CN204574622U - Rotor-type compressor parallel system - Google Patents
Rotor-type compressor parallel system Download PDFInfo
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- CN204574622U CN204574622U CN201520102245.5U CN201520102245U CN204574622U CN 204574622 U CN204574622 U CN 204574622U CN 201520102245 U CN201520102245 U CN 201520102245U CN 204574622 U CN204574622 U CN 204574622U
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- oil
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- rotor
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Abstract
The utility model relates to a kind of rotor-type compressor parallel system, and it comprises compressor, oil eliminator, oil equalizing pipe and oil return pipe; Compressor is multiple stage in parallel, and the blast pipe of multiple compressors is connected with same oil eliminator respectively by high press fit pipe; The oil-in of oil equalizing pipe is connected with the housing of compressor, and the oil-in of oil equalizing pipe is positioned at the position of more than the minimum oil level of compressor, and the oil-out of oil equalizing pipe is connected with blast pipe or described high press fit pipe; Oil eliminator is connected by the air entry of oil return pipe with the gas-liquid separator of compressor.The utility model installs oil equalizing pipe on compressor housing, utilize the pressure differential of compressor itself, the refrigeration oil of having more than needed in compressor is discharged, and takes back in the housing of each compressor by oil return pipe, thus achieve oily autobalance, its structure is simple, cost is lower.Further, the oil-in of oil equalizing pipe is located at more than the upper surface of the cylinder of compressor, when can effectively avoid compressor to run up, petrol starvation occurs.
Description
Technical field
The utility model relates to air-conditioning technical field, particularly relates to a kind of rotor-type compressor parallel system.
Background technology
In refrigeration systems, during compressor operating, must there is a small part refrigeration oil (also known as lubricating oil) can continuously be forced out together with refrigerant from cylinder, enter in the pipeline of refrigeration system and condenser and evaporimeter.When refrigeration oil can not return compressor continuously, compressor pasta can be caused to decline, and exhausted to refrigeration oil, occur that compressor oil starvation burns phenomenon.So ensureing that refrigeration oil returns compressor is continuously one of most important problem in refrigerant system design.
Along with popularizing of awareness of saving energy, multi-connected air conditioning system (be also called the runoff of intermediary when chilling system, English Variable Refrigerant Flow by name, is called for short VRF) is by extensive use.Its form of expression is generally the system that an off-premises station forms with multiple stage indoor set, and the ON/OFF according to indoor set changes, and the cold medium flux in system will and then change.If use single compressor only to adopt on off control often can not adapt to the needs of load acute variation as energy adjustment measure.So be used in same refrigeration system by multiple compressors parallel connection, not only can widen the range of capacity of refrigeration system, reduce starting current, extend the service life of compressor, system can also be simplified significantly, reduce cost of investment.
In the system only having a compressor, as long as adopt necessary measure, as adopted rational circuit design, after each position of system forms stable distribution of oil mass, refrigeration oil can be smoothly through compressor suction duct and return to compressor inside, makes compressor keep normally working pasta.
But, if use multiple compressors in parallel in same refrigeration system, the problem of each compressor can be returned smoothly with regard to there is refrigeration oil.Along with the change of operating condition, if oily internal circulating load when the oily internal circulating load of compressor when discharging is greater than suction, just there will be compressor oil face decline phenomenon; On the contrary, if oily internal circulating load when the oily internal circulating load of compressor when discharging is less than suction, just occur that compressor amasss oily phenomenon.It is excessive that refrigeration oil on compressor too much there will be rotor load, and input power rises; Oil has lacked will cause the different abrasion of movement, damages function.Therefore, ensure that multiple compressors pasta balance is that parallel connection compressor operation technique is crucial.
In existing technology, be much judge oil level by self controlled elements such as oil level controllers and initiatively carry out the circuit of repairing action.
Utility model content
In order to ensure that multiple compressors pasta balances, judge oil level above by self controlled element and initiatively carry out the circuit of repairing action, need multiple control element to coordinate during work, complex structure, the cost of control element are higher, and it is less economical.
The utility model completes based on above-mentioned situation, and its objective is provides a kind of rotor-type compressor parallel system, in rotor-type compressor parallel system, utilizes simple, the lower-cost oil equalizing pipe structure of structure to carry out the pasta autobalance of compressor.
To achieve these goals, the utility model provides a kind of rotor-type compressor parallel system, and it comprises compressor, oil eliminator, oil equalizing pipe and oil return pipe; Described compressor is multiple stage in parallel, and the blast pipe of compressor described in multiple stage is connected with same oil eliminator respectively by high press fit pipe; The oil-in of described oil equalizing pipe is connected with the housing of described compressor, and the oil-in of described oil equalizing pipe is positioned at the position of more than the minimum oil level of described compressor, and the oil-out of described oil equalizing pipe is connected with described blast pipe or described high press fit pipe; Described oil eliminator is connected with the air entry of the gas-liquid separator of described compressor by described oil return pipe.
Pressure differential during rotor-type compressor work can be made full use of thus, by oil equalizing pipe, refrigeration oil more than needed in each compressor is discharged, the refrigerant of refrigeration oil in blast pipe or high press fit pipe takes in oil eliminator, the oil concentrated in same oil eliminator returns the air entry of the gas-liquid separator of each compressor again by oil return pipe, take back in compressor by the refrigerant of the air entry of this gas-liquid separator, thus achieve the refrigeration oil autobalance of each compressor in compressor, this oil equalizing pipe arrange that structure is simple, cost is lower.
Another object of the present utility model avoids compressor, when running up, petrol starvation occurs.
To achieve these goals, further, in rotor-type compressor parallel system of the present utility model, the oil-in of described oil equalizing pipe is positioned at the position of more than the upper surface of the cylinder of described compressor.
Experimental result shows, when the oil-in of oil equalizing pipe is positioned at the upper surface of cylinder, the decline of compressor pasta when maximum speed is in the pasta of reliability guarantee, therefore, the oil-in of oil equalizing pipe is positioned at more than the upper surface of the cylinder of compressor, when can guarantee that compressor runs up, can not petrol starvation be there is, ensure that compressing mechanism is lubricated fully.
Further, described compressor is single cylinder rotor-type compressor or twin rotor formula compressor.
Further, when described compressor is twin rotor formula compressor, the oil-in of described oil equalizing pipe is positioned at the position of more than the upper surface of the casing top half of described twin rotor formula compressor.
Further, the oil-in of described oil equalizing pipe is positioned at the position of below the lower surface of the stator of described compressor.Not long-pending when compressor runs well thus have too much refrigeration oil, avoids too much refrigeration oil to affect the input power of motor.
If the internal diameter of oil equalizing pipe is excessive, compressor just has too much refrigeration oil when running well and is taken in oil equalizing pipe system by refrigerant, adds the oily internal circulating load of oil equalizing pipe system, and then affects the compression performance of compressor.Experiment shows, when the caliber of oil equalizing pipe is 0.5 times of the caliber of blast pipe, oily internal circulating load recruitment is △ 1%, can meet the minimum standard of the oily internal circulating load recruitment of compressor, can not have an impact to the performance of compressor.
Therefore, further, the caliber of described oil equalizing pipe is less than 0.5 times of the caliber of described blast pipe.Ensure that the oily internal circulating load recruitment of compressor is at △ less than 1%, can not have an impact to the performance of compressor thus.
Further, in the housing of described compressor, the oil-in of described oil equalizing pipe protrudes from the inner walls of described compressor.Make compressor when normal pasta (pasta is lower than the oil-in of oil equalizing pipe) runs thus, the mixture resistance of the refrigerant of being discharged by oil equalizing pipe and refrigeration oil is increased, make to discharge difficulty, when the normal pasta of compressor, effectively reduce the oily discharge rate of compressor.
Further, the oil-in of described oil equalizing pipe is connected with the case weld of described compressor.
Further, the oil-out of described oil equalizing pipe and described blast pipe are welded to connect.
A kind of rotor-type compressor parallel system that technique scheme provides, oil equalizing pipe connects the housing of compressor and the blast pipe of compressor or high press fit pipe, utilize the pressure differential of rotor-type compressor itself, the refrigeration oil of having more than needed in compressor is discharged, refrigeration oil is taken to same oil eliminator by refrigerant, and is taken back the air entry of the gas-liquid separator of each compressor by oil return pipe, takes back in the housing of each compressor by refrigerant, thus achieve oily autobalance, its structure is simple, cost is lower.
Accompanying drawing explanation
Fig. 1 is the structural representation of the rotor-type compressor parallel system of the utility model embodiment one;
Fig. 2 is the compressor rotary speed-fuel head change curve of the utility model embodiment one;
Fig. 3 is the oil equalizing pipe installation diagram of the twin rotor formula compressor of the utility model embodiment one;
Fig. 4 is the oil equalizing pipe installation diagram of the single cylinder rotor-type compressor of the utility model embodiment one;
Fig. 5 is that the ratio of the caliber of the oil equalizing pipe of the utility model embodiment one and the caliber of blast pipe is to the influence curve figure of oily internal circulating load recruitment;
Fig. 6 is the enlarged drawing at O place in Fig. 3;
Fig. 7 is the lubricant oil separation mounting structure schematic diagram of the utility model embodiment two.
Wherein, 10, compressor; 11, housing; 12, gas-liquid separator; 13, blast pipe; 14, cylinder; 15, stator; 20, oil equalizing pipe; 21, the oil-in of oil equalizing pipe; 22, the oil-out of oil equalizing pipe; 30, high press fit pipe; 40, oil eliminator; 50, oil return pipe; 60, condenser; 70, choke valve; 80, evaporimeter.
Detailed description of the invention
Below in conjunction with drawings and Examples, detailed description of the invention of the present utility model is described in further detail.Following examples for illustration of the utility model, but are not used for limiting scope of the present utility model.
Embodiment one
As shown in Figure 1, a kind of rotor-type compressor parallel system of the utility model preferred embodiment, it comprises compressor 10, oil equalizing pipe 20, oil eliminator 40 and oil return pipe 50.
The compressor 10 of the present embodiment is rotor-type compressor, it comprises housing 11, be connected gas-liquid separator 12 with the sidepiece of housing 11 and be located at the blast pipe 13 at top of housing 11, bottom in housing 11 arranges compressing mechanism, this compressing mechanism comprises bent axle, cylinder 14 and rolling-rotor, top in housing 11 arranges motor, and this motor comprises rotor and stator 15.In air-conditioning refrigeration system, the blast pipe 13 of compressor is connected with oil eliminator 40 by high press fit pipe 30, refrigerant is after oil eliminator 40 carries out Oil-gas Separation, refrigerant is after 80s through condenser 60, choke valve 70 and evaporimeter successively, then gets back in the housing 11 of compressor through the air entry of the gas-liquid separator 12 of compressor.
The compressor 10 of the present embodiment is multiple stage in parallel, the blast pipe 13 of this multiple compressors 10 is connected with same oil eliminator 40 respectively by high press fit pipe 30, multiple compressors 10 is made to share an oil eliminator 40, pasta adjustment can be carried out thus between multiple compressors 10, wherein, the blast pipe 13 of compressor 10 is the outlet of refrigerant.
The oil-in 21 of the oil equalizing pipe in the present embodiment is connected with the housing 11 of compressor 10, and the oil-in 21 of this oil equalizing pipe is positioned at the position of more than the minimum oil level of compressor 10, the minimum oil level of this compressor refers to the oil level of oil sump bottom compressor, oil sump is positioned at the below of the cylinder 14 of compressor, at the oil level of this oil sump, compressor meets the lubricating requirement under general running speed; The oil-out 22 of oil equalizing pipe is then connected with the blast pipe 13 of compressor 10.The oil-in 21 of oil equalizing pipe housing 11 that is preferred and compressor 10 is welded to connect, and its manufacture craft is simple, can ensure the air-tightness of junction.
According to the design feature of rotor-type compressor, the housing 11 of compressor is high-pressure side, the oil-in 21 of oil equalizing pipe is arranged on the housing 11 of compressor, oil-out 22 regardless of oil equalizing pipe is connected to any position of compressor, refrigeration oil higher than the oil-in 21 of oil equalizing pipe can discharge compressor 10 by oil equalizing pipe 20, only need the pressure differential at the two ends of oil equalizing pipe 20 can overcome the drag losses of oil equalizing pipe 20 and the gravity of refrigeration oil self, therefore, theoretically, the oil-out 22 of oil equalizing pipe can be connected to any position of compressor, as the oil-out 22 of oil equalizing pipe being directly connected with oil eliminator.
The oil-out 22 of the oil equalizing pipe of the present embodiment is connected with the blast pipe 13 of compressor 10, this connected mode with the oil-out 22 of oil equalizing pipe is directly connected to compared with the structure of oil eliminator 40, the Energy Efficiency Ratio of system can be improved, and the operability in actual use procedure can be improved.This is because according to hydromechanical bernoulli principle: flow velocity is faster, pressure is less, and flow velocity is slower, and pressure is larger.The refrigerant flowing velocity V1 at blast pipe 13 place of compressor 10 is large more than the refrigerant flowing velocity V2 of the housing 11 of compressor 10, and therefore the refrigerant pressure P 2 at housing 11 place of compressor 10 is larger than the refrigerant pressure P 1 at blast pipe 13 place.Therefore, utilize the pressure differential between the housing 11 of compressor 10 and blast pipe 13, oily circulation rate can be improved, and then effectively can improve the operability in the Energy Efficiency Ratio of the oil balancing system of compressor and actual use procedure.
In the present embodiment, the refrigeration oil that housing 11 inside of compressor 10 is more than needed is discharged outside the housing 11 of compressor 10 through above-mentioned oil equalizing pipe 20, brought in oil eliminator 40 by refrigerant afterwards and carry out being separated of refrigeration oil and refrigerant, this oil eliminator 40 is connected with the air entry 12a of the gas-liquid separator of compressor 10 by oil return pipe 50, the air entry 12a of gas-liquid separator is the entrance of compressor refrigerant, refrigeration oil enters the air entry 12a side of gas-liquid separator by oil return pipe 50, finally taken back in compressor 10 by the refrigerant of air entry side, the refrigeration oil in compressor is made to be able to autobalance thus, do not affect compressor efficiency.
The oil-out 22 of the oil equalizing pipe of the present embodiment is connected with the blast pipe 13 of compressor 10, refrigeration oil takes in oil eliminator 40 by the gases at high pressure of blast pipe 13, this just requires in compressor manufacturing process, the oil-out 22 of oil equalizing pipe is welded on the blast pipe 13 of compressor 10, is convenient to reach the standard grade when air-conditioning system is produced installation thus.
According to the oil flow characteristic of oil equalizing pipe, the housing 11 of compressor 10 can be discharged higher than the refrigeration oil of the oil-in 21 of oil equalizing pipe in theory outside.And according to the service performance of rotor-type compressor, along with the increase of compressor rotary speed, compressor cold medium flux strengthens, refrigeration oil can be thrown to the top of housing 11 together along with refrigerant, the refrigeration oil be placed between the stator 15 of compressor 10 and housing 11 top can be increased, make the pasta of housing 11 bottom decline along with the rising of rolling-rotor rotating speed thus.
Can draw from above-mentioned analysis, if the oil-in of oil equalizing pipe 21 installation site is too low, because compressor 10 pasta when high rotating speed can decline further, thus compressor 10 oil starvation can be caused, the lubricating oil needed for compressing mechanism cannot be ensured.Therefore, after on the compressor oil equalizing pipe 20 being installed, the change of pasta with rotating speed of compressor 10 must be confirmed.
After a large amount of experiments, drawn the rotating speed shown in Fig. 2-fuel head curve map, in the plot, A straight line represents the pasta that reliability ensures, B curve represents the oil mass change of cylinder upper surface, and C curve represents the oil mass change of cylinder lower surface.
As can be seen from Figure 2, when the oil-in 21 of oil equalizing pipe is positioned at the upper surface of cylinder 14 of compressor 10, more than the pasta A that the minimum point that pasta under maximum speed declines ensures at reliability, the pasta that this reliability ensures makes compressor when maximum speed, and the compressing mechanism of compressor 10 bottom is able to sufficient lubrication.If the oil-in of oil equalizing pipe 21 is positioned at the lower surface of the cylinder of compressor, when rotating speed is about 82rps (namely rotating speed per second is 82), under pasta, be reduced to the pasta A that reliability ensures.Therefore, in order to the compressing mechanism making compressor 10 at high speed can not oil starvation, the minimum altitude h of the oil-in 21 of the oil equalizing pipe of the present embodiment
0should more than the upper surface of the cylinder 14 of compressor 10, the height of the upper surface of the cylinder 14 of compressor 10 is set to h.
As Fig. 3 and Fig. 4, the rotor-type compressor of shown the present embodiment can be single cylinder rotor-type compressor or twin rotor formula compressor, or is the combination of single cylinder rotor-type compressor and twin rotor formula compressor.And for twin rotor formula compressor, it comprises casing top half 14a and lower cylinder 14b, the setting height(from bottom) of the oil-in 21 of oil equalizing pipe should be more than the upper surface of the casing top half 14a of this twin rotor formula compressor, as shown in Figure 3.For single cylinder rotor-type compressor, the setting height(from bottom) of the oil-in 21 of oil equalizing pipe should be more than the upper surface of the cylinder 14 of this single cylinder rotor-type compressor, as shown in Figure 4.
If the refrigeration oil in the housing 11 of compressor 10 is too much, the load of rotor will be made excessive, the input power of the motor of housing upper will be affected, in order to make, compressor 10 is not long-pending when running well too much refrigeration oil, and then do not affect the input power of motor, the extreme higher position of the oil-in 21 of the oil equalizing pipe of the present embodiment should below the lower surface of the stator 15 of compressor, and as shown in Figure 3, the height of the lower surface of this stator 15 is set to H.
Therefore, the setting height(from bottom) h of the oil-in 21 of oil equalizing pipe
0following requirement should be met:
h≤h
0≤H
The oil equalizing pipe 20 that the compressor 10 of the present embodiment is installed, requires that oil equalizing pipe 20 has suitable caliber, and the caliber of oil equalizing pipe 20 is excessive, too small all can affect to the performance of compressor 10.If the caliber of oil equalizing pipe 20 is too large, compressor 10 goes with regard to there being too much refrigeration oil to be discharged in oil equalizing pipe road when running well, and causes oily internal circulating load to rise, and then affects the performance of compressor.But if the caliber of oil equalizing pipe 20 is too small, the refrigeration oil piled up in compressor 10 cannot be discharged in time, then can cause refrigeration oil can not Fast-Balance.Therefore, the design of the size of oil equalizing pipe 20 caliber is very important.
The pipe that caliber is set to d, length is set to L, under laminar condition, the computing formula along stroke pressure loss Δ p of pipe laminar flow is:
Can be known by formula above, if the caliber of oil equalizing pipe 20 is larger, oil equalizing pipe 20 laminar flow less along stroke pressure loss, refrigeration oil discharges compressor 10 with regard to easy by oil equalizing pipe 20.But because the oil-out 22 of oil equalizing pipe is connected with oil eliminator 40, if the caliber of oil equalizing pipe 20 is excessive, compressor 10 just has too much refrigeration oil when running well and is taken in oil equalizing pipe road by refrigerant, this adds increased the oily internal circulating load of compressor, and then affects the compression performance of compressor 10.
Therefore, select the caliber of suitable oil equalizing pipe to seem particularly important, the verification experimental verification that the present embodiment is tested by the oily internal circulating load under different tube diameters, to choose the caliber of optimum oil equalizing pipe 20.
After the test that have passed through the oily internal circulating load test under different tube diameters, draw oily internal circulating load influence curve figure as shown in Figure 5.As can be seen from Figure 5, after compressor 10 is installed oil equalizing pipe 20, can there is certain deterioration in the oily internal circulating load of compressor 10.Abscissa in Fig. 5 is the ratio of the caliber of oil equalizing pipe and the caliber of blast pipe, and ordinate is then the value added of compressor oil circulation amount.By the coupling experience of air-conditioning, the recruitment of oily internal circulating load at △ less than 1%, because the recruitment of this oily internal circulating load can be optimized elimination by oil eliminator in system 40, can not need be discharged in compressor.So can draw from result of the test, when the caliber of oil equalizing pipe is 0.5 times of the caliber of blast pipe, oily internal circulating load recruitment is △ 1%, can meet the minimum standard of oily internal circulating load recruitment, can not have an impact to the performance of compressor.
Therefore, the recruitment in order to the oily internal circulating load making compressor controls at △ less than 1%, and to ensure that the performance of compressor can not have an impact, the pipe diameter determing of the oil equalizing pipe 20 of the present embodiment is less than 0.5 times of the caliber of blast pipe.
When the oil-in 21 of oil equalizing pipe is connected with the housing 11 of compressor 10, in the housing 11 of compressor, the oil-in 21 of oil equalizing pipe should protrude from the certain distance a of housing 11 inwall of compressor 10, as shown in Figure 6.Give prominence to the housing 11 inwall one segment distance a of compressor at the oil-in 21 of oil equalizing pipe after, compressor 10 is when normal pasta (this pasta is lower than the oil-in 21 of oil equalizing pipe) runs, the mixture resistance of the refrigerant of being discharged by oil equalizing pipe 20 and refrigeration oil is increased, discharge difficulty, thus guarantee when the normal pasta of compressor 20, effectively reduce the oily discharge rate of compressor.
Embodiment two
As shown in Figure 7, the rotor-type compressor parallel system of the present embodiment and the difference of embodiment one are only, the oil-out 22 of the oil equalizing pipe of the present embodiment connects with the high press fit pipe 30 be connected between blast pipe 13 and oil eliminator 40, its with the mode in embodiment one, the oil-out 22 of oil equalizing pipe is directly connected with blast pipe 13 unlike, when processing and fabricating compressor, oil equalizing pipe 20 is not needed to be welded on blast pipe 13, but oil equalizing pipe joint is reserved on high press fit pipe 30, the oil-out 22 of oil equalizing pipe is being installed on the oil equalizing pipe joint of high press fit pipe 30 when whole compressor assembling, the mounting structure of the oil equalizing pipe 20 of the present embodiment can reduce the difficulty of the processing and fabricating of compressor.
Because high press fit pipe 30 connects blast pipe 13 and the oil eliminator 40 of compressor 10, therefore, the refrigerant flowing velocity at this high press fit pipe 30 place is large more than the refrigerant flowing velocity on the housing 11 of compressor 10, therefore, the oil-out 22 of this oil equalizing pipe is connected on high press fit pipe, can make equally to produce pressure differential between the oil-in 21 of oil equalizing pipe and oil-out 22.
To sum up, rotor-type compressor parallel system of the present utility model, its structure is simple, cost is lower, adopt oil equalizing pipe to connect the housing of compressor and the blast pipe of compressor or high press fit pipe, utilize the pressure differential of rotor-type compressor itself, by the refrigeration oil discharge of having more than needed in compressor, refrigeration oil is taken to same oil eliminator by refrigerant, and the air entry of the gas-liquid separator of each compressor is taken back by oil return pipe, take back in the housing of each compressor by refrigerant, thus achieve oily autobalance.Further, the oil-in of oil equalizing pipe is located at more than the upper surface of the cylinder of compressor, occurs to lack phenomenon, ensure that compressing mechanism is lubricated fully when can effectively avoid compressor to run up.
The above is only preferred embodiment of the present utility model; should be understood that; for those skilled in the art; under the prerequisite not departing from the utility model know-why; can also make some improvement and replacement, these improve and replace and also should be considered as protection domain of the present utility model.
Claims (9)
1. a rotor-type compressor parallel system, is characterized in that, comprises compressor, oil eliminator, oil equalizing pipe and oil return pipe; Described compressor is multiple stage in parallel, and the blast pipe of compressor described in multiple stage is connected with same oil eliminator respectively by high press fit pipe;
The oil-in of described oil equalizing pipe is connected with the housing of described compressor, and the oil-in of described oil equalizing pipe is positioned at the position of more than the minimum oil level of described compressor, and the oil-out of described oil equalizing pipe is connected with described blast pipe or described high press fit pipe; Described oil eliminator is connected with the air entry of the gas-liquid separator of described compressor by described oil return pipe.
2. rotor-type compressor parallel system as claimed in claim 1, it is characterized in that, the oil-in of described oil equalizing pipe is positioned at the position of more than the upper surface of the cylinder of described compressor.
3. rotor-type compressor parallel system as claimed in claim 2, it is characterized in that, described compressor is single cylinder rotor-type compressor or twin rotor formula compressor.
4. rotor-type compressor parallel system as claimed in claim 3, it is characterized in that, when described compressor is twin rotor formula compressor, the oil-in of described oil equalizing pipe is positioned at the position of more than the upper surface of the casing top half of described twin rotor formula compressor.
5. the rotor-type compressor parallel system as described in any one of claim 1-4, is characterized in that, the oil-in of described oil equalizing pipe is positioned at the position of below the lower surface of the stator of described compressor.
6. rotor-type compressor parallel system as claimed in claim 1, it is characterized in that, the caliber of described oil equalizing pipe is less than 0.5 times of the caliber of described blast pipe.
7. rotor-type compressor parallel system as claimed in claim 1, it is characterized in that, in the housing of described compressor, the oil-in of described oil equalizing pipe protrudes from the inner walls of described compressor.
8. rotor-type compressor parallel system as claimed in claim 1, it is characterized in that, the oil-in of described oil equalizing pipe is connected with the case weld of described compressor.
9. rotor-type compressor parallel system as claimed in claim 1, it is characterized in that, oil-out and the described blast pipe of described oil equalizing pipe are welded to connect.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520102245.5U CN204574622U (en) | 2015-02-12 | 2015-02-12 | Rotor-type compressor parallel system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520102245.5U CN204574622U (en) | 2015-02-12 | 2015-02-12 | Rotor-type compressor parallel system |
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| CN204574622U true CN204574622U (en) | 2015-08-19 |
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| CN201520102245.5U Withdrawn - After Issue CN204574622U (en) | 2015-02-12 | 2015-02-12 | Rotor-type compressor parallel system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104633998A (en) * | 2015-02-12 | 2015-05-20 | 三菱电机(广州)压缩机有限公司 | Rotary compressor parallel connection system |
-
2015
- 2015-02-12 CN CN201520102245.5U patent/CN204574622U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104633998A (en) * | 2015-02-12 | 2015-05-20 | 三菱电机(广州)压缩机有限公司 | Rotary compressor parallel connection system |
| CN104633998B (en) * | 2015-02-12 | 2017-10-31 | 三菱电机(广州)压缩机有限公司 | Rotor-type compressor parallel system |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20150819 Effective date of abandoning: 20171031 |