CN210239993U - Oil circulating system of split type refrigeration compressor - Google Patents
Oil circulating system of split type refrigeration compressor Download PDFInfo
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- CN210239993U CN210239993U CN201921105442.7U CN201921105442U CN210239993U CN 210239993 U CN210239993 U CN 210239993U CN 201921105442 U CN201921105442 U CN 201921105442U CN 210239993 U CN210239993 U CN 210239993U
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Abstract
The utility model discloses a split type compressor's fluid circulation system belongs to compressor fluid circulation technical field, and its technical scheme main points are: the high-pressure-end compressor comprises two compressors connected in parallel, wherein the low-pressure ends of the compressors are connected with a return pipe of a refrigerant at the same time, the high-pressure ends of the compressors are connected with a condenser at the same time, an oil separator is connected between the compressors and the condenser, an oil inlet of each compressor is communicated with the oil separator at the same time, the high-pressure ends of the compressors are connected with first one-way valves, and the first one-way valves are communicated towards the oil separator. The utility model discloses a rational in infrastructure, the high-pressure end at the compressor sets up the first check valve that switches on towards oil separator, and the high-pressure gas of the compressor output of time work can not get into the compressor of shutting down to make high-pressure gas's removal be difficult for receiving the influence.
Description
Technical Field
The utility model belongs to fluid circulation technique, more specifically say, it relates to a split type compressor's fluid circulation system.
Background
In recent years, the scroll compressor gradually develops towards the direction of large cooling capacity, and can replace part of small screw compressor systems, so that parallel connection becomes an important mode for developing the large cooling capacity. Meanwhile, the parallel scroll compressor is concerned about due to the advantages of good capacity adjustability, small volume, relatively low cost, high seasonal energy efficiency and the like.
However, the high-pressure ends of the parallel compressors are simultaneously connected with the condenser, and when the parallel compressors work in batches, part of high-pressure gas output by the high-pressure end of the working compressor enters the non-working compressor, so that the high-pressure gas is deposited in the non-working compressor, the movement of lubricating oil and refrigerant is influenced, and the operation of the compressors is influenced.
Therefore, a new technical solution is needed to solve the above problems.
SUMMERY OF THE UTILITY MODEL
An it is not enough to prior art existence, the utility model aims to provide a split type compressor's fluid circulation system for when solving the compressor and opening in batches, the partial high-pressure gas of the compressor high-pressure end output of work can get into the problem in the compressor of not work.
In order to achieve the above purpose, the utility model provides a following technical scheme: the utility model provides a split type compressor's fluid circulation system, includes two parallelly connected compressors, the low-pressure end of compressor is connected with the back flow of refrigerant simultaneously, the high-pressure end of compressor is connected with the condenser simultaneously, be connected with oil separator between compressor and the condenser, the oil inlet of compressor communicates with oil separator simultaneously, the high-pressure end of compressor all is connected with first check valve, first check valve switches on towards oil separator.
By adopting the technical scheme, when the two compressors are started at intervals, the high-pressure end of the working compressor outputs the compressed gas mixed with the refrigerant and the lubricating oil, and the stopped compressor utilizes the first one-way valve connected with the stopped compressor to prevent the compressed gas from entering the inner cavity of the stopped compressor, so that the compressed gas can normally move towards the phase-oil separator, cannot be deposited in the stopped compressor, and cannot influence the movement of the refrigerant and the lubricating oil.
The utility model discloses further set up to: oil inlets of the two compressors are connected with an oil pump together.
Through adopting above-mentioned technical scheme, utilize the gear pump to provide the stable lubricating oil of pressure to the compressor to the work of compressor can not receive the influence in the time.
The utility model discloses further set up to: and oil inlets of the compressors are connected with throttle valves.
Through adopting above-mentioned technical scheme, utilize the choke valve to make the pressure that gets into the lubricating oil in the compressor remain stable, make the pressure of lubricating oil can not too high to make the normal use of compressor can not receive the influence.
The utility model discloses further set up to: an oil outlet of the oil pump is connected with an overflow valve, and an oil outlet of the overflow valve is connected with the oil separator.
By adopting the technical scheme, the pressure between the throttle valve and the oil pump is kept stable by utilizing the overflow valve, and the condition that the oil way is damaged due to overhigh pressure can not occur.
The utility model discloses further set up to: and a first pneumatic control reversing valve for opening and closing the oil inlet of the compressor is arranged between the throttling valve and the oil inlet of the compressor, the control port of the first pneumatic control reversing valve is connected with the high-pressure end of the adjacent compressor, and the oil inlet of the compressor is opened at the initial position of the first pneumatic control reversing valve.
By adopting the technical scheme, when one compressor starts to work, the first air control reversing valve is used for controlling the oil inlet of the compressor which stops working to be closed, so that lubricating oil cannot enter the compressor which stops working, the quantity of mixed gas entering the oil separator is reduced, and the load of the oil separator is reduced.
The utility model discloses further set up to: and a steam storage box is arranged between the high-pressure end of the compressor and the control port of the first pneumatic reversing valve.
By adopting the technical scheme, the time for the compressed gas to enter the control opening of the first pneumatic reversing valve is slowed down by the arrangement of the steam storage box, so that the lubricating oil can still lubricate parts in the stopped compressor, and the compressor is not easy to damage.
The utility model discloses further set up to: the lower end of the steam storage box is connected with a steam return pipeline, one end of the steam return pipeline, far away from the steam storage box, is connected with the oil separator, a second pneumatic control reversing valve is arranged in the steam return pipeline, a control port of the second pneumatic control reversing valve is connected with a steam inlet of the steam storage box connected with the second pneumatic control reversing valve, and the steam return pipeline at the initial position of the second pneumatic control reversing valve is in a conduction state.
By adopting the technical scheme, when the working compressor stops working, the second air control check valve is opened, so that high-pressure gas in the steam storage tank flows into the oil separator, the first liquid control reversing valve connected with the compressor which does not start working is opened at the moment, lubricating oil can enter the compressor which does not start working, and the compressor is not easy to damage.
The utility model discloses further set up to: and the steam inlet of the second pneumatic control reversing valve is connected with the lower end of the steam storage box.
By adopting the technical scheme, the liquid in the steam storage tank can enter the oil separator through the steam return pipeline and cannot be accumulated in the steam storage tank.
To sum up, the utility model discloses following beneficial effect has:
1. the high-pressure end of the compressor is provided with the first one-way valve communicated towards the oil separator, so that high-pressure gas output by the working compressor cannot enter the stopped compressor, and the movement of the high-pressure gas is not easily influenced;
2. the first air-controlled check valve is utilized to seal the oil inlet of the compressor after the compressor stops working, and at the moment, lubricating oil output by the oil pump cannot enter the stopped compressor, so that the quantity of the lubricating oil entering the oil separator from the high-pressure end of the compressor is reduced, and the load of the oil separator is reduced.
Drawings
FIG. 1 is a schematic view of the circulation system of the present embodiment.
Description of the drawings: 1. a compressor; 11. a first check valve; 12. an oil pump; 13. a throttle valve; 14. an overflow valve; 15. a first pneumatically controlled directional valve; 16. a steam storage tank; 161. a steam return pipeline; 17. a second pneumatic control directional valve; 2. a return pipe; 3. a condenser; 4. an oil separator.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings.
In which like parts are designated by like reference numerals. It should be noted that the terms "front," "back," "left," "right," "upper" and "lower" used in the following description refer to directions in the drawings, and the terms "bottom" and "top," "inner" and "outer" refer to directions toward and away from, respectively, the geometric center of a particular component.
An oil circulation system of a split type refrigeration compressor, as shown in fig. 1, includes two compressors 1 connected in parallel, a low pressure end of the compressor 1 is connected to a return pipe 2 of a refrigerant, and a high pressure end thereof is connected to a condenser 3 for cooling the refrigerant. An oil separator 4 is connected between the compressor 1 and the condenser 3, and an oil inlet of the compressor 1 is simultaneously communicated with the lower end of the oil separator 4. The high pressure end of the compressor 1 is connected with a first one-way valve 11, and the first one-way valves 11 are communicated towards the phase oil separator 4. When the two compressors 1 are started at intervals, the high-pressure end of the working compressor 1 outputs compressed gas mixed by refrigerant and lubricating oil, and the stopped compressor 1 utilizes the first one-way valve 11 connected with the stopped compressor to prevent the compressed gas from entering the inner cavity of the stopped compressor, so that the compressed gas can normally move towards the phase-oil separator 4 and cannot deposit in the stopped compressor 1, and the movement of the refrigerant and the lubricating oil is not influenced.
As shown in fig. 1, since the lubricating oil in the compressor 1 flows in only by the difference between the high and low levels of the lubricating oil in the liquid separator, it is difficult to maintain a stable pressure of the hydraulic oil in the compressor 1, and it is difficult to form an oil film when the compressor 1 is impacted, which makes it easy to damage the compressor 1. Therefore, the oil inlets of the two compressors 1 are connected with an oil pump 12 together, and the oil pump 12 is a gear pump. The gear pump is used to supply the compressor 1 with lubricating oil of a stable pressure so that the operation of the compressor 1 is not affected.
As shown in fig. 1, since the pressure of the lubricant oil supplied from the gear pump is kept constant, when the operation of two compressors 1 is changed to the operation of one compressor 1, the pressure of the lubricant oil supplied into one compressor 1 is increased, and the operation of the compressor 1 is still affected. Therefore, the oil inlets of the compressor 1 are all connected with the throttle valve 13, and the other end of the throttle valve 13 is simultaneously connected with the oil outlet of the oil pump 12. The throttle valve 13 is used to keep the pressure of the lubricating oil entering the compressor 1 stable, so that the pressure of the lubricating oil is not too high, and the normal use of the compressor 1 is not affected.
As shown in fig. 1, since the amount of lubricant introduced into the compressor 1 is limited by the throttle valve 13 while the amount of lubricant discharged from the oil pump 12 is kept constant, the pressure between the relief valve 14 and the oil pump 12 is constantly increased, thereby causing damage to the oil passage. A pressure-limited overflow valve 14 is connected to the outlet of the oil pump 12, and the outlet of the overflow valve 14 is connected to the oil separator 4. The pressure between the throttle valve 13 and the oil pump 12 is kept stable by the relief valve 14, and the situation that the oil path is damaged due to overhigh pressure cannot occur.
As shown in fig. 1, since the lubricating oil is introduced into the stopped compressor 1 after the compressor 1 stops operating, and then introduced into the oil separator 4 to separate the coolant and the lubricating oil again, the load on the oil separator 4 is increased. Therefore, a first pneumatic control reversing valve 15 for opening and closing the oil inlet of the compressor 1 is arranged between the throttle valve 13 and the oil inlet of the compressor 1, a control port of the first pneumatic control reversing valve 15 is connected with a high-pressure end of the adjacent compressor 1, and the oil inlet of the compressor 1 is opened at the initial position of the first pneumatic control reversing valve 15. When one compressor 1 starts to work, the first air-operated reversing valve 15 is used for controlling the oil inlet of the compressor 1 which stops working to be closed, so that lubricating oil cannot enter the compressor 1 which stops working, the quantity of mixed gas entering the oil separator 4 is reduced, and the load of the oil separator 4 is reduced.
As shown in fig. 1, since the components on the inner wall of the compressor 1 may still operate for a while after the compressor 1 stops operating, if the supply of the lubricating oil is directly cut off, the components inside the compressor 1 may be damaged. Therefore, the steam storage box 16 is arranged between the high-pressure end of the compressor 1 and the control port of the first pneumatic reversing valve 15, the time for the compressed gas to enter the control port of the first pneumatic reversing valve 15 is reduced by the arrangement of the steam storage box 16, the lubricating oil can still lubricate parts in the stopped compressor 1, and the compressor 1 is not easy to damage.
As shown in fig. 1, when the working compressor 1 is stopped and the stopped compressor 1 is started, the control port of the first pneumatic directional control valve 15 connected to the stopped compressor 1 is still controlled by the high-pressure gas in the steam storage tank 16, so that the lubricating oil cannot be introduced into the oil inlet of the compressor 1 which is just started, and at this time, the parts inside the compressor 1 which is just started are worn. Therefore, the lower end of the steam storage tank 16 is connected with a steam return pipeline 161, and one end of the steam return pipeline 161 far away from the steam storage tank 16 is connected with the oil separator 4. The steam return pipelines 161 are all provided with a second pneumatic control reversing valve 17, a control port of the second pneumatic control reversing valve 17 is connected with an air inlet of the steam storage box 16 connected with the second pneumatic control reversing valve, and the steam return pipelines 161 of the second pneumatic control one-way valve are communicated in an initial state. At this time, when the working compressor 1 stops working, the second pneumatic control check valve is opened to enable the high-pressure gas in the steam storage tank 16 to flow into the oil separator 4, the first hydraulic control reversing valve connected with the compressor 1 which does not start working is opened at this time, and the lubricating oil can enter the compressor 1 which does not start working, so that the compressor 1 is not easily damaged.
As shown in fig. 1, as the time for the high-pressure gas to accumulate in the steam storage tank 16 increases, the heat inside the high-pressure gas is dissipated into the air, and the gas is liquefied into liquid and remains at the bottom of the steam storage tank 16. Therefore, the air inlet of the second pneumatic control reversing valve 17 is connected with the lower end of the steam storage tank 16, so that the liquid in the steam storage tank 16 can enter the oil separator 4 through the steam return pipeline 161 and can not be accumulated in the steam storage tank 16.
The working principle is as follows:
when one compressor 1 is started and one compressor 1 is closed, the high-pressure end of the compressor 1 which stops working stops discharging high-pressure gas, at the moment, a second pneumatic control reversing valve 17 connected with the compressor 1 which stops working is opened, so that the high-pressure gas in a gas storage tank 16 is discharged into an oil separator 4, at the moment, a first pneumatic control reversing valve 15 connected with the compressor 1 which starts working is opened, lubricating oil in the oil separator 4 enters the compressor 1 which starts working through an oil pump 12, the high-pressure end of the compressor 1 which starts working introduces the high-pressure gas mixed with refrigerant and lubricating oil into the oil separator 4, at the same time, the second pneumatic control reversing valve 17 connected with the compressor 1 which starts to work under the control of the high-pressure gas closes the steam return pipeline 161, the high-pressure gas enters the steam storage tank 16, after the high-pressure gas in the steam storage tank 16 is gradually increased, the pneumatic control reversing valve which stops working is controlled to be closed.
The specific embodiments are only for explaining the present invention, and it is not limited to the present invention, and those skilled in the art can make modifications of the present embodiments without inventive contribution as required after reading the present specification, but all of them are protected by patent law within the scope of the claims of the present invention.
Claims (8)
1. The utility model provides a split type compressor's fluid circulation system, includes two parallelly connected compressors (1), the low-pressure side of compressor (1) is connected with back flow (2) of refrigerant simultaneously, the high-pressure side of compressor (1) is connected its characterized in that with condenser (3) simultaneously: an oil separator (4) is connected between the compressor (1) and the condenser (3), an oil inlet of the compressor (1) is communicated with the oil separator (4), high-pressure ends of the compressor (1) are connected with first one-way valves (11), and the first one-way valves (11) are communicated towards the oil separator (4).
2. The oil circulation system of the split type refrigerating compressor according to claim 1, wherein: oil inlets of the two compressors (1) are connected with an oil pump (12) together.
3. The oil circulation system of the split type refrigerating compressor according to claim 2, wherein: and oil inlets of the compressor (1) are connected with a throttle valve (13).
4. An oil circulation system of a split type refrigerating compressor according to claim 3, wherein: an oil outlet of the oil pump (12) is connected with an overflow valve (14), and an oil outlet of the overflow valve (14) is connected with the oil separator (4).
5. An oil circulation system of a split type refrigerating compressor according to claim 3, wherein: and a first pneumatic control reversing valve (15) for opening and closing the oil inlet of the compressor (1) is arranged between the throttling valve (13) and the oil inlet of the compressor (1), a control port of the first pneumatic control reversing valve (15) is connected with a high-pressure end of the adjacent compressor (1), and the oil inlet of the compressor (1) is opened at the initial position of the first pneumatic control reversing valve (15).
6. The oil circulation system of the split type refrigerating compressor according to claim 5, wherein: and a steam storage tank (16) is arranged between the high-pressure end of the compressor (1) and the control port of the first pneumatic reversing valve (15).
7. The oil circulation system of the split type refrigerating compressor according to claim 6, wherein: the utility model discloses an oil separator, including steam storage tank (16), steam storage tank (16) lower extreme all is connected with return steam pipe way (161), the one end that steam storage tank (16) were kept away from in return steam pipe way (161) all is connected with oil separator (4), be provided with second gas accuse switching-over valve (17) in return steam pipe way (161), the control mouth of second gas accuse switching-over valve (17) is connected rather than the steam inlet of the steam storage tank (16) of connecting, initial position return steam pipe way (161) the conducting state of second gas accuse switching-over valve (17).
8. The oil circulation system of the split type refrigerating compressor according to claim 7, wherein: and the steam inlet of the second pneumatic control reversing valve (17) is connected with the lower end of the steam storage tank (16).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921105442.7U CN210239993U (en) | 2019-07-15 | 2019-07-15 | Oil circulating system of split type refrigeration compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921105442.7U CN210239993U (en) | 2019-07-15 | 2019-07-15 | Oil circulating system of split type refrigeration compressor |
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| Publication Number | Publication Date |
|---|---|
| CN210239993U true CN210239993U (en) | 2020-04-03 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921105442.7U Active CN210239993U (en) | 2019-07-15 | 2019-07-15 | Oil circulating system of split type refrigeration compressor |
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|---|---|
| CN (1) | CN210239993U (en) |
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- 2019-07-15 CN CN201921105442.7U patent/CN210239993U/en active Active
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