CN206348131U - A kind of Performance Test System of the big pressure difference operating mode of restricting element - Google Patents
A kind of Performance Test System of the big pressure difference operating mode of restricting element Download PDFInfo
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- CN206348131U CN206348131U CN201621191805.XU CN201621191805U CN206348131U CN 206348131 U CN206348131 U CN 206348131U CN 201621191805 U CN201621191805 U CN 201621191805U CN 206348131 U CN206348131 U CN 206348131U
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- restricting element
- pressure
- pressure sensor
- controller
- compressor
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Abstract
The utility model is related to test equipment technical field, a kind of Performance Test System of the big pressure difference operating mode of restricting element is disclosed, including the first compressor to form loop, the first oil eliminator, condenser, tested restricting element, the second evaporator, the second compressor, the second oil eliminator and the first evaporator are sequentially communicated by pipeline；Also include electric expansion valve, first pressure sensor, second pressure sensor, the 3rd pressure sensor, the first controller, second controller, frequency converter, the 3rd controller, condensing pressure control two-port valve, cooling water inlet pipe and outlet pipe.When the utility model can solve single stage compress, due to test scope defect caused by the limitation of compressor itself compression ratio, widen the condition range of restricting element performance test, restricting element is tested it is broader deeper into test provide technical support and guarantee.
Description
Technical field
The utility model is related to test equipment technical field, the performance of specifically a kind of big pressure difference operating mode of restricting element
Test system, in particular for Performance Test System of the restricting element in refrigeration system under conditions of big pressure difference.
Background technology
In refrigeration systems, restricting element is as one of four most basic big parts of kind of refrigeration cycle, and the quality of its performance is directly
The success or failure that refrigerant system design is used cooperatively are decide, therefore, performance of the research restricting element under different operating modes has very
Important practical significance.For a refrigeration part, the research in terms of its reliability, usability will often be far longer than
Specified applying working condition scope.Under this background, the measurement condition scope of restricting element is often greater than refrigeration system compressor
The operating mode of actual use.If carrying out the performance test of restricting element according to the condition range of compressor, restricting element can be caused
The defect and deficiency of performance study.Therefore, prior art has much room for improvement.
Utility model content
There is provided a kind of performance test system of the big pressure difference operating mode of restricting element for above-mentioned problem for the utility model
System, is solved the defect in restricting element performance test caused by being limited due to compressor pressure ratios, widens the survey of restricting element performance
The condition range of examination.
The utility model to achieve the above object, takes following technical scheme to be achieved：
A kind of Performance Test System of the big pressure difference operating mode of restricting element, including be sequentially communicated to form the of loop by pipeline
One compressor, the first oil eliminator, condenser, tested restricting element, the second evaporator, the second compressor, the second oil eliminator
With the first evaporator；Also include electric expansion valve, first pressure sensor, second pressure sensor, the 3rd pressure sensor, the
One controller, second controller, frequency converter, the 3rd controller, condensing pressure control two-port valve, cooling water inlet pipe and water outlet
Pipe；The condenser, the first evaporator and the second evaporator are equipped with cooling water inlet and coolant outlet, and the cooling water enters
Mouth connects cooling water inlet pipe, and the coolant outlet connects cooling water outlet pipe；The electric expansion valve two ends difference
Connect condensator outlet and the first evaporator；The first pressure sensor is arranged on tested restricting element entrance, described
Second pressure sensor is arranged on tested restricting element outlet；3rd pressure sensor is arranged on the first evaporator inlet；
The condensing pressure control two-port valve is arranged between the cooling water inlet of condenser and cooling water inlet pipe；First control
Device is electrically connected with first pressure sensor, condensing pressure control two-port valve respectively；The second pressure sensor is successively with second
Controller, frequency converter and the second compression mechatronics；3rd controller respectively with the 3rd pressure sensor, electric expansion valve
Electrical connection；The oil outlet end of first oil eliminator connects the oil revolving end of the first compressor；Second oil eliminator it is fuel-displaced
The oil revolving end of the second compressor of end connection.
Preferably, the tested restricting element entrance sets a pneumatic ball valve respectively with outlet, is easy to connect or changes
Tested restricting element.
First compressor, the first oil eliminator, condenser, electric expansion valve and the first evaporator constitute one stage of compression system
SAPMAC method system, the first compressor, the first oil eliminator, condenser, electric expansion valve, the first evaporator, the second compressor,
Two oil eliminators and the second evaporator constitute two-stage compression cooling cycle system.
Under high pressure operating mode, all parts work of one stage of compression cooling cycle system, and the second compressor, the second oil separation
Device and the second evaporator are not worked (refrigerant can pass through), and the pressure of tested restricting element arrival end is gathered by first pressure sensor
Power (i.e. the condensing pressure of one stage of compression refrigeration system), is then passed to the first controller, the first controller is according to target operating condition
Pressure and actual samples pressure carry out PID arithmetic, output signal then are passed into condensing pressure control two-port valve, and then realize
The control of tested restricting element inlet port pressure.Meanwhile, one stage of compression cooling cycle system is gathered by the 3rd pressure sensor
Evaporating pressure, be then passed to the 3rd controller, the 3rd controller is according to the target evaporating pressure and actual samples pressure of setting
Power carries out PID arithmetic, output signal then is passed into electric expansion valve, and then realize one stage of compression refrigeration system evaporating pressure
Control.
The utility model controls the condensing pressure of one stage of compression refrigeration system to realize tested throttling member by the first controller
Part inlet pressure is controlled, and the main heat exchange amount by the auxiliary side of condenser of control of the condensing pressure of one stage of compression refrigeration system is real
It is existing.
Under low pressure operating mode, all parts work of two-stage compression cooling cycle system is gathered by second pressure sensor
The pressure of tested restricting element outlet, is then passed to second controller, second controller is according to target operating condition pressure and reality
Sampled pressure carries out PID arithmetic, and then output signal is passed to the frequency converter of the second compressor, passes through the change of the second compressor
Frequency realizes the control of tested restricting element outlet pressure.
The condensing pressure of two-stage compression cooling cycle system is equal to the evaporating pressure of one stage of compression cooling cycle system simultaneously,
Therefore while the evaporating pressure of one stage of compression cooling cycle system obtains control, the condensation pressure of two-stage compression cooling cycle system
Power being controlled similarly.
By using cooperatively for one stage of compression cooling cycle system and two-stage compression cooling cycle system, by section traditionally
Fluid element Performance Test System is decomposed into high pressure and low-pressure state, and high pressure is realized by one stage of compression cooling cycle system, low pressure
Realized by two-stage compression cooling cycle system, the high pressure and low pressure operating mode that need are studied for restricting element performance test, led to
Crossing such a refrigeration system realizes independent control, and then can realize that the performance test under big pressure difference is studied.
Compared with prior art, the beneficial effects of the utility model are as follows：
The utility model controls the entrance condition state that restricting element test needs by one stage of compression cooling cycle system,
The outlet condition state that restricting element test needs is controlled by two-stage compression cooling cycle system.Single-stage pressure can so be solved
During contracting, due to test scope defect caused by the limitation of compressor itself compression ratio, the operating mode model of restricting element performance test is widened
Enclose, to restricting element test it is broader deeper into test provide technical support and guarantee.
Brief description of the drawings
Fig. 1 is a kind of schematic diagram of the Performance Test System of the big pressure difference operating mode of restricting element of the utility model.
Embodiment
Embodiment of the present utility model is described in detail below in conjunction with accompanying drawing.
Referring to Fig. 1, a kind of Performance Test System of the big pressure difference operating mode of restricting element, including it is sequentially communicated to be formed by pipeline
First compressor 1, the first oil eliminator 2, condenser 3, tested restricting element 10, the second evaporator 9, second compressor in loop
7th, the second oil eliminator 8 and the first evaporator 5.The test system also includes electric expansion valve 4, first pressure sensor 11, the
Two pressure sensors 12, the 3rd pressure sensor 13, the first controller 14, second controller 15, frequency converter 17, the 3rd controller
18th, condensing pressure control two-port valve 6, cooling water inlet pipe 18 and outlet pipe 19.
Condenser 3, the first evaporator 5 and the second evaporator 9 are equipped with cooling water inlet and coolant outlet, and cooling water enters
Mouth connects cooling water inlet pipe 18, and coolant outlet connects cooling water outlet pipe 19.The two ends of electric expansion valve 4 are connected respectively
The evaporator 5 of condensator outlet 3 and first.First pressure sensor 11 is arranged on the tested entrance of restricting element 10, the second pressure
Force snesor 12 is arranged on tested restricting element 10 and exported, and the 3rd pressure sensor 13 is arranged on the first evaporator inlet 5.
Condensing pressure control two-port valve 6 is arranged between the cooling water inlet of condenser 3 and cooling water inlet pipe 18.First
Controller 14 is electrically connected with first pressure sensor 11, condensing pressure control two-port valve 6 respectively.Second pressure sensor 12 is successively
Electrically connected with second controller 15, the compressor 7 of frequency converter 17 and second.3rd controller 16 respectively with the 3rd pressure sensor
13rd, electric expansion valve 4 is electrically connected.
The oil outlet end of first oil eliminator 2 connects the oil revolving end of the first compressor 1；The oil outlet end of second oil eliminator 8 connects
The oil revolving end of logical second compressor 7.
The tested entrance of restricting element 10 can set a pneumatic ball valve respectively with outlet, be easy to connect or change tested section
Fluid element.
First compressor 1, the first oil eliminator 2, condenser 3, the evaporator 5 of electric expansion valve 4 and first constitute one-level
Compress cooling cycle system.First compressor 1, the first oil eliminator 2, condenser 3, electric expansion valve 4, the first evaporator 5,
Two compressors 7, the second oil eliminator 8 and the second evaporator 9 constitute two-stage compression cooling cycle system.
Under high pressure operating mode, all parts work of one stage of compression cooling cycle system, and the second compressor 7, the second oil
Do not worked (refrigerant can pass through) from the evaporator 9 of device 8 and second, gathering tested restricting element 10 by first pressure sensor 11 enters
The pressure (i.e. the condensing pressure of one stage of compression refrigeration system) at mouth end, is then passed to the first controller 14, the first controller 14
PID arithmetic is carried out according to target operating condition pressure and actual samples pressure, output signal is then passed into condensing pressure control two
Port valve 6, and then realize the control of the tested inlet port pressure of restricting element 10.Meanwhile, gather one by the 3rd pressure sensor 13
The evaporating pressure of level compression cooling cycle system, is then passed to the 3rd controller 16, and the 3rd controller 16 is according to the mesh of setting
Mark evaporating pressure and actual samples pressure carries out PID arithmetic, output signal is then passed into electric expansion valve 4, and then realize
One stage of compression refrigeration system evaporating pressure is controlled.
The utility model controls the condensing pressure of one stage of compression refrigeration system to realize tested throttling by the first controller 14
The inlet pressure of element 10 is controlled, the main heat exchange by the auxiliary side of condenser 3 of control of the condensing pressure of one stage of compression refrigeration system
Amount is realized.
Under low pressure operating mode, all parts work of two-stage compression cooling cycle system is adopted by second pressure sensor 12
The pressure that the tested restricting element 10 of collection is exported, is then passed to second controller 15, second controller 15 is according to target operating condition pressure
Power and actual samples pressure carry out PID arithmetic, and then output signal is passed to the frequency converter 17 of the second compressor 7, by the
The control of the tested outlet pressure of restricting element 10 is realized in the frequency conversion of two compressors 7.
The condensing pressure of two-stage compression cooling cycle system is equal to the evaporating pressure of one stage of compression cooling cycle system simultaneously,
Therefore while the evaporating pressure of one stage of compression cooling cycle system obtains control, the condensation pressure of two-stage compression cooling cycle system
Power being controlled similarly.
By using cooperatively for one stage of compression cooling cycle system and two-stage compression cooling cycle system, by section traditionally
Fluid element Performance Test System is decomposed into high pressure and low-pressure state, and high pressure is realized by one stage of compression cooling cycle system, low pressure
Realized by two-stage compression cooling cycle system, the high pressure and low pressure operating mode that need are studied for restricting element performance test, led to
Crossing such a refrigeration system realizes independent control, and then can realize that the performance test under big pressure difference is studied.
Compared with prior art, the beneficial effects of the utility model are as follows：
The utility model controls the entrance condition state that restricting element test needs by one stage of compression cooling cycle system,
The outlet condition state that restricting element test needs is controlled by two-stage compression cooling cycle system.Single-stage pressure can so be solved
During contracting, due to test scope defect caused by the limitation of compressor itself compression ratio, the operating mode model of restricting element performance test is widened
Enclose, to restricting element test it is broader deeper into test provide technical support and guarantee.
Only as described above, the only preferred embodiment of the utility model, when the utility model can not be limited with this
The scope of implementation, i.e., generally according to simple made by the content described in the utility model claim and utility model specification
Equivalent changes and modifications, all still belongs within the utility model claim scope.In addition, summary part and title are only
For aiding in patent document search to be used, not for limiting the interest field of the utility model.
Claims (2)
1. a kind of Performance Test System of the big pressure difference operating mode of restricting element, it is characterised in that including being sequentially communicated shape by pipeline
Into first compressor in loop, the first oil eliminator, condenser, tested restricting element, the second evaporator, the second compressor, the
Two oil eliminators and the first evaporator；Also include electric expansion valve, first pressure sensor, second pressure sensor, the 3rd pressure
Force snesor, the first controller, second controller, frequency converter, the 3rd controller, condensing pressure control two-port valve, cooling water enter
Water pipe and outlet pipe；The condenser, the first evaporator and the second evaporator are equipped with cooling water inlet and coolant outlet, institute
State cooling water inlet and connect cooling water inlet pipe, the coolant outlet connects cooling water outlet pipe；The electronic expansion
Valve two ends connect condensator outlet and the first evaporator respectively；The first pressure sensor is arranged on tested restricting element
Entrance, the second pressure sensor is arranged on tested restricting element outlet；3rd pressure sensor is arranged on the first steaming
Send out device entrance；The condensing pressure control two-port valve is arranged between the cooling water inlet of condenser and cooling water inlet pipe；Institute
The first controller is stated to electrically connect with first pressure sensor, condensing pressure control two-port valve respectively；The second pressure sensor
Successively with second controller, frequency converter and the second compression mechatronics；3rd controller respectively with the 3rd pressure sensor,
Electric expansion valve is electrically connected；The oil outlet end of first oil eliminator connects the oil revolving end of the first compressor；Second oil
Oil outlet end from device connects the oil revolving end of the second compressor.
2. the Performance Test System of the big pressure difference operating mode of a kind of restricting element according to claim 1, it is characterised in that described
Tested restricting element entrance sets a pneumatic ball valve respectively with outlet.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621191805.XU CN206348131U (en) | 2016-10-28 | 2016-10-28 | A kind of Performance Test System of the big pressure difference operating mode of restricting element |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621191805.XU CN206348131U (en) | 2016-10-28 | 2016-10-28 | A kind of Performance Test System of the big pressure difference operating mode of restricting element |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206348131U true CN206348131U (en) | 2017-07-21 |
Family
ID=59316526
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621191805.XU Expired - Fee Related CN206348131U (en) | 2016-10-28 | 2016-10-28 | A kind of Performance Test System of the big pressure difference operating mode of restricting element |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206348131U (en) |
-
2016
- 2016-10-28 CN CN201621191805.XU patent/CN206348131U/en not_active Expired - Fee Related
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| CP03 | Change of name, title or address | ||
| CP03 | Change of name, title or address |
Address after: 510640 Jun Cheng Road, Whampoa District, Guangzhou, Guangdong Province, No. 16 Patentee after: GUANGZHOU LANSHI TECHNOLOGY DEVELOPMENT Co.,Ltd. Address before: 510640 F2 room 10, Lingtang Road, Xintang street, Guangzhou, Guangdong, Tianhe District Patentee before: GZ-LANS EXPERIMENTAL TECHNOLOGY Co.,Ltd. |
|
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170721 Termination date: 20211028 |