CN114718876B - Oil supply system and compressor - Google Patents
Oil supply system and compressor Download PDFInfo
- Publication number
- CN114718876B CN114718876B CN202110014880.8A CN202110014880A CN114718876B CN 114718876 B CN114718876 B CN 114718876B CN 202110014880 A CN202110014880 A CN 202110014880A CN 114718876 B CN114718876 B CN 114718876B
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- Prior art keywords
- oil
- compressor
- supply system
- cavity
- oil pumping
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- 238000005086 pumping Methods 0.000 claims abstract description 83
- 230000013011 mating Effects 0.000 claims description 4
- 230000000149 penetrating effect Effects 0.000 claims description 2
- 239000003921 oil Substances 0.000 abstract description 172
- 239000010687 lubricating oil Substances 0.000 abstract description 15
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- 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
- F04C29/028—Means for improving or restricting lubricant flow
-
- 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
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
-
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/809—Lubricant sump
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
The application provides an oil supply system and a compressor, wherein the oil supply system comprises: the device comprises a cylinder, an oil pool, an oil pumping piston, an oil inlet pipe, an oil outlet pipe, an oil inlet one-way valve and an oil outlet one-way valve; the oil pumping piston is arranged in the cylinder, the upper end of the oil pumping piston is communicated with the exhaust cavity through the clearance cavity, the lower end of the oil pumping piston is provided with an oil pumping working cavity, one end of the oil inlet pipe and one end of the oil outlet pipe are both communicated with the oil pumping working cavity, the other end of the oil inlet pipe is connected with the oil pool, and the other end of the oil outlet pipe is connected with a moving part of the compressor; the oil inlet one-way valve is arranged between the oil inlet pipe and the oil pumping working cavity, and the oil outlet one-way valve is arranged between the oil outlet pipe and the oil pumping working cavity. In the oil supply system and the compressor provided by the application, the pressure difference between the pressure of the exhaust cavity and the back pressure of the system is used as a power source of the oil pumping piston to push the oil pumping piston to reciprocate so as to realize the circulating flow of lubricating oil, thereby improving the oil supply capability of the oil supply system and ensuring that the upper supporting structure can be fully lubricated.
Description
Technical Field
The application relates to the technical field of compressors, in particular to an oil supply system and a compressor.
Background
The compressor is a driven fluid machine that lifts low pressure gas to high pressure gas and is the heart of the refrigeration system. Existing compressors generally include a housing and a pump body assembly and motor assembly disposed within the housing, the motor assembly including a stator and a rotor for driving the pump body assembly into operation, the pump body assembly including a cylinder and a bearing for effecting compression of a working fluid (e.g., refrigerant). The compressors may be classified into various types such as a reciprocating compressor (reciprocal compressor), a scroll compressor (scroll compressor), a rotary compressor (rotary compressor), and the like according to the pump body assembly.
Wherein, the motor assembly of rotary compressor has a bent axle, the motor assembly passes through the bent axle and transmits the rotation force of motor to the pump body part. Meanwhile, an oil pumping channel is formed in the crankshaft, an oil pumping rotary vane is arranged at the lower end of the crankshaft, and the lower end of the crankshaft is arranged below the oil surface. Under the drive of motor, bent axle and pump oily spiral vane are rotatory together, and lubricating oil is inhaled from the lower extreme of bent axle under centrifugal force effect, and along pump oily spiral vane spiral rising, then continue to rise to the top of bent axle along the pump oily passageway of bent axle, and then lubricated bearing and kinematic pair, also can play the inside refrigerated effect of compressor simultaneously.
For large-size rotary compressors, the upper end of the crankshaft is further provided with an upper supporting structure matched with the crankshaft, and the upper supporting structure is supported on the upper part of the crankshaft and used for controlling concentricity of the motor stator and the motor rotor. However, during actual use, it has been found that oil supply between the upper support structure and the crankshaft is difficult and mechanical wear is liable to occur. In addition, the compressor cannot provide larger centrifugal force during low-speed operation, so that the oil pumping capacity is insufficient, the sufficient supply of lubricating oil cannot be ensured, and further, the reliability and the energy efficiency of the compressor are adversely affected.
Disclosure of Invention
Aiming at the defects in the prior art, the application aims to provide an oil supply system and a compressor, which overcome the difficulties in the prior art, can improve the oil supply capability of the oil supply system, and can ensure the full supply of lubricating oil even for the moving parts of the high-lift part under the working condition of low rotation speed.
According to an aspect of the present application, there is provided an oil supply system including: the device comprises a cylinder, an oil pool, an oil pumping piston, an oil inlet pipe, an oil outlet pipe, an oil inlet one-way valve and an oil outlet one-way valve;
the cylinder comprises an exhaust cavity and a clearance cavity, an exhaust port is arranged at the top of the exhaust cavity, the exhaust cavity is communicated with the clearance cavity through the exhaust port, and the pressure difference between the pressure of the exhaust cavity and the clearance cavity and the back pressure outside the cylinder changes reciprocally;
the oil pumping piston is arranged in the cylinder, the upper end of the oil pumping piston is communicated with the exhaust cavity through the clearance cavity, the lower end of the oil pumping piston is provided with an oil pumping working cavity, one end of the oil inlet pipe and one end of the oil outlet pipe are communicated with the oil pumping working cavity, the other end of the oil inlet pipe is connected with the oil pool, and the other end of the oil outlet pipe is connected with a moving part of the compressor;
the oil inlet one-way valve is arranged between the oil inlet pipe and the oil pumping working cavity, and the oil outlet one-way valve is arranged between the oil outlet pipe and the oil pumping working cavity.
Optionally, in the oil supply system, the oil inlet check valve and the oil outlet check valve are both disposed at the lower end of the oil pumping piston.
Optionally, in the oil supply system, the exhaust port is a crescent structure, and the upper end of the oil pumping piston is located beside the crescent structure.
Optionally, in the oil supply system, the oil pool is disposed at a bottom of the compressor, and oil surface pressure of the oil pool is a back pressure outside the cylinder.
Optionally, in the oil supply system, the moving part of the compressor includes an upper support structure, and the upper support structure is sleeved at the upper end of the crankshaft and is used for supporting the crankshaft.
Optionally, in the oil supply system, a mating surface of the upper supporting structure and the crankshaft is an upper supporting bearing surface, and the other end of the oil outlet pipe is connected to the upper supporting bearing surface.
Optionally, in the oil supply system, an oil pumping channel is disposed in the crankshaft, and the oil pumping channel penetrates through opposite ends of the crankshaft along an up-down direction.
According to another aspect of the present application, there is provided a compressor comprising the oil supply system as described above.
Optionally, in the oil supply system, the compressor is a rotary compressor.
In the oil supply system and the compressor provided by the application, the oil pumping piston is arranged in the cylinder, and the pressure difference between the pressure of the exhaust cavity and the back pressure of the system is used as a power source of the oil pumping piston to push the oil pumping piston to reciprocate so as to realize the circulating flow of lubricating oil, so that the oil supply capability of the oil supply system of the compressor is improved, the upper supporting structure is ensured to be fully lubricated, and the reliability and the energy efficiency of the compressor are improved.
Drawings
The technical scheme of the present application will be described in detail below with reference to the accompanying drawings and specific embodiments so as to make the characteristics and advantages of the present application more apparent.
Fig. 1 is a schematic view of a compressor according to an embodiment of the present application;
FIG. 2 is an enlarged schematic view of area A of FIG. 1;
fig. 3 is a schematic structural view of a cylinder according to an embodiment of the present application.
Detailed Description
Hereinafter, embodiments of the present application will be described in detail. While the application will be described and illustrated in conjunction with certain specific embodiments, it will be understood that it is not intended to limit the application to these embodiments alone. On the contrary, the application is intended to cover modifications and equivalent arrangements included within the scope of the appended claims.
In addition, numerous specific details are set forth in the following description in order to provide a better illustration of the application. It will be understood by those skilled in the art that the present application may be practiced without these specific details. In other instances, well-known structures and components have not been described in detail in order to not obscure the present application.
The technical scheme of the present application will be described in detail below with reference to the accompanying drawings and specific embodiments so as to make the characteristics and advantages of the present application more apparent.
Please refer to fig. 1 to 3 in combination, which are schematic diagrams of a compressor according to an embodiment of the application. As shown in fig. 1 to 3, the oil supply system of the compressor 100 includes: a cylinder (reference numeral is not shown in the figure), an oil pool (not shown in the figure), an oil pumping piston 1, an oil inlet pipe 2, an oil outlet pipe 3, an oil inlet check valve 4 and an oil outlet check valve 5; the cylinder is provided with an exhaust cavity 6 and a clearance cavity 7, an exhaust port 8 is arranged at the top of the exhaust cavity 6, the exhaust cavity 6 is communicated with the clearance cavity 7 through the exhaust port 8, and the pressure difference between the pressures of the exhaust cavity 6 and the clearance cavity 7 and the back pressure outside the cylinder changes reciprocally; the oil pumping piston 1 is arranged in the cylinder, the upper end of the oil pumping piston 1 is communicated with the exhaust cavity 6 through the clearance cavity 7, the lower end of the oil pumping piston 1 is provided with an oil pumping working cavity 9, one end of the oil inlet pipe 2 and one end of the oil outlet pipe 3 are both communicated with the oil pumping working cavity 9, the other end of the oil inlet pipe 2 is connected with the oil pool, and the other end of the oil outlet pipe 3 is connected with a moving part of the compressor; the oil inlet one-way valve 4 is arranged between the oil inlet pipe 2 and the oil pumping working cavity 9, and the oil outlet one-way valve 5 is arranged between the oil outlet pipe 3 and the oil pumping working cavity 9.
Specifically, the compressor 100 includes a housing (not shown in the drawings), a motor (not shown in the drawings), a cylinder (not shown in the drawings), a crankshaft 10, a main bearing and a sub-bearing (not shown in the drawings), both of which are accommodated in the housing, the main bearing being provided at an upper end of the cylinder, the sub-bearing being provided at a lower end of the cylinder, the main bearing and the sub-bearing defining a compression space together with the cylinder and supporting the crankshaft 10, one end of the crankshaft 10 being connected to the motor, the other end of the crankshaft 10 penetrating through the main bearing into the cylinder and transmitting a rotational force of the motor to the cylinder to compress a refrigerant.
In this embodiment, the compressor 100 further includes an upper support structure 11, where the upper support structure 11 is disposed at an upper end of the crankshaft, and is used to support the crankshaft 10. The mating surface of the upper support structure 11 and the crankshaft 10 is an upper support bearing surface (reference numeral is not shown in the figure). The oil supply system of the compressor 100 comprises a cylinder, an oil pool, an oil pumping piston 1, an oil inlet pipe 2, an oil outlet pipe 3, an oil inlet check valve 4 and an oil outlet check valve 5. The cylinder is provided with an exhaust cavity 6 and a clearance cavity 7, an exhaust port 8 is arranged at the top of the exhaust cavity 6, the exhaust cavity 6 is communicated with the clearance cavity 7 through the exhaust port 8, and the exhaust port 8 is of a crescent groove structure. The oil pumping piston 1 set up in the inside of cylinder, just the upper end of oil pumping piston 1 is clearance chamber 7, the lower extreme of oil pumping piston 1 is provided with pump oil work chamber 9, promptly oil pumping piston 1 is located between clearance chamber 7 and the pump oil work chamber 9. The oil inlet pipe 2 is connected between the oil pumping working chamber 9 and the oil pool, the oil outlet pipe 3 is connected between the oil pumping working chamber 9 and moving parts of the compressor 100, and the moving parts of the compressor 100 comprise bearings (comprising a main bearing and a secondary bearing), a crankshaft 10 and an upper supporting structure 11.
With continued reference to fig. 2, the oil inlet check valve 4 and the oil outlet check valve 5 are both disposed at the lower end of the oil pumping piston 1, the oil pumping working chamber 9 is communicated with the oil inlet pipe 2 through the oil inlet check valve 4, and the oil pumping working chamber 9 is communicated with the oil outlet pipe 3 through the oil outlet check valve 5.
In the present embodiment, the upper end of the oil pumping piston 1 communicates with the exhaust chamber 6 and the clearance chamber 7, so that the pressure of the upper end of the oil pumping piston 1 changes in synchronization with the pressures of the exhaust chamber 6 and the clearance chamber 7.
In this embodiment, the oil sump is disposed at the bottom of the compressor 100, and the oil level pressure of the oil sump is the back pressure outside the cylinder (i.e., the system back pressure of the compressor 100).
In this embodiment, the oil outlet pipe 3 is connected between the oil pumping working chamber 9 and an upper supporting bearing surface at the top of the compressor 100, and the ambient pressure of the upper supporting sliding bearing is also the system back pressure of the compressor 100.
In this embodiment, the back pressure of the entire system is substantially unchanged when the compressor 100 is in operation. The gas pressure inside the cylinder (including the gas pressure inside the exhaust chamber 6 and the clearance chamber 7) will change back and forth once per revolution of the crankshaft 10. During the operation of the compressor 100, the pressure difference between the pressures inside the exhaust chamber 6 and the clearance chamber 7 and the back pressure outside the cylinder changes reciprocally, and the reciprocally changed pressure difference is used as a power source to push the oil pumping piston 1 to reciprocate, so as to realize the circulation flow of the lubricating oil.
During the initial suction phase, the gas pressure inside the discharge chamber 6 (i.e. discharge chamber pressure) is equal to the suction pressure, less than the system back pressure of the compressor 100. At this time, the gas pressure of the exhaust chamber 6 is smaller than the gas pressure of the pumping chamber 9, that is, the pressure of the lower end surface of the pumping piston 1 is greater than the pressure of the upper end surface thereof, and thus the pumping piston 1 moves upward. The oil inlet one-way valve 4 is opened, the oil outlet one-way valve 5 is closed, and lubricating oil in an oil pool flows into the oil pumping working cavity 9 through the oil inlet one-way valve 4.
As the crankshaft 10 rotates, the gas of the exhaust chamber 6 is compressed, so that the gas pressure of the exhaust chamber 6 is rapidly increased. In the exhaust phase, the gas pressure of the exhaust chamber 6 has increased to be greater than the system back pressure. At this time, the gas pressure of the exhaust chamber 6 is greater than the gas pressure of the pumping chamber 9, that is, the pressure of the upper end surface of the pumping piston 1 is greater than the pressure of the lower end surface thereof, and thus the pumping piston 1 moves downward. The oil inlet one-way valve 4 is closed, the oil outlet one-way valve 5 is opened, and lubricating oil in the oil pumping working cavity 9 is pressed into an upper supporting bearing surface through the oil outlet one-way valve 5.
Thus, the gas pressure of the exhaust chamber 6 changes from low to high once every revolution of the crankshaft 10, and the pumping piston 1 reciprocates once, thus completing one pumping cycle.
In this embodiment, the oil outlet pipe 3 is located between the upper support bearing surface of the top of the compressor 100. In other embodiments, the flowline 3 may also be connected to other moving parts of the compressor 100. Correspondingly, the lubricating oil entering the oil pumping working chamber 9 can be pressed into the matching surfaces of other moving parts through the oil outlet one-way valve 5.
Accordingly, the present embodiment also provides a compressor 100, the compressor 100 including the oil supply system as described above. Please refer to the above, and detailed description thereof is omitted herein.
In this embodiment, the compressor 100 is a rotary compressor.
In this embodiment, the oil supply system of the compressor 100 further includes a crankshaft 10, and an oil pumping channel is disposed in the crankshaft 10, and penetrates through opposite ends of the crankshaft 10 in the up-down direction.
In the existing rotary compressors, lubricating oil in an oil sump is pumped to a bearing mating surface mainly by using a pumping oil channel formed by a rotary vane inside a crankshaft. However, in some conditions, the inverter compressor is maintained at a very low operating speed for a long time, and at this time, the pumping capacity of the vane is very low, and it is difficult to obtain sufficient supply of lubricating oil for moving parts (such as sliding bearings in the upper support structure) at the high lift portion.
In the rotary compressor provided in this embodiment, since the oil pumping piston 1 is additionally arranged in the cylinder, the oil pumping piston 1 can realize reciprocating motion by using the pressure difference (the pressure difference between the pressure of the exhaust cavity and the back pressure of the system) of reciprocating change as a power source, so that the circulating flow of lubricating oil can be realized without other pressure control devices, the oil pumping capability is relatively high, and the lubricating oil can be conveyed to all moving parts of the compressor, including the moving parts of high-lift parts, thereby improving the lubricating effect of the compressor.
For example, a compressor of a certain type has a suction pressure of 1.018MPa and a back pressure of 2.862MPa. At low rotational speed (15 Hz) operating conditions, the exhaust chamber pressure in the exhaust phase is about 2.874MPa, at which time the pumping chamber 9 still has a 12000Pa pressure differential, which can provide a 1.2m oil head.
Experiments prove that the oil supply system provided by the embodiment can be used for conveying lubricating oil to the upper supporting structure 11 of the compressor 100 and meeting the lubricating requirement of an upper supporting bearing surface (namely the matching surface of the upper supporting structure and the crankshaft) under the working condition of low rotation speed.
In summary, according to the oil supply system and the compressor, the oil pumping piston is arranged in the cylinder, and the pressure difference between the pressure of the exhaust cavity and the back pressure of the system is used as a power source of the oil pumping piston to push the oil pumping piston to reciprocate so as to realize the circulating flow of lubricating oil, so that the oil supply capability of the oil supply system of the compressor is improved, the upper supporting structure is ensured to be fully lubricated, and the reliability and the energy efficiency of the compressor are improved.
The foregoing is a further detailed description of the application in connection with the preferred embodiments, and it is not intended that the application be limited to the specific embodiments described. It will be apparent to those skilled in the art that several simple deductions or substitutions may be made without departing from the spirit of the application, and these should be considered to be within the scope of the application.
Claims (9)
1. An oil supply system, comprising: the device comprises a cylinder, an oil pool, an oil pumping piston, an oil inlet pipe, an oil outlet pipe, an oil inlet one-way valve and an oil outlet one-way valve;
the cylinder comprises an exhaust cavity and a clearance cavity, an exhaust port is arranged at the top of the exhaust cavity, the exhaust cavity is communicated with the clearance cavity through the exhaust port, and the pressure difference between the pressure of the exhaust cavity and the clearance cavity and the back pressure outside the cylinder changes reciprocally;
the oil pumping piston is arranged in the cylinder, the upper end of the oil pumping piston is communicated with the exhaust cavity through the clearance cavity, the lower end of the oil pumping piston is provided with an oil pumping working cavity, one end of the oil inlet pipe and one end of the oil outlet pipe are communicated with the oil pumping working cavity, the other end of the oil inlet pipe is connected with the oil pool, and the other end of the oil outlet pipe is connected with a moving part of the compressor;
the oil inlet one-way valve is arranged between the oil inlet pipe and the oil pumping working cavity, and the oil outlet one-way valve is arranged between the oil outlet pipe and the oil pumping working cavity.
2. The oil supply system of claim 1, wherein the oil inlet check valve and the oil outlet check valve are both disposed at a lower end of the oil pumping piston.
3. The oil supply system of claim 1, wherein the exhaust port is a crescent structure and the upper end of the pumping piston is located beside the crescent structure.
4. The oil supply system according to claim 1, wherein the oil sump is provided at a bottom of the compressor, and oil surface pressure of the oil sump is back pressure outside the cylinder.
5. The oil supply system of claim 1, wherein the moving part of the compressor includes an upper support structure, which is sleeved on an upper end of the crankshaft, for supporting the crankshaft.
6. The oil supply system of claim 5, wherein the mating surface of the upper support structure and the crankshaft is an upper support bearing surface, and the other end of the oil outlet pipe is connected to the upper support bearing surface.
7. The oil supply system of claim 5, wherein an oil pumping channel is provided in the crankshaft, the oil pumping channel penetrating opposite ends of the crankshaft in an up-down direction.
8. A compressor, comprising: the oil supply system according to any one of claims 1 to 7.
9. The compressor of claim 8, wherein the compressor is a rotary compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110014880.8A CN114718876B (en) | 2021-01-06 | 2021-01-06 | Oil supply system and compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110014880.8A CN114718876B (en) | 2021-01-06 | 2021-01-06 | Oil supply system and compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114718876A CN114718876A (en) | 2022-07-08 |
| CN114718876B true CN114718876B (en) | 2023-09-26 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110014880.8A Active CN114718876B (en) | 2021-01-06 | 2021-01-06 | Oil supply system and compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114718876B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06167287A (en) * | 1992-12-01 | 1994-06-14 | Hitachi Ltd | Rotary compressor |
| CN1176348A (en) * | 1996-08-05 | 1998-03-18 | Lg电子株式会社 | Lubrication Mechanism of Hermetic Reciprocating Compressor |
| CN101158352A (en) * | 2007-11-09 | 2008-04-09 | 美的集团有限公司 | Shell low-pressure rotary compressor and control mode and application of refrigerant and oil return thereof |
| CN102996456A (en) * | 2011-09-15 | 2013-03-27 | 安徽美芝精密制造有限公司 | Rotation type compressor oil pump apparatus |
| CN108005901A (en) * | 2017-12-28 | 2018-05-08 | 广东美的制冷设备有限公司 | Low backpressure rotary compressor |
| CN110848134A (en) * | 2019-11-07 | 2020-02-28 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary machine oil pumping structure, compressor oil pumping structure and rotary compressor |
-
2021
- 2021-01-06 CN CN202110014880.8A patent/CN114718876B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06167287A (en) * | 1992-12-01 | 1994-06-14 | Hitachi Ltd | Rotary compressor |
| CN1176348A (en) * | 1996-08-05 | 1998-03-18 | Lg电子株式会社 | Lubrication Mechanism of Hermetic Reciprocating Compressor |
| CN101158352A (en) * | 2007-11-09 | 2008-04-09 | 美的集团有限公司 | Shell low-pressure rotary compressor and control mode and application of refrigerant and oil return thereof |
| CN102996456A (en) * | 2011-09-15 | 2013-03-27 | 安徽美芝精密制造有限公司 | Rotation type compressor oil pump apparatus |
| CN108005901A (en) * | 2017-12-28 | 2018-05-08 | 广东美的制冷设备有限公司 | Low backpressure rotary compressor |
| CN110848134A (en) * | 2019-11-07 | 2020-02-28 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotary machine oil pumping structure, compressor oil pumping structure and rotary compressor |
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| Publication number | Publication date |
|---|---|
| CN114718876A (en) | 2022-07-08 |
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