CN102278837B - Oil equalization system of compressor units - Google Patents
Oil equalization system of compressor units Download PDFInfo
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- CN102278837B CN102278837B CN 201110173741 CN201110173741A CN102278837B CN 102278837 B CN102278837 B CN 102278837B CN 201110173741 CN201110173741 CN 201110173741 CN 201110173741 A CN201110173741 A CN 201110173741A CN 102278837 B CN102278837 B CN 102278837B
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- compressor
- oil
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- compressor bank
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- 239000007788 liquid Substances 0.000 claims abstract description 34
- 238000001816 cooling Methods 0.000 claims description 4
- 210000004243 sweat Anatomy 0.000 claims description 4
- 235000019628 coolness Nutrition 0.000 claims description 2
- 238000005057 refrigeration Methods 0.000 abstract description 28
- 238000001514 detection method Methods 0.000 abstract description 3
- 238000009827 uniform distribution Methods 0.000 abstract description 2
- 239000003921 oil Substances 0.000 description 85
- 230000009183 running Effects 0.000 description 7
- 239000000446 fuel Substances 0.000 description 4
- 230000007812 deficiency Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000010725 compressor oil Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 235000003642 hunger Nutrition 0.000 description 1
- 235000015927 pasta Nutrition 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 230000037351 starvation Effects 0.000 description 1
Abstract
The invention discloses an oil equalization system of compressor units. The oil equalization system comprises a multi-temperature evaporative refrigeration system formed by connecting more than two high-temperature working condition compressor units and a low-temperature working condition compressor unit in parallel; an oil return hole of an oil separator is connected with an oil return pipeline; the oil return pipeline is connected to crankcases of the high-temperature working condition compressor units through capillary tubes respectively; overflow pipes are arranged at the upper parts of the upper limits of the normal oil levels of the crankcases of the high-temperature working condition compressor units; and the overflow pipes are connected to the inlet of a gas-liquid separator of the low-temperature working condition compressor unit through capillary tubes and an electromagnetic valve. The oil equalization system has the advantages that: as long as the filling amount of refrigeration oil in the system is proper, uniform distribution of the refrigeration oil can be ensured; and any oil equalization program and any oil level detection are not needed.
Description
Technical field
The invention belongs to refrigeration technology field, relate in particular to multi-evaporation temperature, unit compressor oil equalization in parallel system.
Background technology
In the Refrigeration Technique, when adopting multiple compressors to come circulating refrigerant, owing to the equal reason of start and stop, each compressor displacement of each compressor, the inhomogeneous problem of compressor chamber refrigeration oil that can cause, thereby have the problem of the oil-poor or rich oil of certain compressor.In order to eliminate this inhomogeneous state, two kinds of solutions are arranged in the prior art, the one, adopt the oil level detection system, control the switching of return line valve according to the height of oil level in the compressor.This method can be controlled the oil level of compressor preferably, and deficiency is that cost is very high; Another kind method is that compressor adopts the oil equalizing pipe road, under the identical situation of compressor crankcase pressure, can realize the refrigeration oil uniform distribution, its deficiency be multi-evaporation temperature each compressor crankcase pressure of unit in parallel not simultaneously, just can cause refrigeration oil can more flow in the relatively low compressor of crankcase pressure.
Summary of the invention
The objective of the invention is to solve the deficiencies in the prior art, a kind of oil-balancing system of controlling simple, with low cost and reliable compressor in parallel is provided.
To achieve these goals, the present invention takes following technical scheme: a kind of compressor bank oil-balancing system, comprise the how warm sweat cooling system that is constituted by two above worst hot case compressor bank and the parallel connection of a worst cold case compressor bank, the check valve I is passed through in the worst hot case compressor bank of many temperature sweat coolings system and the exhaust of worst cold case compressor bank respectively, after check valve II and check valve III are converged, be connected to the entrance of oil eliminator, the outlet of oil eliminator is connected to the outdoor heat exchanger entrance, the outdoor heat exchanger outlet is connected to the liquid reservoir entrance, the liquid reservoir outlet divides two-way to be connected to two indoor side heat exchanger entrances by expansion valve respectively, one of them indoor side heat exchanger outlet is connected to worst hot case gas-liquid separator for compressor I entrance, another indoor side heat exchanger outlet is linked to the entrance of worst cold case gas-liquid separator for compressor II, the outlet of worst hot case gas-liquid separator for compressor I and worst cold case gas-liquid separator for compressor II is connected respectively to the air inlet of worst hot case compressor bank and worst cold case compressor bank, the spill port that it is characterized in that described oil eliminator connects return line, return line is connected to the crankcase of each worst hot case compressor bank respectively by capillary, the upper position of the normal oil level upper limit of the crankcase of each worst hot case compressor bank is provided with overflow pipe, and overflow pipe is connected to the entrance of worst cold case gas-liquid separator for compressor by capillary and magnetic valve.
A kind of compressor bank oil-balancing system of the present invention is characterized in that the normal oil level upper limit position of the crankcase of described each worst hot case compressor bank is connected by the oil equalizing pipe road.
A kind of compressor bank oil-balancing system of the present invention is characterized in that described oil eliminator is the float-ball type oil eliminator.
The principle of oil-balancing system of the present invention is: the exhaust of compressor in parallel enters into oil eliminator, when the refrigeration oil of separating reaches certain liquid level in oil eliminator, by return line and throttling capillaceous, refrigeration oil is assigned to the crankcase of each worst hot case compressor equably.
When the crankcase pressure of each high temperature compressed machine not simultaneously, oil level just can produce certain discrepancy in elevation in the crankcase.Because oil eliminator can push back each crankcase with the refrigeration oil of separating in time, so each worst hot case compressor oil-poor problem can not occur.
When the oil level of a certain worst hot case compressor arrived the height of overflow passage, refrigeration oil can overflow in the gas-liquid separator of worst cold case compressor, and then get back in the worst cold case compressor owing to the effect of pressure reduction.
The invention has the beneficial effects as follows: as long as the filling quantity of refrigeration oil is suitable in the system, just can ensure the refrigeration oil distributed uniform, and not need to move any equal oily program and carry out the detection of any oil level.
Description of drawings
The present invention has accompanying drawing 1 width of cloth,
Fig. 1 is the structural scheme of mechanism of oil-balancing system of the present invention.
In the accompanying drawing, 1-first compressor; 2-second compressor; 3-the 3rd compressor; 4-check valve I; 5-check valve II; 6-check valve III; 7-capillary I; 8-capillary II; The 9-oil eliminator; The 10-outdoor heat exchanger; The 11-liquid reservoir; 12-expansion valve I; 13-indoor side heat exchanger I; 14-gas-liquid separator I; 15-check valve IV; 16-expansion valve II; 17-indoor side heat exchanger II; 18-gas-liquid separator II; 19-capillary III; 20-capillary IV; 21-overflow passage I; 22-overflow passage II; 23-oil equalizing pipe road; The 24-return line; The 25-magnetic valve.
The specific embodiment
Describe embodiments of the invention in detail below in conjunction with accompanying drawing.
Embodiment is the refrigeration system of the multi-evaporation temperature unit in parallel of 2 worst hot case compressor bank and 1 worst cold case compressor bank formation.Wherein first compressor 1 and second compressor 2 are the worst hot case compressor, and the 3rd compressor 3 is the worst cold case compressor.After its exhaust converges through check valve I 4, check valve II 5 and check valve III 6 respectively, be connected to the entrance of oil eliminator 9.The spill port of oil eliminator 9 connects return line 24, is connected to the crankcase of first compressor 1 more respectively by capillary I 7, is connected to the crankcase of second compressor 2 by capillary II 8.And first compressor, 1 normal oil level upper limit position is connected to second compressor, 2 normal oil level upper limit positions by the oil equalizing pipe road.In the high slightly position of first compressor, the 1 normal oil level upper limit, be connected to the entrance of gas-liquid separator 18 by capillary III 19 and magnetic valve 25, equally, in the high slightly position of second compressor, the 2 normal oil level upper limits, also be connected to the porch of gas-liquid separator 18 by capillary IV 20 and magnetic valve 25.The outlet of oil eliminator 9 is connected to outdoor heat exchanger 10 entrances, outdoor heat exchanger 10 outlets are connected to liquid reservoir 11 entrances, liquid reservoir 11 outlets divide two-way respectively by expansion valve 12,16 are connected to indoor side heat exchanger 13,17 entrances, indoor side heat exchanger 13,17 outlets are connected respectively to the entrance of worst hot case gas-liquid separator for compressor I 14 and worst cold case gas-liquid separator for compressor II 18, and the outlet of worst hot case gas-liquid separator for compressor I 14 and worst cold case gas-liquid separator for compressor II 18 is connected respectively to worst hot case compressor bank 1,2 and the air inlet of worst cold case compressor bank 3.
The running of present embodiment is:
1) first compressor, 1, the second compressor 2 and the 3rd compressor 3 turn round simultaneously.
When first compressor, 1, the second compressor 2 and the 3rd compressor 3 turned round simultaneously, exhaust entered oil eliminator 9 simultaneously, and when the fuel head in the oil eliminator 9 reached the ball-cock assembly operating position, ball-cock assembly was opened.Refrigeration oil is by return line 24 and have capillary I 7 and the branch road of capillary II 8 throttlings is got back to first compressor 1 and second compressor 2.
For first compressor 1 and second compressor 2, if crankcase pressure is identical, take the lead in reaching of normal oil level upper limit position, wherein refrigeration oil can be by oil equalizing pipe road 23 to an other movement.Along with the further oil return of oil eliminator 9, first compressor 1 and second compressor 2 all can reach the normal oil level upper limit position then.When oil level continues to rise, when reaching the height of the above overflow passage 21 of oil equalizing pipe road 23 level heights and 22, refrigeration oil can move by overflow passage 21 and 22 entrances to the gas-liquid separator 18 of the 3rd compressor 3, and enters in the gas-liquid separator 18, finally gets back in the 3rd compressor 3.
For first compressor 1 and second compressor 2, if crankcase pressure difference, the mobile trend of refrigeration oil by getting back to the low relatively compressor of crankcase pressure in oil equalizing pipe road 23, is got back to the entrance of the gas-liquid separator 18 of the 3rd compressor 3 for earlier then by the overflow passage of this compressor.
2) the first compressor 1(or second compressor 2) and the 3rd compressor 3 turn round simultaneously
When supposing that first compressor 1 and the 3rd compressor 3 turn round simultaneously, the exhaust of 2 compressors enters oil eliminator 9 simultaneously, and when the fuel head in the oil eliminator 9 reached the ball-cock assembly operating position, ball-cock assembly was opened.Refrigeration oil is by return line 24 and have capillary I 7 and the branch road of capillary II 8 throttlings is got back to first compressor 1 and second compressor 2.
For first compressor 1 and second compressor 2, must be that first compressor, 1 crankcase pressure of running is low relatively.Like this, when the oil level of second compressor 2 reaches the normal oil level upper limit position, refrigeration oil can move in first compressor 1 by oil equalizing pipe road 23.Along with the oil level in first compressor 1 reaches the height of overflow passage 21, refrigeration oil can be got back to the entrance of the gas-liquid separator 18 of the 3rd compressor 3 by overflow passage 21, thereby realizes the purpose to 3 oil returns of the 3rd compressor.
When second compressor 2 and the 3rd compressor 3 turned round simultaneously, situation was with above-mentioned identical.
3) first compressor 1 and second compressor 2 stop, 3 runnings of the 3rd compressor
First compressor 1 and second compressor 2 stop, and during 3 runnings of the 3rd compressor, the exhaust of the 3rd compressor 3 enters oil eliminator 9, and when the fuel head in the oil eliminator 9 reached the ball-cock assembly operating position, ball-cock assembly was opened.Refrigeration oil is by return line 24 and have capillary I 7 and the branch road of capillary II 8 throttlings is got back to first compressor 1 and second compressor 2.
For first compressor 1 and second compressor 2, its crankcase pressure is identical, takes the lead in reaching of normal oil level upper limit position, and wherein refrigeration oil can be by oil equalizing pipe road 23 to an other movement.Along with the further oil return in oil eliminator 9 ground, first compressor 1 and second compressor 2 all can reach the normal oil level upper limit position then.When oil level continues to rise, can reach the above overflow passage 21 of oil equalizing pipe road 23 level heights and 22 height.At this moment, the crankcase pressure of first compressor 1 and second compressor 2 is suitable with the pressure of inspiration(Pi) of the 3rd compressor 3, and the entrance level height of the gas-liquid separator 18 of common the 3rd compressor can be than the level height height of overflow passage 21 and 22.Of short duration relatively high pressure is realized in first compressor 1 that the power of oil return forms in the time of will opening by each oil eliminator 9 ball-cock assemblys and second compressor, 2 crankcases, refrigeration oil is moved in the gas-liquid separator 18 by overflow passage 21 and 22, finally get back in the 3rd compressor 3.
4) the 3rd compressor 3 shuts down
1 running of first compressor or 2 runnings of second compressor, perhaps first compressor 1 and second compressor 2 turn round simultaneously, and the 3rd compressor 3 stops.Magnetic valve 25 cuts out.Exhaust enters into oil eliminator 9, and when the fuel head in the oil eliminator 9 reached the ball-cock assembly operating position, ball-cock assembly was opened.Refrigeration oil is by return line 24 and have capillary I 7 and the branch road of capillary II 8 throttlings is got back to first compressor 1 and second
Compressor 2.
If first compressor 1 is different with the crankcase pressure of second compressor 2, two compressor pastas may have certain discrepancy in elevation.Yet by the oil return constantly of oil eliminator 9, the compressor that is enough to ensure running is oil starvation not.
In addition, no matter be any in above-mentioned four kinds of situations, as long as the filling quantity of system's refrigeration oil is suitable, no matter be that any compressor is to shut down or operating condition, can both ensure the oil return equably of each compressor.Just the trend that moves of refrigeration oil is all from being high pressure one side direction low-pressure one side.
More than be illustrated with regard to an embodiment of the invention, the present invention is not limited only to this.In embodiment, the worst hot case number of compressors is not limited to two, can be any several more than two; The worst cold case number of compressors is not limited to one.
Claims (3)
1. compressor bank oil-balancing system, comprise the how warm sweat cooling system that is constituted by two above worst hot case compressor bank and the parallel connection of a worst cold case compressor bank, the worst hot case compressor bank (1 of many temperature sweat coolings system, 2) and the exhaust of worst cold case compressor bank (3) pass through check valve I (4) respectively, after check valve II (5) and check valve III (6) are converged, be connected to the entrance of oil eliminator (9), the outlet of oil eliminator (9) is connected to outdoor heat exchanger (10) entrance, outdoor heat exchanger (10) outlet is connected to liquid reservoir (11) entrance, liquid reservoir (11) outlet divides two-way respectively by expansion valve (12,16) be connected to two indoor side heat exchangers (13,17) entrance, one of them indoor side heat exchanger (13) outlet is connected to worst hot case gas-liquid separator for compressor I (14) entrance, another indoor side heat exchanger (17) outlet is connected to the entrance of worst cold case gas-liquid separator for compressor II (18), the outlet of worst hot case gas-liquid separator for compressor I (14) and worst cold case gas-liquid separator for compressor II (18) is connected respectively to worst hot case compressor bank (1,2) and the air inlet of worst cold case compressor bank (3), the spill port that it is characterized in that described oil eliminator (9) connects return line (24), return line (24) is connected to each worst hot case compressor bank (1 by capillary (7) respectively, 2) crankcase, each worst hot case compressor bank (1, the upper position of the normal oil level upper limit of crankcase 2) is provided with overflow pipe (21,22), overflow pipe is by capillary (19,20) and magnetic valve (25) be connected to the entrance of worst cold case gas-liquid separator for compressor (18).
2. according to the described a kind of compressor bank oil-balancing system of claim 1, it is characterized in that the normal oil level upper limit position of the crankcase of described each worst hot case compressor bank is connected by the oil equalizing pipe road.
3. according to the described a kind of compressor bank oil-balancing system of claim 1, it is characterized in that described oil eliminator is the float-ball type oil eliminator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110173741 CN102278837B (en) | 2011-01-28 | 2011-06-24 | Oil equalization system of compressor units |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110031826 | 2011-01-28 | ||
| CN201110031826.0 | 2011-01-28 | ||
| CN 201110173741 CN102278837B (en) | 2011-01-28 | 2011-06-24 | Oil equalization system of compressor units |
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| Publication Number | Publication Date |
|---|---|
| CN102278837A CN102278837A (en) | 2011-12-14 |
| CN102278837B true CN102278837B (en) | 2013-08-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201110173741 Active CN102278837B (en) | 2011-01-28 | 2011-06-24 | Oil equalization system of compressor units |
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| CN (1) | CN102278837B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102954624A (en) * | 2012-11-27 | 2013-03-06 | 大连三洋压缩机有限公司 | Parallel compressor oil return device and control method |
| CN103913015B (en) * | 2012-12-31 | 2016-04-27 | 丹佛斯（天津）有限公司 | Oil balancing unit and use its refrigeration system |
| CN103062841B (en) * | 2013-01-18 | 2015-08-19 | 四川长虹电器股份有限公司 | A kind of air-conditioning system, control system and air conditioning control method |
| CN104848599B (en) * | 2015-05-26 | 2017-06-13 | 珠海格力电器股份有限公司 | Air-conditioning system and its control method |
| CN105674626B (en) * | 2016-03-30 | 2017-12-05 | 杭州佳力斯韦姆新能源科技有限公司 | A kind of air-source carbon dioxide heat pump system with high pressure oil |
| CN111256379A (en) * | 2018-11-30 | 2020-06-09 | 广东美芝精密制造有限公司 | Refrigerating device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0838640A3 (en) * | 1996-10-28 | 1998-06-17 | Matsushita Refrigeration Company | Oil level equalizing system for plural compressors |
| CN1614328A (en) * | 2003-11-07 | 2005-05-11 | 松下电器产业株式会社 | Air conditioner and its control |
| CN101113854A (en) * | 2006-07-26 | 2008-01-30 | 海尔集团公司 | Oil equalizing and coolant counterbalancing system of multiple air-conditioning unit and controlling method thereof |
| CN201229085Y (en) * | 2008-06-13 | 2009-04-29 | 广东志高空调有限公司 | Parallel air-conditioning unit with multi compressors |
| CN201724461U (en) * | 2010-07-01 | 2011-01-26 | 大连三洋压缩机有限公司 | Refrigeration and cold storage system device for air conditioner |
| CN202171368U (en) * | 2011-01-28 | 2012-03-21 | 大连三洋压缩机有限公司 | Oil equalizing system for compressor unit |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10205897A (en) * | 1997-01-28 | 1998-08-04 | Matsushita Refrig Co Ltd | Oil balancing system for a plurality of compressors |
| US20060073026A1 (en) * | 2004-10-06 | 2006-04-06 | Shaw David N | Oil balance system and method for compressors connected in series |
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2011
- 2011-06-24 CN CN 201110173741 patent/CN102278837B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0838640A3 (en) * | 1996-10-28 | 1998-06-17 | Matsushita Refrigeration Company | Oil level equalizing system for plural compressors |
| CN1614328A (en) * | 2003-11-07 | 2005-05-11 | 松下电器产业株式会社 | Air conditioner and its control |
| CN101113854A (en) * | 2006-07-26 | 2008-01-30 | 海尔集团公司 | Oil equalizing and coolant counterbalancing system of multiple air-conditioning unit and controlling method thereof |
| CN201229085Y (en) * | 2008-06-13 | 2009-04-29 | 广东志高空调有限公司 | Parallel air-conditioning unit with multi compressors |
| CN201724461U (en) * | 2010-07-01 | 2011-01-26 | 大连三洋压缩机有限公司 | Refrigeration and cold storage system device for air conditioner |
| CN202171368U (en) * | 2011-01-28 | 2012-03-21 | 大连三洋压缩机有限公司 | Oil equalizing system for compressor unit |
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| CN102278837A (en) | 2011-12-14 |
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Address after: 116600 economic and Technological Development Zone, No. 8 loose Street Applicant after: DALIAN SANYO COMPRESSOR Co.,Ltd. Address before: 116033 No. 78 East Sea Road, Ganjingzi District, Liaoning, Dalian Applicant before: DALIAN SANYO COMPRESSOR Co.,Ltd. |
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Owner name: PANASONIC APPLIANCES COMPRESSOR (DALIAN) CO., LTD. Free format text: FORMER NAME: DALIAN SANYO COMPRESSOR CO., LTD. |
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Address after: 116600 Dalian economic and Technological Development Zone, Liaoning Pine Street, No. 8 Patentee after: PANASONIC APPLIANCES COMPRESSOR (DALIAN) CO.,LTD. Address before: 116600 Dalian economic and Technological Development Zone, Liaoning Pine Street, No. 8 Patentee before: DALIAN SANYO COMPRESSOR Co.,Ltd. |
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Effective date of registration: 20170203 Address after: 116600 Dalian economic and Technological Development Zone, Liaoning Pine Street, No. 8 Patentee after: PANASONIC REFRIGERATOR SYSTEM (DALIAN) CO.,LTD. Address before: 116600 Dalian economic and Technological Development Zone, Liaoning Pine Street, No. 8 Patentee before: PANASONIC APPLIANCES COMPRESSOR (DALIAN) CO.,LTD. |
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| CP01 | Change in the name or title of a patent holder |
Address after: 116600 No. 8 Songlan Street, Dalian Economic and Technological Development Zone, Liaoning Province Patentee after: Bingshan Songyang Refrigerator System (Dalian) Co.,Ltd. Address before: 116600 No. 8 Songlan Street, Dalian Economic and Technological Development Zone, Liaoning Province Patentee before: PANASONIC REFRIGERATOR SYSTEM (DALIAN) CO.,LTD. |
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