CN202171368U - Oil equalizing system for compressor unit - Google Patents
Oil equalizing system for compressor unit Download PDFInfo
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- CN202171368U CN202171368U CN201120218323XU CN201120218323U CN202171368U CN 202171368 U CN202171368 U CN 202171368U CN 201120218323X U CN201120218323X U CN 201120218323XU CN 201120218323 U CN201120218323 U CN 201120218323U CN 202171368 U CN202171368 U CN 202171368U
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Abstract
The utility model discloses an oil equalizing system for a compressor unit. The oil equalizing system comprises a multi-temperature evaporation refrigeration system which is formed by in parallel connecting more than two high-temperature working condition compressor units and a low-temperature working condition compressor unit, wherein an oil return hole of an oil separator is connected with an oil return pipeline; the oil return pipeline is respectively connected to a crankshaft box of each high-temperature working condition compressor unit by a capillary tube; an overflow tube is arranged on the upper part of a normal oil level upper limit of the crankshaft box of each high-temperature working condition compressor unit; and the overflow tube is connected to an inlet of a gas-liquid separator of the low-temperature working condition compressor by a capillary tube and a solenoid valve. The oil equalizing system for the compressor unit has the beneficial effects that the refrigeration oil can be ensured to be distributed uniformly without operating any oil equalizing programme and detecting any oil level, as long as the charging capacity of the refrigeration oil in the system is proper.
Description
Technical field
The utility model belongs to refrigeration technology field, relates in particular to multi-evaporation temperature, parallelly connected unit compressor oil equalization 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 uneven 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 each compressor crankcase pressure of multi-evaporation temperature parallel connection unit not simultaneously, just can cause refrigeration oil can more flow in the relatively low compressor of crankcase pressure.
Summary of the invention
The purpose of the utility model is the deficiency that solves prior art, and a kind of oil-balancing system of controlling simple, with low cost and reliable parallelly connected compressor is provided.
To achieve these goals; The utility model is taked following technical scheme: a kind of compressor bank oil-balancing system; Comprise the how warm sweat cooling system that constitutes by two above worst hot case compressor bank and the parallel connection of worst cold case compressor bank; After the worst hot case compressor bank of many temperature sweat coolings system and the exhaust of worst cold case compressor bank converge through check valve I, check valve II and check valve III respectively; Be connected to the inlet of oil eliminator; The outlet of oil eliminator is connected to the outdoor heat exchanger inlet; The outdoor heat exchanger outlet is connected to the liquid reservoir inlet; The liquid reservoir outlet divides two-way to be connected to the indoor side heat exchanger inlet through expansion valve respectively, and the indoor side heat exchanger outlet is connected respectively to the inlet of worst hot case gas-liquid separator for compressor I and worst cold case gas-liquid separator for compressor II, and 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 said oil eliminator connects return line; Return line is connected to the crankcase of each worst hot case compressor bank respectively through 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 inlet of worst cold case gas-liquid separator for compressor through capillary and magnetic valve.
The said a kind of compressor bank oil-balancing system of the utility model is characterized in that the normal oil level upper limit position of the crankcase of said each worst hot case compressor bank is connected through the oil equalizing pipe road.
The said a kind of compressor bank oil-balancing system of the utility model is characterized in that said oil eliminator is the float-ball type oil eliminator.
The principle of the oil-balancing system of the utility model is: the exhaust of parallelly connected compressor enters into oil eliminator; When the refrigeration oil of separating reaches certain liquid level in oil eliminator; Through 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 beneficial effect of the utility model is: as long as the filling quantity of refrigeration oil is suitable in the system, just can ensure the refrigeration oil distributed uniform, and need not move any equal oily program and carry out the detection of any oil level.
Description of drawings
The utility model has accompanying drawing 1 width of cloth,
Fig. 1 is the structural scheme of mechanism of the oil-balancing system of the utility model.
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 heat exchanger I; 14-gas-liquid separator I; 15-check valve IV; 16-expansion valve II; 17-indoor 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
Specify the embodiment of the utility model below in conjunction with accompanying drawing.
Embodiment is the refrigeration system of the multi-evaporation temperature parallel connection unit 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 inlet 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 through capillary I 7, is connected to the crankcase of second compressor 2 through 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 through the oil equalizing pipe road.In the high slightly position of first compressor, the 1 normal oil level upper limit; Be connected to the inlet of gas-liquid separator 18 through 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 through capillary IV 20 and magnetic valve 25.The outlet of oil eliminator 9 is connected to outdoor heat exchanger 10 inlets; Outdoor heat exchanger 10 outlets are connected to liquid reservoir 11 inlets; Liquid reservoir 11 outlets divide two-way to be connected to indoor side heat exchanger 13,17 inlets through expansion valve 12,16 respectively; Indoor side heat exchanger 13,17 outlets are connected respectively to the inlet 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 the air inlet of worst hot case compressor bank 1,2 and 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 got into 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 through 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 move to other one through oil equalizing pipe road 23.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 through overflow passage 21 and 22 inlets to the gas-liquid separator 18 of the 3rd compressor 3, and gets 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 is different; The mobile trend of refrigeration oil through getting back to the low relatively compressor of crankcase pressure in oil equalizing pipe road 23, is got back to the inlet of the gas-liquid separator 18 of the 3rd compressor 3 for earlier then through the overflow passage of this compressor.
2) 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 gets into 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 through 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 through 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 inlet of the gas-liquid separator 18 of the 3rd compressor 3 through 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 gets 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 through 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 move to other one through oil equalizing pipe road 23.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 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 inlet level height of the gas-liquid separator 18 of common the 3rd compressor can be higher than the level 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 through each oil eliminator 9 ball-cock assemblys and second compressor, 2 crankcases; Refrigeration oil is moved in the gas-liquid separator 18 through 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 through 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 possibly have certain discrepancy in elevation.Yet through 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 situation, as long as the filling quantity of system's refrigeration oil is suitable,, can both ensure the oil return equably of each compressor no matter be that any compressor is to shut down or operating condition.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 the embodiment of the utility model, the utility model 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 constitutes by two above worst hot case compressor bank and the parallel connection of worst cold case compressor bank; After the worst hot case compressor bank (1,2) of many temperature sweat coolings system and the exhaust of worst cold case compressor bank (3) are passed through check valve I (4), check valve II (5) and check valve III (6) respectively and are converged; Be connected to the inlet of oil eliminator (9); The outlet of oil eliminator (9) is connected to outdoor heat exchanger (10) inlet; Outdoor heat exchanger (10) outlet is connected to liquid reservoir (11) inlet; Liquid reservoir (11) outlet divides two-way to be connected to indoor side heat exchanger (13,17) inlet through expansion valve (12,16) respectively; Indoor side heat exchanger (13,17) outlet is connected respectively to the inlet of worst hot case gas-liquid separator for compressor I (14) and 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 the air inlet of worst hot case compressor bank (1,2) and worst cold case compressor bank (3); The spill port that it is characterized in that said oil eliminator (9) connects return line (24); Return line (24) is connected to the crankcase of each worst hot case compressor bank (1,2) respectively through capillary (7), the upper position of the normal oil level upper limit of the crankcase of each worst hot case compressor bank (1,2) is provided with overflow pipe (21,22), and overflow pipe is connected to the inlet of worst cold case gas-liquid separator for compressor (18) through capillary (19,20) and magnetic valve (25).
2. according to the said 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 said each worst hot case compressor bank is connected through the oil equalizing pipe road.
3. according to the said a kind of compressor bank oil-balancing system of claim 1, it is characterized in that said oil eliminator is the float-ball type oil eliminator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201120218323XU CN202171368U (en) | 2011-01-28 | 2011-06-24 | Oil equalizing system for compressor unit |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201120031240.X | 2011-01-28 | ||
| CN201120031240 | 2011-01-28 | ||
| CN201120218323XU CN202171368U (en) | 2011-01-28 | 2011-06-24 | Oil equalizing system for compressor unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202171368U true CN202171368U (en) | 2012-03-21 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201120218323XU Expired - Lifetime CN202171368U (en) | 2011-01-28 | 2011-06-24 | Oil equalizing system for compressor unit |
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| Country | Link |
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| CN (1) | CN202171368U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278837A (en) * | 2011-01-28 | 2011-12-14 | 大连三洋压缩机有限公司 | Oil equalization system of compressor units |
-
2011
- 2011-06-24 CN CN201120218323XU patent/CN202171368U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278837A (en) * | 2011-01-28 | 2011-12-14 | 大连三洋压缩机有限公司 | Oil equalization system of compressor units |
| CN102278837B (en) * | 2011-01-28 | 2013-08-14 | 大连三洋压缩机有限公司 | Oil equalization system of compressor units |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee | ||
| CP02 | Change in the address of a patent holder |
Address after: 116600 Dalian economic and Technological Development Zone, Liaoning Pine Street, No. 8 Patentee after: Dalian Sanyo Compressor Co., Ltd. Address before: 116033 No. 78 East Sea Road, Ganjingzi District, Liaoning, Dalian Patentee before: Dalian Sanyo Compressor Co., Ltd. |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20120321 Effective date of abandoning: 20130814 |
|
| RGAV | Abandon patent right to avoid regrant |