021-08-23 | 2021-08-23 | Rotary compressor and refrigeration equipment |
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| CN113482932A true CN113482932A (en) | 2021-10-08 |
| CN113482932B CN113482932B (en) | 2023-09-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202110973442.4A Active CN113482932B (en) | 2021-08-23 | 2021-08-23 | Rotary compressor and refrigeration equipment |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113883061A (en) * | 2021-11-02 | 2022-01-04 | 珠海格力电器股份有限公司 | Silencer, compressor and air conditioner |
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| US4983108A (en) * | 1988-09-28 | 1991-01-08 | Mitsubishi Denki Kabushiki Kaisha | Low pressure container type rolling piston compressor with lubrication channel in the end plate |
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| CN113482932B (en) | 2023-09-01 |
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