CN118327967B - Compressor gas bearing structure and compressor with same - Google Patents
Compressor gas bearing structure and compressor with same Download PDFInfo
- Publication number
- CN118327967B CN118327967B CN202410752285.8A CN202410752285A CN118327967B CN 118327967 B CN118327967 B CN 118327967B CN 202410752285 A CN202410752285 A CN 202410752285A CN 118327967 B CN118327967 B CN 118327967B
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- gas bearing
- gas
- piston cylinder
- compressor
- rotating shaft
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- 230000002093 peripheral effect Effects 0.000 claims description 3
- 238000005192 partition Methods 0.000 claims description 2
- 230000008093 supporting effect Effects 0.000 abstract description 16
- 238000010438 heat treatment Methods 0.000 abstract description 9
- 239000010687 lubricating oil Substances 0.000 description 15
- 238000005299 abrasion Methods 0.000 description 7
- 239000003921 oil Substances 0.000 description 6
- 238000005461 lubrication Methods 0.000 description 4
- 238000004891 communication Methods 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- 230000000903 blocking effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
- F16C32/0614—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings
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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
- F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a compressor gas bearing structure and a compressor with the same, wherein the compressor gas bearing structure comprises: a piston cylinder; a gas bearing provided at an end of the piston cylinder; the piston is rotatably arranged in the piston cylinder; and the rotating shaft is rotatably matched in the gas bearing and is connected with the piston, and the gas bearing is suitable for guiding the gas in the piston cylinder to the rotating shaft. The compressor gas bearing structure provided by the embodiment of the invention has the advantages of high supporting rigidity, long service life, space saving, capability of avoiding influencing the low-temperature heating performance of a heat pump system and the like.
Description
Technical Field
The invention relates to the technical field of compression equipment, in particular to a compressor gas bearing structure and a compressor with the same.
Background
In the rotor compressor in the related art, the rotation of the main shaft is lubricated through lubricating oil, but when the rotation speed of the compressor is greatly improved, a lubricating oil film cannot provide enough dynamic pressure supporting rigidity, the dry friction of a rotating shaft is easily caused by insufficient local oil supply, mechanical abrasion is then caused, even the condition that the rotating shaft is blocked and stopped is caused, lubricating oil is adopted for lubrication, a lubricating oil pool is required to be arranged at the bottom of the compressor, the oil pool occupies a large space, the overall height of the compressor is raised, the miniaturization difficulty of the compressor is increased, and the lubricating oil enters a refrigerant circulation pipeline and can obviously reduce the low-temperature heating performance of a heat pump system.
Disclosure of Invention
The present invention aims to solve at least one of the technical problems existing in the prior art. Therefore, the invention provides the compressor gas bearing structure which has the advantages of high supporting rigidity, long service life, space saving, capability of avoiding influencing the low-temperature heating performance of the heat pump system and the like.
The invention also provides a compressor with the compressor gas bearing structure.
To achieve the above object, an embodiment according to a first aspect of the present invention proposes a compressor gas bearing structure comprising: a piston cylinder; a gas bearing provided at an end of the piston cylinder; the piston is rotatably arranged in the piston cylinder; and the rotating shaft is rotatably matched in the gas bearing and is connected with the piston, and the gas bearing is suitable for guiding the gas in the piston cylinder to the rotating shaft.
The compressor gas bearing structure provided by the embodiment of the invention has the advantages of high supporting rigidity, long service life, space saving, capability of avoiding influencing the low-temperature heating performance of a heat pump system and the like.
In addition, the compressor gas bearing structure according to the above embodiment of the present invention may have the following additional technical features:
According to one embodiment of the invention, an air cavity is arranged in the air bearing, a radial exhaust port with one end communicated with the air cavity and the other end facing the rotating shaft is arranged on the inner peripheral wall of the air bearing, an air inlet communicated with the air cavity and the piston cylinder is arranged on the end face of the air bearing facing the piston cylinder, and an axial air gap allowing air flow to pass is arranged between the air bearing and the rotating shaft.
According to one embodiment of the invention, the gas bearing comprises a bearing flange and a muffler cover, which is arranged axially outside the bearing flange and which together with the bearing flange defines the gas chamber.
According to one embodiment of the invention, the air inlet is provided with a one-way valve allowing only air in the piston cylinder to enter the air chamber.
According to one embodiment of the invention, the compressor gas bearing structure further comprises a floating disc, the floating disc is arranged on the rotating shaft and is positioned on one side of the gas bearing away from the piston cylinder, an axial exhaust port, one end of the axial exhaust port is communicated with the gas cavity, and the other end of the axial exhaust port faces the floating disc, and a radial air gap allowing air flow to pass is arranged between the floating disc and the gas bearing.
According to one embodiment of the invention, the floating disc is provided with a diversion opening penetrating through the floating disc along the axial direction, and the diversion opening is staggered with the axial exhaust opening.
According to one embodiment of the invention, the number of the gas bearings is two and the gas bearings are respectively positioned at two ends of the piston cylinder, and the number of the floating discs is two and the gas bearings are respectively positioned at one side away from the piston cylinder.
According to one embodiment of the invention, the compressor gas bearing structure further comprises a sliding vane, a sliding vane groove is arranged in the piston cylinder, the sliding vane can be matched in the sliding vane groove in a sliding manner along the radial direction of the piston cylinder, and the sliding vane is suitable for dividing the space in the piston cylinder into a gas discharge cavity and a gas suction cavity.
According to one embodiment of the invention, the piston cylinder is provided with a flow guide channel, one end of the flow guide channel is communicated with the air cavity, the other end of the flow guide channel is communicated with the sliding vane groove towards the sliding vane, and a sliding vane air gap is arranged between the sliding vane and the sliding vane groove.
According to one embodiment of the invention, the compressor gas bearing structure further comprises a stator and a rotor connected to the shaft, the stator and the rotor being located below the piston cylinder.
An embodiment according to a second aspect of the invention proposes a compressor comprising a compressor gas bearing structure according to an embodiment of the first aspect of the invention.
According to the compressor disclosed by the embodiment of the invention, the compressor gas bearing structure disclosed by the embodiment of the first aspect of the invention has the advantages of high supporting rigidity, long service life, space saving, avoidance of influencing the low-temperature heating performance of a heat pump system and the like.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:
FIG. 1 is a cross-sectional view of a compressor gas bearing structure according to one embodiment of the present invention.
FIG. 2 is a partial cross-sectional view of a gas bearing above a compressor gas bearing structure in accordance with one embodiment of the present invention.
FIG. 3 is a partial cross-sectional view of a gas bearing below a compressor gas bearing structure in accordance with one embodiment of the present invention.
Fig. 4 is an exploded view of a compressor gas bearing structure according to one embodiment of the present invention.
FIG. 5 is a partial cross-sectional view of a compressor gas bearing structure according to one embodiment of the invention.
Fig. 6 is a schematic structural view of a piston cylinder of a compressor gas bearing structure according to one embodiment of the present invention.
FIG. 7 is a schematic view of a bearing flange of a compressor gas bearing structure according to one embodiment of the present invention.
Fig. 8 is a cross-sectional view of a compressor gas bearing structure according to another embodiment of the present invention.
Reference numerals: compressor gas bearing structure 1, piston cylinder 10, slide vane groove 11, flow guide passage 12, gas bearing 20, bearing flange 21, muffler cover 22, air chamber 23, radial exhaust port 24, air inlet 25, check valve 251, axial exhaust port 26, exhaust hole 261, exhaust gap 262, communication port 27, piston 30, rotary shaft 40, axial air gap 41, floating disc 50, flow guide port 51, radial air gap 52, slide vane 60, stator 71, rotor 72, and housing 2.
Detailed Description
The present application has been made based on the findings and knowledge of the inventors regarding the following facts and problems:
In the rotor compressor in the related art, the rotation of the main shaft is lubricated through lubricating oil, but when the rotation speed of the compressor is greatly improved, a lubricating oil film cannot provide enough dynamic pressure supporting rigidity, the dry friction of a rotating shaft is easily caused by insufficient local oil supply, mechanical abrasion is then caused, even the condition that the rotating shaft is blocked and stopped is caused, lubricating oil is adopted for lubrication, a lubricating oil pool is required to be arranged at the bottom of the compressor, the oil pool occupies a large space, the overall height of the compressor is raised, the miniaturization difficulty of the compressor is increased, and the lubricating oil enters a refrigerant circulation pipeline and can obviously reduce the low-temperature heating performance of a heat pump system.
Specifically, in the working process of the rotor compressor, a plurality of friction pairs exist, and the friction pairs mainly comprise friction between a main shaft and a flange, friction between a piston and a flange, friction sheets and friction cylinders, and mechanical abrasion and even locking shutdown are easy to occur at the positions when the rotating speed is greatly improved by adopting lubricating oil for lubrication.
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the invention.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, features defining "first", "second" may include one or more such features, either explicitly or implicitly. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
A compressor gas bearing structure 1 according to an embodiment of the present invention is described below with reference to the accompanying drawings.
As shown in fig. 1 to 8, a compressor gas bearing structure 1 according to an embodiment of the present invention includes a piston cylinder 10, a gas bearing 20, a piston 30, and a rotating shaft 40.
A gas bearing 20 is provided at the end of the piston cylinder 10. A piston 30 is rotatably provided in the piston cylinder 10. The shaft 40 is rotatably fitted in the gas bearing 20 and connected to the piston 30, the gas bearing 20 being adapted to guide the gas in the piston cylinder 10 to the shaft 40.
Specifically, when the compressor is running, the rotating shaft 40 rotates to drive the piston 30 to rotate, the piston 30 rotates in the piston cylinder 10 to compress gas, generated gas flows to the rotating shaft 40 under the guidance of the gas bearing 20, and a supporting force is formed on the rotating shaft 40 to form the gas bearing, so that the rotating shaft 40 and the gas bearing 20 cannot be in direct contact, and lubrication and supporting effects are realized.
According to the compressor gas bearing structure 1 provided by the embodiment of the invention, through arranging the gas bearing 20, the gas bearing 20 is utilized to guide the gas flow driven by the piston cylinder 10 to the rotating shaft 40 so as to support and lubricate the rotating shaft 40 by using the gas flow, compared with a mode of lubricating oil adopted in the related art, the supporting rigidity of the gas flow support is higher than that of the lubricating oil in high-speed operation, the reliability is higher, the dry friction of the rotating shaft 40 caused by insufficient local oil supply when the rotating speed of the compressor is greatly improved can be avoided, the abrasion and the blocking of the rotating shaft 40 are avoided, the service life of the compressor is prolonged, the arrangement of a bottom oil pool can be omitted, the space is saved, the whole height of the compressor is conveniently reduced, the compressor is conveniently miniaturized, and on the other hand, the lubricating oil is not required to be adopted to lubricate, the lubricating oil is not required to enter a refrigerant circulation pipeline, and the low-temperature heating performance of a heat pump system can be prevented from being reduced.
In addition, the gas bearing 20 directly adopts the gas flow driven by the piston 30 in the piston cylinder 10 as a gas source, so that the gas bearing 20 does not need to be additionally supplied with gas, the arrangement of an additional gas source and a gas path can be omitted, the integral structure of the compressor is simplified, the gas supply of the gas bearing 20 is more sufficient when the rotating speed of the compressor is higher, the supporting rigidity of the rotating shaft 40 can be further improved, and the abrasion and the blocking of the rotating shaft 40 when the rotating speed of the compressor is high are further avoided.
Therefore, the compressor gas bearing structure 1 according to the embodiment of the invention has the advantages of high supporting rigidity, long service life, space saving, avoidance of influencing the low-temperature heating performance of the heat pump system, and the like.
A compressor gas bearing structure 1 according to a specific embodiment of the present invention is described below with reference to the accompanying drawings.
In some embodiments of the present invention, as shown in fig. 1-8, a compressor gas bearing structure 1 according to an embodiment of the present invention includes a piston cylinder 10, a gas bearing 20, a piston 30, and a rotating shaft 40.
Specifically, as shown in fig. 1-3 and 8, the air chamber 23 is provided in the air bearing 20, the radial exhaust port 24 is provided on the inner peripheral wall of the air bearing 20, one end of which communicates with the air chamber 23 and the other end of which faces the rotating shaft 40, the air inlet 25 is provided on the end surface of the air bearing 20, which faces the piston cylinder 10, which communicates with the air chamber 23 and the piston cylinder 10, and an axial air gap 41 is provided between the air bearing 20 and the rotating shaft 40, which allows the air flow to pass through. Specifically, the air flow driven by the piston 30 in the cylinder 10 enters the air chamber 23 through the air inlet 25, flows to the rotary shaft 40 through the radial air outlet 24, and is then discharged from the axial air gap 41 between the rotary shaft 40 and the gas bearing 20, and enters the compressor housing 2. The air chamber 23 extends along the circumferential direction of the gas bearing 20, and the radial exhaust ports 24 are plural and arrayed along the circumferential and axial directions of the gas bearing 20. In this way, the air bearing 20 is used to guide the air flow in the piston cylinder 10 to the rotating shaft 40, so that the air flow supports the rotating shaft 40 in the radial direction to avoid the rotating shaft 40 from contacting with the air bearing 20, and lubricate the rotation between the rotating shaft 40 and the air bearing 20, and the air is buffered through the air cavity 23, so that the radial exhaust port 24 can continuously spray the air, and the rotating shaft 40 is continuously supported.
More specifically, as shown in fig. 1 to 4, 7 and 8, the gas bearing 20 includes a bearing flange 21 and a muffler cover 22, the muffler cover 22 being provided axially outside the bearing flange 21 and defining an air chamber 23 together with the bearing flange 21. The bearing flange 21 and the muffler cover 22 can be manufactured separately, facilitating the formation of the air chamber 23, the radial exhaust port 24 and the air inlet port 25, and facilitating the manufacture of the gas bearing 20.
Advantageously, as shown in fig. 2 and 4, a non-return valve 251 is provided at the inlet 25, which allows only the gas inside the piston cylinder 10 to enter the gas chamber 23. This prevents the gas in the gas chamber 23 from flowing back into the piston cylinder 10, ensuring that the gas chamber 23 is sufficiently supplied.
Fig. 1,2,4 and 8 illustrate a compressor gas bearing structure 1 according to some examples of the invention. As shown in fig. 1,2,4 and 8, the compressor gas bearing structure 1 further comprises a floating disc 50, the floating disc 50 is arranged on the rotating shaft 40 and is located on one side of the gas bearing 20 away from the piston cylinder 10, an end surface of the gas bearing 20 away from the piston cylinder 10 is provided with an axial exhaust port 26, one end of which is communicated with the air cavity 23, and the other end of which faces the floating disc 50, and a radial air gap 52 allowing air flow to pass is arranged between the floating disc 50 and the gas bearing 20. Specifically, the air flow driven by the piston 30 in the piston cylinder 10, after entering the air chamber 23 through the air inlet 25, also flows to the floating disc 50 through the axial air outlet 26 and supports the floating disc 50 in the axial direction, and then is discharged through the radial air gap 52 into the casing 2 of the compressor. This makes it possible to axially support the floating disc 50 by the air flow and lubricate the rotation between the floating disc 50 and the gas bearing 20, and also to support the rotary shaft 40 and the piston 30 to which the floating disc 50 is connected, avoiding the mutual friction between the floating disc 50 and the gas bearing 20 and also avoiding the friction between the piston 30 and the gas bearing 20 in the axial direction.
Specifically, the axial exhaust port 26 may include an exhaust hole 261 opened at the muffler cover 22 and an exhaust gap 262 formed by a gap between the bearing flange 21 and the muffler cover 22, which may each achieve guiding of the air flow to the floating disc 50. The diameter of the end of the exhaust hole 261, which communicates with the air chamber 23, is smaller than that of the end toward the floating disc 50 to enhance the supporting effect of the air flow. The exhaust holes 261 may be plural and provided at intervals along the circumferential direction of the gas bearing 20. The exhaust gap 262 extends in the circumferential direction of the gas bearing 20.
Alternatively, as shown in fig. 2 and 3, the floating disc 50 is provided with a diversion opening 51 penetrating through the floating disc 50 in the axial direction, and the diversion opening 51 is staggered from the axial exhaust opening 26. This allows the air flow to be discharged not only from the radial air gap 52 into the housing 2, but also from the air guide opening 51 into the housing 2, ensuring the air flow rate supporting the floating disc 50. The offset of the flow guide opening 51 from the axial exhaust opening 26 can prevent the air flow discharged from the axial exhaust opening 26 from directly passing through the flow guide opening 51 and not having the effect of supporting the floating disc 50.
Specifically, the gas bearings 20 are two and are located at both ends of the piston cylinder 10, respectively. In this way, the two gas bearings 20 can be used to support the rotating shaft 40, so that the stress of the rotating shaft 40 is more uniform, and the abrasion of the rotating shaft 40 is further avoided.
In some embodiments, as shown in fig. 1-4, when the floating disc 50 is one, it is arranged above the upper gas bearing 20, and the floating disc 50 is supported by the air flow to counteract the gravity of the structures such as the rotating shaft 40 and the piston 30, so as to avoid friction between the piston 30 and the gas bearing 20. Specifically, the support force to the floating disc 50 can be adjusted by adjusting the axial exhaust port 26 to avoid excessive or insufficient support force to avoid friction of the piston 30 with the upper or lower gas bearing 20.
In other embodiments, as shown in FIG. 8, the floating disc 50 is two and is located on each side of the two gas bearings 20 away from the piston cylinder 10. Thus, the floating disc 50 can be supported in two opposite directions by using the two gas bearings 20, so that two opposite supporting forces are provided for the rotating shaft 40 and the piston 30, and friction between the piston 30 and the two gas bearings 20 is avoided. This reduces the dimensional requirements for the axial exhaust port 26.
Fig. 4-6 illustrate a compressor gas bearing structure 1 according to some examples of the invention. As shown in fig. 4-6, the compressor gas bearing structure 1 further includes a vane 60, a vane groove 11 is provided in the piston cylinder 10, the vane 60 is slidably fitted in the vane groove 11 in a radial direction of the piston cylinder 10, and the vane 60 is adapted to partition a space in the piston cylinder 10 into a discharge chamber and a suction chamber. This facilitates the suction and discharge of the compressor by the rotation of the piston 30.
Specifically, as shown in fig. 5 and 6, a flow guiding channel 12 is provided on the piston cylinder 10, one end of the flow guiding channel 12 is communicated with the air cavity 23, the other end is communicated with the sliding vane groove 11 towards the sliding vane 60, and a sliding vane air gap is provided between the sliding vane 60 and the sliding vane groove 11. Specifically, the diversion channel 12 communicates with the air chamber 23 through a communication opening 27 on the bearing flange 21. The air flow in the air cavity 23 can flow to the sliding vane 60 through the flow guide channel 12 to support and lubricate the sliding vane 60, reduce the friction resistance of the sliding vane 60, slow down the abrasion of the sliding vane 60 and prolong the service life of the sliding vane 60.
Specifically, the plurality of flow guiding channels 12 are respectively located at two sides of the sliding vane 60 in the thickness direction, so that the sliding vane 60 is stressed more uniformly, and friction at two sides of the sliding vane 60 in the thickness direction is reduced. The plurality of diversion channels 12 are respectively connected with the two gas bearings 20 to ensure uniform gas supply.
Specifically, the compressor gas bearing structure 1 further includes a stator 71 and a rotor 72, the rotor 72 is connected to the rotary shaft 40, the stator 71 drives the rotor 72 to rotate by electromagnetic force, and the rotor 72 drives the rotary shaft 40 and the piston 30 to rotate.
In some embodiments, as shown in fig. 8, the stator 71 and rotor 72 are located below the piston cylinder 10. This reduces vibration caused by the rotational torque of the rotor 72 and improves the stability of the compressor.
A compressor according to an embodiment of the present invention is described below. The compressor according to the embodiment of the present invention comprises the compressor gas bearing structure 1 according to the above-described embodiment of the present invention.
The compressor according to the embodiment of the invention has the advantages of high supporting rigidity, long service life, space saving, avoiding influencing the low-temperature heating performance of the heat pump system and the like by utilizing the compressor gas bearing structure 1 according to the embodiment of the invention.
Other constructions and operations of compressors according to embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail herein.
In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the invention, the scope of which is defined by the claims and their equivalents.
Claims (9)
1. A compressor gas bearing structure, comprising:
A piston cylinder;
a gas bearing provided at an end of the piston cylinder;
the piston is rotatably arranged in the piston cylinder;
The rotating shaft is rotatably matched in the gas bearing and is connected with the piston, the gas bearing is suitable for guiding gas in the piston cylinder to the rotating shaft, the gas bearing is internally provided with a gas cavity, the inner peripheral wall of the gas bearing is provided with a radial exhaust port, one end of the radial exhaust port is communicated with the gas cavity, the other end of the radial exhaust port faces the rotating shaft, the end face, facing the piston cylinder, of the gas bearing is provided with a gas inlet, communicated with the gas cavity and the piston cylinder, and an axial air gap allowing gas flow to pass is formed between the gas bearing and the rotating shaft;
The floating disc is arranged on the rotating shaft and is positioned on one side, far away from the piston cylinder, of the gas bearing, one end, far away from the piston cylinder, of the gas bearing is provided with an axial exhaust port, the other end of the axial exhaust port is communicated with the air cavity, the other end of the axial exhaust port faces the floating disc, and a radial air gap allowing air flow to pass through is arranged between the floating disc and the gas bearing.
2. The compressor gas bearing structure of claim 1, wherein the gas bearing includes a bearing flange and a muffler cover disposed axially outward of the bearing flange and defining the gas cavity with the bearing flange.
3. A compressor gas bearing arrangement according to claim 1, wherein the gas inlet is provided with a one-way valve allowing only gas in the piston cylinder to enter the gas chamber.
4. The compressor gas bearing structure of claim 1, wherein said floating disc is provided with a flow guiding port extending axially through said floating disc, said flow guiding port being offset from said axial exhaust port.
5. The compressor gas bearing structure of claim 1, wherein said gas bearings are two and are located at opposite ends of said piston cylinder, respectively, and said floating disc is two and is located at a side of said two gas bearings remote from said piston cylinder, respectively.
6. The compressor gas bearing structure of claim 1, further comprising a slide plate, wherein a slide plate groove is provided in the piston cylinder, the slide plate being slidably fitted in the slide plate groove along a radial direction of the piston cylinder, the slide plate being adapted to partition a space in the piston cylinder into a discharge chamber and a suction chamber.
7. The compressor gas bearing structure of claim 6, wherein a flow guide channel is provided on the piston cylinder, one end of the flow guide channel is communicated with the air cavity and the other end is communicated with the slide groove towards the slide, and a slide air gap is provided between the slide and the slide groove.
8. The compressor gas bearing structure of claim 1, further comprising a stator and a rotor coupled to the shaft, the stator and the rotor being positioned below the piston cylinder.
9. A compressor comprising a compressor gas bearing arrangement according to any one of claims 1-8.
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Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194735A (en) * | 2016-08-29 | 2016-12-07 | 广东美芝制冷设备有限公司 | Rotary compressor and there is its refrigerating circulatory device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1575545A1 (en) * | 1967-06-24 | 1970-02-05 | Linde Ag | Pressurized gas lubricated slide bearing |
| JP2870749B2 (en) * | 1987-10-31 | 1999-03-17 | 株式会社島津製作所 | Air conditioner for aircraft |
| CN101440812B (en) * | 2008-12-24 | 2011-01-19 | 广东美芝制冷设备有限公司 | Lubrication apparatus of rotary compressor and control method thereof |
| JP5642297B2 (en) * | 2012-01-11 | 2014-12-17 | 三菱電機株式会社 | Vane type compressor |
| CN203756523U (en) * | 2013-11-20 | 2014-08-06 | 广东美芝制冷设备有限公司 | Rotary compressor and compression device thereof |
| CN103727032B (en) * | 2013-12-16 | 2017-02-15 | 西安交通大学 | Low-back-pressure non-lubricating-oil rolling piston type refrigeration compressor |
| KR101710350B1 (en) * | 2014-12-04 | 2017-02-27 | 광동 메이지 컴프레셔 컴퍼니 리미티드 | Low backpressure rotary compressor |
| CN105090040B (en) * | 2015-09-25 | 2018-04-17 | 珠海凌达压缩机有限公司 | Pump body structure and compressor with same |
| CN206035811U (en) * | 2016-08-29 | 2017-03-22 | 广东美芝制冷设备有限公司 | Multi -cylinder rotary compressor |
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Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194735A (en) * | 2016-08-29 | 2016-12-07 | 广东美芝制冷设备有限公司 | Rotary compressor and there is its refrigerating circulatory device |
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