CN114354179B - Balance valve testing system and method - Google Patents
Balance valve testing system and method Download PDFInfo
- Publication number
- CN114354179B CN114354179B CN202111667610.3A CN202111667610A CN114354179B CN 114354179 B CN114354179 B CN 114354179B CN 202111667610 A CN202111667610 A CN 202111667610A CN 114354179 B CN114354179 B CN 114354179B
- Authority
- CN
- China
- Prior art keywords
- valve
- pressure
- balance
- pipe diameter
- flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Landscapes
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The invention discloses a balance valve testing system and a balance valve testing method, and belongs to the technical field of valve detection. The balance valve testing system comprises an oil tank mechanism, a first valve group mechanism, a second valve group mechanism, a differential pressure valve mechanism and an air tank; the oil tank mechanism comprises a balance valve, a second oil tank and a second oil pump, and the balance valve is respectively connected with the first valve group mechanism, the second valve group mechanism, the gas tank and the differential pressure valve mechanism; the first valve group mechanism comprises a third valve group, a fourth valve group, a balance meter and a second differential pressure transmitter, a third signal pipe valve is arranged between the first valve group mechanism and the balance valve, and the other end of the third signal pipe valve is connected with the oil tank mechanism. The invention can completely simulate the hydrogen side sealing oil circulation system of the double-flow-ring steam turbine generator unit, simulate the conditions of various working conditions such as starting, running, stopping and the like of the generator, and has reliable test and high accuracy.
Description
Technical Field
The invention relates to a balance valve testing system and a balance valve testing method, and belongs to the technical field of valve detection.
Background
The balancing valve is a regulating valve that does not require any additional energy source. The valve is arranged at the hydrogen side sealing oil position in a sealing oil system of the generator set, and one balance valve is arranged in an oil way flowing to the excitation end; the other balance valve is arranged on the oil way flowing to the steam end. In a seal oil system of a hydrogen-cooled generator, the balance between the hydrogen side oil pressure and the air side oil pressure is ensured. Therefore, the movement between the hydrogen and the empty side oil grooves can be reduced, the hydrogen can be prevented from leaking out or air is prevented from being mixed into the mechanism, and the safety and the normal operation of the generator set are ensured. Therefore, the balance valve is a very important and indispensable key device in the power generation seal oil system.
Because the valve has an important effect on the performance of the seal oil system and even the generator set, the valve needs to have high reliability, and therefore an effective test means is needed to test the valve performance.
Disclosure of Invention
The invention aims to provide a balance valve testing system and a balance valve testing method, which can truly simulate various working conditions of a double-flow-ring turbine motor sealing tile during working and are used for checking whether the performance of the balance valve can meet the requirements; the performance of the balance valve has great significance in actual operation, and for the performance measurement of the balance valve in the system, whether the balance valve can be effectively applied in an actual system or not and whether the application efficiency accords with industry standards or not are detected, so that the method has great significance in the judgment and subsequent adjustment of the actual application of the balance valve.
A first object of the present invention is to provide a balance valve testing system including an oil tank mechanism, a first valve group mechanism, a second valve group mechanism, a differential pressure valve mechanism, and a gas tank; the oil tank mechanism comprises a balance valve, a second oil tank and a second oil pump, and the balance valve is respectively connected with the first valve group mechanism, the second valve group mechanism, the gas tank and the differential pressure valve mechanism; the first valve group mechanism comprises a third valve group, a fourth valve group, a balance meter and a second differential pressure transmitter, a third signal pipe valve is arranged between the first valve group mechanism and the balance valve, and the other end of the third signal pipe valve is connected with the oil tank mechanism; the second valve group mechanism comprises a first valve group, a second valve group, a differential pressure meter and a first differential pressure transmitter, one end of the second valve group mechanism is connected with the gas tank through a first signal pipe valve, and the other end of the second valve group mechanism is connected with the balance valve through a fourth signal pipe valve; the differential pressure valve mechanism comprises a differential pressure valve and a first oil tank, wherein the differential pressure valve is communicated with the first oil tank, and the differential pressure valve mechanism is also communicated with the gas tank.
In one embodiment of the invention, the air tank is filled with lubricating oil, and the differential pressure valve is connected with lubricating oil at the lower part of the air tank; the air tank is provided with a fifth pressure gauge, a fifth pressure transmitter, a first exhaust valve and a second air inlet valve, and the second air inlet valve is connected with an air compressor; the air tank is connected with the second oil tank through a pipeline, and a first air inlet valve and a second air outlet valve are arranged on the pipeline between the air tank and the second oil tank; the second oil tank is provided with a first liquid level meter; and a second liquid level meter is arranged on the gas tank.
In one embodiment of the invention, the balance meter is connected with the second differential pressure transmitter through a pipeline, and a third valve group and a fourth valve group are arranged on the pipeline between the balance meter and the second differential pressure transmitter; the differential pressure meter is connected with the first differential pressure transmitter through a pipeline, and a first valve bank and a second valve bank are arranged on the pipeline between the differential pressure meter and the first differential pressure transmitter.
In one embodiment of the invention, the second oil tank is connected with the second oil pump through a pipeline, a second inlet valve and a fourth filter are arranged between the second oil tank and the second oil pump, the second oil pump is connected with a second check valve, the second check valve is connected with the balance valve through a pipeline, and a second thermometer, a third pressure gauge, a second platinum thermal resistor, a third pressure transmitter and a first inlet valve are arranged between the second check valve and the balance valve; the second oil pump is also connected with a second bypass valve; an outlet valve, a third filter, a fourth pressure transmitter, a fourth pressure gauge, a second flow transmitter and a second flow regulating valve are arranged between the balance valve and the second oil tank.
In one embodiment of the invention, the differential pressure valve is communicated with the first oil tank through three pipelines, and the first pipeline is directly communicated with the differential pressure valve and the first oil tank; the second pipeline is provided with a second valve, a second signal pipe valve, a second pressure transmitter, a second pressure gauge, a second filter, a first flow transmitter and a first flow regulating valve, and the second signal pipe valve is communicated with the balance valve; the third pipeline is provided with a first valve, a first filter, a first pressure transmitter, a first platinum thermal resistor, a first pressure gauge, a first check valve and a first oil pump.
In one embodiment of the invention, the third pipeline is further provided with a branch pipe, the branch pipe is provided with a first bypass valve, one end of the first bypass valve is connected to the third pipeline, and the other end of the first bypass valve is communicated with the first oil tank.
In one embodiment of the invention, the balance valve comprises two types of through diameters, wherein the balance valve with one type of through diameter adopts the pipe diameter of DN25, and the balance valve with the other type of through diameter adopts the pipe diameter of DN 40.
The second object of the invention is to provide a balance valve testing method, which comprises a balance valve single machine test and a balance valve and differential pressure valve linkage test.
In one embodiment of the present invention, the balanced valve stand-alone test comprises the steps of:
s1, static test is carried out to simulate the static working condition of a generator;
starting a second oil pump, and adjusting a second bypass valve to enable the outlet pressure of the second oil pump, namely the numerical value of a third pressure gauge, to be 0.15MPa when the pipe diameter DN25 is provided, and to be 0.2MPa when the pipe diameter DN40 is provided; starting an air compressor to charge air into the air tank BB003 to 84KPa when the pipe diameter DN25 is reached, and to charge air into 100KPa when the pipe diameter DN40 is reached; the second flow regulating valve is regulated, so that the second flow transmitter displays the flow as 19L/min when the pipe diameter DN25 is provided, and 83L/min when the pipe diameter DN40 is provided; closing the middle valves of the third valve group and the fourth valve group, observing the differential pressure value of the balance valve, and if the differential pressure value exceeds +/-490 Pa, opening a protective cover at the bottom of the balance valve, and adjusting a fine adjustment bolt to ensure that the balance accuracy meets the technical requirement; adjusting the second bypass valve to enable the outlet pressure of the third pressure gauge on the second oil pump to be 0.15Mpa when the pipe diameter DN25 is used; when the pipe diameter DN40 is respectively 0.2Mpa, 0.3Mpa, 0.4Mpa, 0.5Mpa and 0.62Mpa, corresponding second flow transmitter flow, balance accuracy of the balance meter and values of air side oil pressure of the fifth pressure meter, namely pressure of a gas tank, hydrogen side oil pressure of the fourth pressure meter and hydrogen side oil temperature of the second platinum thermal resistor are recorded; the qualification requirements are as follows: under the condition that the flow of the balance valve is kept unchanged at the maximum, the pressure balance value of the balance valve is required to be within a range of +/-490 Pa pressure difference in the whole pressure increasing and reducing process;
s2, a dynamic test is performed to simulate the working condition of the generator during rotation;
starting a second oil pump, and adjusting a second bypass valve to enable the outlet pressure of the second oil pump, namely the numerical value of a third pressure gauge, to be 0.15MPa when the pipe diameter DN25 is provided, and to be 0.2MPa when the pipe diameter DN40 is provided; starting an air compressor to charge the air tank to 84KPa when the pipe diameter DN25 is reached, and 100KPa when the pipe diameter DN40 is reached; the second flow regulating valve is regulated, so that the second flow transmitter displays that the flow is 19L/min when the pipe diameter DN25 is provided and 83L/min when the pipe diameter DN40 is provided; closing the middle valves of the third valve group and the fourth valve group, observing the differential pressure value of the balance valve, and if the differential pressure value exceeds +/-490 Pa, opening a protective cover at the bottom of the balance valve, and adjusting a fine adjustment bolt to ensure that the balance accuracy meets the technical requirement; the second flow regulating valve is regulated to enable the flow of the second flow transmitter to be 8L/min when the pipe diameter DN25 is provided, and be 16L/min, 19L/min, 25L/min, 30L/min, 50L/min and 83L/min when the pipe diameter DN40 is provided, and the balance pressure difference of the balance meter under the corresponding flow of the second flow transmitter, the air side oil pressure of the fifth pressure meter, the hydrogen side oil pressure of the fourth pressure meter and the hydrogen side oil temperature of the second platinum thermal resistor are recorded; in the test process, along with the change of the flow of the balance valve, the outlet pressure of the second oil pump, namely the numerical value of the third pressure gauge, is also changed, when the flow is set, the second bypass valve is properly adjusted in a fine mode, and the outlet pressure of the second oil pump is controlled to be 0.15MPa when the pipe diameter DN25 is kept, and 0.2MPa when the pipe diameter DN40 is kept; the qualification requirements are as follows: under the condition that the oil-hydrogen pressure difference is kept unchanged, the pressure balance value of the balance valve needs to be within the range of +/-490 Pa pressure difference in the whole flow rising and falling process.
In one embodiment of the invention, the balance valve and differential pressure valve linkage test is used for simulating the normal operation condition of the generator, and comprises the following steps:
the differential pressure valve is put into, the first oil pump is started, the first bypass valve of the first oil pump is gradually closed, and the first flow regulating valve is regulated to enable the flow of the first flow transmitter to be 50L/min; closing intermediate valves of the first three valve group and the second three valve group, and rotating an adjusting bolt at the top of the differential pressure valve to enable a differential pressure meter to display that the differential pressure is 84Kpa when the pipe diameter DN25 is the pipe diameter DN40 and is 100Kpa when the pipe diameter DN40 is the pipe diameter DN 40; the balance valve is put into, the second oil pump is started, the second bypass valve is regulated to enable the outlet pressure of the second oil pump, namely the numerical value of the third pressure gauge, to be 0.6Mpa when the pipe diameter DN25 is provided, and 1.1Mpa when the pipe diameter DN40 is provided; the second flow regulating valve is regulated to enable the flow of the second flow transmitter to be 8L/min when the pipe diameter DN25 is provided, and 16L/min when the pipe diameter DN40 is provided; closing the middle valves of the third valve group and the fourth valve group, observing the balance pressure difference value of the balance valve, and if the balance pressure difference value exceeds +/-490 Pa, opening a protective cover at the bottom of the balance valve, and adjusting a fine adjustment bolt to enable the balance pressure difference value to meet the technical requirements; starting an air compressor to pressurize the air tank, wherein the pressure of the fifth pressure gauge is respectively 0.05MPa, 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa and 0.5MPa when the pipe diameter DN25 is adopted; or the pressure of the fifth pressure gauge is respectively 0.05MPa, 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa, 0.5MPa and 0.6MPa when the pipe diameter DN40 is used, and the barometric pressure value of the fifth pressure gauge, the air side oil pressure of the second pressure gauge, the differential pressure valve oil-hydrogen differential pressure of the differential pressure gauge, the outlet pressure of the hydrogen side oil pump of the third pressure gauge, the hydrogen side oil pressure of the fourth pressure gauge, the hydrogen side oil temperature of the second platinum thermal resistor, the balance valve flow of the second flow transmitter and the balance pressure of the balance gauge are recorded; closing the air compressor and the second air inlet valve, opening the first air outlet valve for exhausting, wherein the pressure of the fifth pressure gauge is respectively 0.5MPa, 0.4MPa, 0.3MPa, 0.2MPa, 0.1MPa and 0.05MPa when the pipe diameter DN25 is adopted; or the pressure of the fifth pressure gauge PI505 is respectively 0.6MPa, 0.5MPa, 0.4MPa, 0.3MPa, 0.2MPa, 0.1MPa and 0.05MPa when the pipe diameter DN40 is used, and various values are recorded; the second flow regulating valve is regulated to ensure that the flow of the second flow transmitter is 8L/min, 16L/min, 19L/min and 25L/min respectively when the pipe diameter DN25 is adopted; when the pipe diameter DN40 is 30L/min, 50L/min and 83L/min, repeating the steps of air pressure filling and air pressure reducing for test and recording; in the test process, along with the change of the flow of the balance valve, the third pressure gauge of the outlet pressure of the oil pump also changes, and when the flow is set, the second bypass valve is properly adjusted in a fine mode, and the outlet pressure of the oil pump at the hydrogen side is controlled to be 0.6Mpa when the pipe diameter DN25 is set; the pipe diameter DN40 is 1.1Mpa; the qualification requirements are as follows: under the condition that the oil-hydrogen pressure difference is kept unchanged, the pressure balance value of the balance valve is required to be within the range of +/-490 Pa in the rising and falling processes of the pressure in the engine at each balance valve flow check point.
Advantageous effects
1. The invention completely simulates the hydrogen side sealing oil circulation system of the double-flow ring steam turbine generator unit, simulates the conditions of various working conditions such as generator starting, running, stopping and the like, and has comprehensive detection range; compared with the prior art, the system increases the digital output to the microcomputer, and is helpful for rapidly analyzing the cause of the valve problem.
2. The balance valve detected by the invention accords with the blank hydrogen side pressure difference value of +/-490 Pa (+ -50 mmH 20) in the practical application in a power plant; the oil channeling of the empty hydrogen side of the sealing tile is prevented, and the reliable operation of the unit is ensured.
3. In order to ensure the accuracy of the balance valve test, the balance valve and the differential pressure valve are subjected to linkage test, so that the system is matched with the system of the generator, the test is reliable, and the accuracy is high.
Drawings
FIG. 1 is a diagram of a stand-alone balanced valve test system of example 1;
FIG. 2 is a diagram of a system for testing the linkage of the balance valve and the differential pressure valve in the embodiment 2;
wherein: AP 003-air compressor, AA 300-second intake valve, LI 502-second level gauge, AA 501-first exhaust valve, BB 003-gas tank, PI 505-fifth pressure gauge, PT 105-fifth pressure transmitter, AA 301-first signal pipe valve, AP 001-first oil pump, AA 201-first check valve, AA 001-first bypass valve, BB 001-first tank, TI 501-first thermometer, PI 501-first pressure gauge, CT 101-first platinum thermal resistor, PT 101-first pressure transmitter, AT 001-first filter, AA 002-first valve, AA 003-second valve, AA 101-pressure difference valve, AA 303-second signal pipe valve, PT 102-second pressure transmitter, PI 502-second pressure gauge, AT 002-second filter, FT 101-first flow transmitter, AA 141-first flow regulating valve, PDI 506-differential pressure gauge, AA 306-first third valve bank, AA 307-second third valve bank, PDT 106-first differential pressure transmitter, PDI 507-balance gauge, AA 308-third valve bank, AA 309-fourth third valve bank, PDT 107-second differential pressure transmitter, AA 305-fourth signal tube valve, AA 304-third signal tube valve, AA 007-outlet valve, AT 003-third filter, PT 104-fourth pressure transmitter, AA 121-balance valve, PI 504-fourth pressure gauge, FT 102-second flow transmitter, AA 006-first inlet valve, AA 142-second flow regulator valve, CT 102-second platinum thermal resistor, PT 103-third pressure transmitter, PI 503-third pressure gauge, TI 502-second thermometer, AA 005-second bypass valve, AA 202-second check valve, AP 002-second oil pump, AC 001-fourth filter, AA 004-second inlet valve, BB 002-second oil tank, AA 302-first air inlet valve, AA 502-second air outlet valve, LI 501-first liquid level meter.
Detailed Description
The present invention will be further described in detail below with reference to specific embodiments and with reference to the accompanying drawings, in order to make the objects, technical solutions and advantages of the present invention more apparent. Wherein like parts are designated by like reference numerals. It should be noted that the words "front", "rear", "left", "right", "upper" and "lower" used in the following description refer to directions in the drawings. The words "inner" and "outer" are used to refer to directions toward or away from, respectively, the geometric center of a particular component.
Example 1
The embodiment provides a balance valve testing system, as shown in fig. 1, comprising a first three-valve group mechanism, an oil tank mechanism and an air tank BB003, wherein the oil tank mechanism comprises a balance valve AA121, and the balance valve AA121 is respectively connected with the first three-valve group mechanism and the air tank BB 003;
the first valve group mechanism comprises a third valve group AA308, a fourth valve group AA309, a balance meter PDI507 and a second pressure difference transmitter PDT107, wherein the balance meter PDI507 is connected with the second pressure difference transmitter PDT107 through a pipeline, and the third valve group AA308 and the fourth valve group AA309 are arranged on the pipeline between the balance meter PDI507 and the second pressure difference transmitter PDT 107; the first valve group mechanism is connected with the balance valve AA121 through a pipeline, a third signal pipe valve AA304 is arranged on the pipeline between the first valve group mechanism and the balance valve AA121, and the other end of the third signal pipe valve AA304 is connected with the oil tank mechanism;
the oil tank mechanism further comprises a second oil tank BB002 and a second oil pump AP002, wherein the second oil tank BB002 is connected with the second oil pump AP002 through a pipeline, a second inlet valve AA004 and a fourth filter AC001 are arranged between the second oil tank BB002 and the second oil pump AP002, the second oil pump AP002 is connected with a second check valve AA202, the second check valve AA202 is connected with a balance valve AA121 through a pipeline, and a second thermometer TI502, a third pressure gauge PI503, a second platinum thermal resistor CT102, a third pressure transmitter PT103 and a first inlet valve AA006 are arranged between the second check valve AA202 and the balance valve AA 121; the second oil pump AP002 is also connected with a second bypass valve AA005, and the second bypass valve AA005 is used for adjusting pressure; an outlet valve AA007, a third filter AT003, a fourth pressure transmitter PT104, a fourth pressure gauge PI504, a second flow transmitter FT102 and a second flow regulating valve AA142 are arranged between the balance valve AA121 and the second oil tank BB 002.
Further, the gas tank BB003 is connected to the second oil tank BB002 through a pipe, and a first gas inlet valve AA302 and a second gas outlet valve AA502 are provided on the pipe between the gas tank BB003 and the second oil tank BB 002.
Further, the balance valve AA121 is connected to the gas tank BB003 through a pipe, and a first signal pipe valve AA301 and a fourth signal pipe valve AA305 are disposed on the pipe between the balance valve AA121 and the gas tank BB 003.
Further, a first level gauge LI501 is provided on the second tank BB 002; a second level gauge LI502 is provided on the tank BB 003.
Further, a fifth pressure gauge PI505, a fifth pressure transmitter PT105, a first exhaust valve AA501, and a second intake valve AA300 are further provided on the air tank BB003, and the second intake valve AA300 is connected to an air compressor AP003.
Example 2
As shown in fig. 2, this embodiment differs from embodiment 1 in that it further includes a differential pressure valve mechanism and a second three-valve group mechanism, the second three-valve group mechanism being respectively communicated with the balance valve AA121 and the gas tank BB003, the differential pressure valve mechanism being respectively communicated with the balance valve AA121 and the gas tank BB 003;
the second valve group mechanism comprises a differential pressure meter PDI506 and a first differential pressure transmitter PDT106, the differential pressure meter PDI506 and the first differential pressure transmitter PDT106 are connected through a pipeline, a first valve group AA306 and a second valve group AA307 are arranged on a pipeline between the differential pressure meter PDI506 and the first differential pressure transmitter PDT106, one end of the second valve group mechanism is connected into a gas tank BB003 through a first signal pipe valve AA301, and the other end of the second valve group mechanism is connected into a balance valve AA121 through a fourth signal pipe valve AA305.
The differential pressure valve mechanism comprises a differential pressure valve AA101 and a first oil tank BB001, the differential pressure valve AA101 is communicated with the first oil tank BB001 through three pipelines, and the first pipeline is directly communicated with the differential pressure valve AA101 and the first oil tank BB001; the second pipeline is provided with a second valve AA003, a second signal pipe valve AA303, a second pressure transmitter PT102, a second pressure gauge PI502, a second filter AT002, a first flow transmitter FT101 and a first flow regulating valve AA141, and the second signal pipe valve AA303 is communicated with a balance valve AA 121; be equipped with first valve AA002, first filter AT001, first pressure transmitter PT101, first platinum thermal resistor CT101, first manometer PI501, first check valve AA201 and first oil pump AP001 on the third pipeline, still be equipped with a branch pipe on the third pipeline, be equipped with first bypass valve AA001 on the branch pipe, the one end of first bypass valve AA001 is inserted on the third pipeline, and the other end communicates with first oil tank BB 001.
Further, the tank BB003 is filled with lubricating oil, and the differential pressure valve AA101 is connected to the lubricating oil at the lower part of the tank BB003 through a gas pressure signal pipe and a first signal pipe valve AA 301.
Furthermore, the control switch instruction of each instrument and meter, the pressure of the sampling signal, the pressure difference and the flow are all input to the microcomputer by the PLC.
Further, the balancing valve AA121 includes two kinds of diameters, wherein the balancing valve AA121 with one kind of diameter selects the diameter of DN25, and the balancing valve AA121 with the other kind of diameter selects the diameter of DN 40.
Example 3
The present embodiment provides a balanced valve testing method that first performs a test preparation including that all instruments must be within a valid period of validity before the balanced valve testing method performs a test. The test station meter power is turned on to check whether the displays of the flow transmitters FT101, FT102, pressure transmitters PT101, PT102, PT103, PT104, PT105 and differential pressure transmitters PDT106, PDT107 are correct (see FIG. 2 for details), and the display should be initially shown as follows: PT105 is 0.005MPa, the others are 0. Checking whether each valve of the test device is normally opened or closed. It is checked whether the oil level in the oil tank BB002, the gas tank BB003 is at the intermediate position shown by the level gauges LI501 and LI502.
The appearance and the cleanliness of the tested balance valve are primarily checked, the appearance size and the installation correctness of each part are checked by referring to the drawing, the outer surface is free from collision, the sealing surface is free from scratch, the cleaning of internal parts is required to be ensured before the valve is tested, and the damage or the impurity entering the testing device is prevented.
The balance test method comprises a balance valve single machine test and a balance valve and differential pressure valve linkage test.
The balance valve single machine test comprises the following steps:
the presetting of the valves is shown in fig. 1, the second bypass valve AA005 of the second oil pump AP002 is opened (closing can increase the outlet pressure of the oil pump, otherwise, decrease), the first inlet valve AA006, the outlet valve AA007, the third signal pipe valve AA304 and the fourth signal pipe valve AA305 of the balance valve AA121 are opened, the second inlet valve AA004 is opened, the first exhaust valve AA501 on the gas tank BB003 and the first intake valve AA302 of the second oil tank BB002 are closed, and the second exhaust valve AA502 is opened; the second flow regulating valve AA142 is in the neutral position (closing off flow decreases, whereas flow increases); the trimming bolt on the balancing valve AA121 is at the middle position; the pressure gauge isolation valves and the valves of the third valve group AA308 and the fourth valve group AA309 are opened.
S1, static test is carried out to simulate the static working condition of a generator;
the balance valve static test is to check the regulation performance of the balance valve on the outlet pressure by changing the inlet pressure (third pressure transmitter PT 103/third pressure gauge PI 503) of the balance valve under the condition that the maximum flow rate of the balance valve is 19L/min at the pipe diameter DN25 and 83L/min at the pipe diameter DN 40.
Starting the second oil pump AP002, and adjusting the second bypass valve AA005 to enable the outlet pressure of the second oil pump AP002, namely the numerical value of the third pressure gauge PI503 to be 0.15MPa when the pipe diameter DN25 is provided, and 0.2MPa when the pipe diameter DN40 is provided; starting an air compressor AP003 to charge air tank BB003 to 84KPa when the pipe diameter DN25 is reached, and to 100KPa when the pipe diameter DN40 is reached; adjusting the second flow regulating valve AA142 to enable the second flow transmitter FT102 to display that the flow is 19L/min when the pipe diameter DN25 is the flow and 83L/min when the pipe diameter DN40 is the flow; closing intermediate valves of a third valve group AA308 and a fourth valve group AA309, observing the differential pressure value of the balance valve, and opening a protective cover at the bottom of the balance valve if the differential pressure value exceeds +/-490 Pa (+/-50 mmH 20), and adjusting the fine tuning bolts to ensure that the balance accuracy meets the technical requirements (the fine tuning bolts cannot be adjusted in the formal test process); adjusting the second bypass valve AA005 to enable the outlet pressure of the third pressure gauge PI503 on the second oil pump AP002 to be 0.15Mpa when the pipe diameter DN25 is used; when the pipe diameter DN40 is respectively 0.2Mpa, 0.3Mpa, 0.4Mpa, 0.5Mpa and 0.62Mpa, corresponding flow rate of the second flow transmitter FT102 (if the flow rate is changed, the flow rate is adjusted to 19/83L/min by adjusting the second flow rate adjusting valve AA 142), balance accuracy of the balance meter PDI507, and values of air side oil pressure of the fifth pressure meter PI505, namely pressure of the air tank BB003, hydrogen side oil pressure of the fourth pressure meter PI504 and hydrogen side oil temperature of the second platinum thermal resistor CT102 are recorded; the qualification requirements are as follows: under the condition that the flow of the balance valve is kept to be the largest, the pressure balance value of the balance valve needs to be within a range of +/-490 Pa pressure difference in the whole pressure increasing and reducing process.
S2, a dynamic test is performed to simulate the working condition of the generator during rotation;
dynamic testing of the balance valve is to verify the regulation performance of the balance valve for outlet pressure in a designed flow range by changing the flow through the balance valve under the condition that the balance valve is limited to rated oil-hydrogen pressure difference.
Starting the second oil pump AP002, and adjusting the second bypass valve AA005 to enable the outlet pressure of the second oil pump AP002, namely the numerical value of the third pressure gauge PI503 to be 0.15MPa when the pipe diameter DN25 is provided, and 0.2MPa when the pipe diameter DN40 is provided; starting an air compressor AP003 to charge air tank BB003 to 84KPa when the pipe diameter DN25 is reached, and to 100KPa when the pipe diameter DN40 is reached; adjusting the second flow regulating valve AA142 to enable the second flow transmitter FT102 to display that the flow is 19L/min when the pipe diameter DN25 is the flow and 83L/min when the pipe diameter DN40 is the flow; closing intermediate valves of a third valve group AA308 and a fourth valve group AA309, observing the differential pressure value of the balance valve, and opening a protective cover at the bottom of the balance valve if the differential pressure value exceeds +/-490 Pa (+/-50 mmH 20), and adjusting the fine tuning bolts to ensure that the balance accuracy meets the technical requirements (the fine tuning bolts cannot be adjusted in the formal test process); the second flow regulating valve AA142 is regulated to enable the flow of the second flow transmitter FT102 to be 8L/min when the pipe diameter DN25 is provided, and the flow of the second flow transmitter FT102 is 16L/min, 19L/min, 25L/min, 30L/min, 50L/min and 83L/min when the pipe diameter DN40 is provided, and the balance pressure difference of a balance meter PDI507 and the values of the air side oil pressure of a fifth pressure meter PI505, the hydrogen side oil pressure of a fourth pressure meter PI504 and the hydrogen side oil temperature of a second platinum thermal resistor CT102 under the corresponding flow of the second flow transmitter FT102 are recorded; in the test process, along with the change of the flow of the balance valve, the outlet pressure of the second oil pump AP002, namely the numerical value of the third pressure gauge PI503, is also changed, when the flow is set, the second bypass valve AA005 can be properly adjusted, and the outlet pressure of the second oil pump AP002 is controlled to be 0.15MPa when the pipe diameter DN25 is kept, and 0.2MPa when the pipe diameter DN40 is kept; the qualification requirements are as follows: under the condition that the oil-hydrogen pressure difference is kept unchanged, the pressure balance value of the balance valve needs to be within the range of +/-490 Pa pressure difference in the whole flow rising and falling process.
S3, data deviation and problem analysis;
if the balance valve is problematic, static tests may meet, and overscaling may occur in dynamic tests. If the equilibrium threshold bias or tuning performance is too poor during the test, it is possible that: the piston in the balance valve is blocked by impurities in the oil, and the piston is necessary to be disassembled and cleaned and then tested; the balance valve is poor in quality, and if burrs are found during disassembly, the surface of the casting is not cleaned, and the phenomena of scratches, bruise and napping are caused, the casting needs to be treated or repaired. Of particular note is: the balance valve differential pressure regulating valve with poor response performance may exceed the standard at the final factory test.
The balance valve and differential pressure valve linkage test is used for simulating the normal operation condition of the generator and comprises the following steps:
the differential pressure valve AA101 is qualified in a single-machine test, the preset settings of all valves of a differential pressure valve AA101 test system are shown in FIG. 2, and a first bypass valve AA001 of a first oil pump AP001 is opened, wherein the first valve AA002, a second valve AA003, a first signal pipe valve AA301, a second signal pipe valve AA303, a first valve group AA306 and a second valve group AA307 of the differential pressure valve AA101 are respectively opened, and all valves and meters are respectively arranged; the first air inlet valve AA302 of the second oil tank BB002 and the second air inlet valve AA306 of the air tank BB003 are opened, and the first air outlet valve AA501 and the second air outlet valve AA502 are closed; the first flow rate adjustment valve AA141 is in the neutral position; the differential pressure valve adjusting screw is adjusted to be the uppermost; the presetting of the valves of the balance valve AA121 test system is shown in FIG. 2, the second bypass valve AA005 of the second oil pump AP002 is opened (the first inlet valve AA006 of the balance valve, the outlet valve AA007 of the balance valve and the second inlet valve AA004 of the second oil pump AP002 are reduced, the third signal pipe valve AA304, the fourth signal pipe valve AA305, the third valve group AA308, the fourth valve group AA309 and the instrument isolation valves are opened, the second flow regulating valve AA142 is in the middle position (the flow is reduced, the flow is increased), and the balance valve trimming bolt is in the middle position.
The differential pressure valve AA101 is put into, the first oil pump AP001 is started, the first bypass valve AA001 of the first oil pump AP001 is gradually closed, and the first flow regulating valve AA141 is regulated to enable the flow of the first flow transmitter FT101 to be 50L/min; closing intermediate valves of the first valve group AA306 and the second valve group AA307, and rotating a top adjusting bolt of the differential pressure valve AA101 (the pressure difference of a main pipeline is increased when the pressure is downwards pressed, and conversely, the pressure difference is reduced), so that a differential pressure table PDI506 displays that the pressure difference is 84Kpa when the pipe diameter DN25 is the pipe diameter, and is 100Kpa when the pipe diameter DN40 is the pipe diameter; the balance valve is put in, the second oil pump AP002 is started, the second bypass valve AA005 is regulated to enable the outlet pressure of the second oil pump AP002, namely the numerical value of the third pressure gauge PI503, to be 0.6Mpa when the pipe diameter DN25 is provided, and 1.1Mpa when the pipe diameter DN40 is provided; the second flow rate adjusting valve AA142 is adjusted to enable the flow rate of the second flow rate changer FT102 to be 8L/min when the pipe diameter DN25 is used and 16L/min when the pipe diameter DN40 is used; closing intermediate valves of a third valve group AA308 and a fourth valve group AA309, observing balance pressure difference values of the balance valves, and if the balance pressure difference values exceed +/-490 Pa (+/-50 mmH 20), opening a protective cover at the bottom of the balance valve, and adjusting the fine tuning bolts to enable the balance pressure difference to meet the technical requirements (the fine tuning bolts cannot be adjusted in the formal test process); starting an air compressor AP003 to pressurize a gas tank BB003, wherein the pressure of a fifth pressure gauge PI505 is respectively 0.05MPa, 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa and 0.5MPa when the pipe diameter DN25 is adopted; or the pressure of the fifth pressure gauge PI505 is respectively 0.05MPa, 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa, 0.5MPa and 0.6MPa when the pipe diameter DN40 is used, the air pressure value of the fifth pressure gauge PI505, the air side oil pressure of the second pressure gauge PI502, the differential valve oil-hydrogen pressure difference of the differential pressure gauge PDI506, the outlet pressure of the hydrogen side oil pump of the third pressure gauge PI503, the hydrogen side oil pressure of the fourth pressure gauge PI504, the hydrogen side oil temperature of the second platinum resistor CT102, the balance valve flow of the second flow transmitter FT102 and the balance pressure difference of the balance gauge PDI507 are recorded; closing the air compressor AP003 and the second air inlet valve AA300, opening the first air outlet valve AA501 for exhausting, wherein the pressure of the fifth pressure gauge PI505 is respectively 0.5MPa, 0.4MPa, 0.3MPa, 0.2MPa, 0.1MPa and 0.05MPa when the pipe diameter DN25 is adopted; or the pressure of the fifth pressure gauge PI505 is respectively 0.6MPa, 0.5MPa, 0.4MPa, 0.3MPa, 0.2MPa, 0.1MPa and 0.05MPa when the pipe diameter DN40 is used, and various values are recorded; the second flow regulating valve AA142 is regulated, so that the flow of the second flow transducer FT102 is respectively 8L/min, 16L/min, 19L/min and 25L/min when the pipe diameter DN25 is used; when the pipe diameter DN40 is 30L/min, 50L/min and 83L/min, repeating the steps of air pressure filling and air pressure reducing for test and recording; in the test process, along with the change of the flow of the balance valve, the third pressure gauge PI503 of the outlet pressure of the oil pump also changes, and when the flow is set, the second bypass valve AA005 is properly adjusted, and the outlet pressure of the oil pump at the hydrogen side is controlled to be 0.6Mpa when the pipe diameter DN25 is set; the pipe diameter DN40 is 1.1Mpa; the qualification requirements are as follows: under the condition that the oil-hydrogen pressure difference is kept unchanged, the pressure balance value of the balance valve is required to be within the range of +/-490 Pa in the rising and falling processes of the pressure in the engine at each balance valve flow check point.
Although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the embodiments described, or equivalents may be substituted for elements thereof, and any modifications, equivalents, improvements and similar elements thereof may be made without departing from the spirit and principles of the present invention.
Claims (2)
1. A balance valve test method is characterized in that a balance valve test system is applied, and comprises a balance valve single machine test and a balance valve and differential pressure valve linkage test;
the balance valve testing system comprises an oil tank mechanism, a first valve group mechanism, a second valve group mechanism, a differential pressure valve mechanism and an air tank;
the oil tank mechanism comprises a balance valve, a second oil tank and a second oil pump, and the balance valve is respectively connected with the first valve group mechanism, the second valve group mechanism, the gas tank and the differential pressure valve mechanism;
the first valve group mechanism comprises a third valve group, a fourth valve group, a balance meter and a second differential pressure transmitter, a third signal pipe valve is arranged between the first valve group mechanism and the balance valve, and the other end of the third signal pipe valve is connected with the oil tank mechanism;
the second valve group mechanism comprises a first valve group, a second valve group, a differential pressure meter and a first differential pressure transmitter, one end of the second valve group mechanism is connected with the gas tank through a first signal pipe valve, and the other end of the second valve group mechanism is connected with the balance valve through a fourth signal pipe valve;
the differential pressure valve mechanism comprises a differential pressure valve and a first oil tank, the differential pressure valve is communicated with the first oil tank, and the differential pressure valve mechanism is also communicated with the air tank;
the air tank is filled with lubricating oil, and the differential pressure valve is connected with lubricating oil at the lower part of the air tank; the air tank is provided with a fifth pressure gauge, a fifth pressure transmitter, a first exhaust valve and a second air inlet valve, and the second air inlet valve is connected with an air compressor; the air tank is connected with the second oil tank through a pipeline, and a first air inlet valve and a second air outlet valve are arranged on the pipeline between the air tank and the second oil tank; the second oil tank is provided with a first liquid level meter; a second liquid level meter is arranged on the gas tank;
the balance meter is connected with the second differential pressure transmitter through a pipeline, and a third valve bank and a fourth valve bank are arranged on the pipeline between the balance meter and the second differential pressure transmitter; the differential pressure meter is connected with the first differential pressure transmitter through a pipeline, and a first three-valve group and a second three-valve group are arranged on the pipeline between the differential pressure meter and the first differential pressure transmitter;
the second oil tank is connected with a second oil pump through a pipeline, a second inlet valve and a fourth filter are arranged between the second oil tank and the second oil pump, the second oil pump is connected with a second check valve, the second check valve is connected with a balance valve through a pipeline, and a second thermometer, a third pressure gauge, a second platinum thermal resistor, a third pressure transmitter and a first inlet valve are arranged between the second check valve and the balance valve; the second oil pump is also connected with a second bypass valve; an outlet valve, a third filter, a fourth pressure transmitter, a fourth pressure gauge, a second flow transmitter and a second flow regulating valve are arranged between the balance valve and the second oil tank;
the differential pressure valve is communicated with the first oil tank through three pipelines, and the first pipeline is directly communicated with the differential pressure valve and the first oil tank; the second pipeline is provided with a second valve, a second signal pipe valve, a second pressure transmitter, a second pressure gauge, a second filter, a first flow transmitter and a first flow regulating valve, wherein the second signal pipe valve is communicated with the balance valve; the third pipeline is provided with a first valve, a first filter, a first pressure transmitter, a first platinum thermal resistor, a first pressure gauge, a first check valve and a first oil pump;
the third pipeline is also provided with a branch pipe, a first bypass valve is arranged on the branch pipe, one end of the first bypass valve is connected to the third pipeline, and the other end of the first bypass valve is communicated with the first oil tank;
the balance valve comprises two specification diameters, wherein the balance valve with one specification diameter adopts the diameter of DN25, and the balance valve with the other specification diameter adopts the diameter of DN 40;
the balance valve and differential pressure valve linkage test is used for simulating the normal operation condition of the generator and comprises the following steps:
the differential pressure valve is put into, the first oil pump is started, the first bypass valve of the first oil pump is gradually closed, and the first flow regulating valve is regulated to enable the flow of the first flow transmitter to be 50L/min; closing intermediate valves of the first three valve group and the second three valve group, and rotating an adjusting bolt at the top of the differential pressure valve to enable a differential pressure meter to display that the differential pressure is 84Kpa when the pipe diameter DN25 is the pipe diameter DN40 and is 100Kpa when the pipe diameter DN40 is the pipe diameter DN 40; the balance valve is put into, the second oil pump is started, the second bypass valve is regulated to enable the outlet pressure of the second oil pump, namely the numerical value of the third pressure gauge, to be 0.6Mpa when the pipe diameter DN25 is provided, and 1.1Mpa when the pipe diameter DN40 is provided; the second flow regulating valve is regulated to enable the flow of the second flow transmitter to be 8L/min when the pipe diameter DN25 is provided, and 16L/min when the pipe diameter DN40 is provided; closing the middle valves of the third valve group and the fourth valve group, observing the balance pressure difference value of the balance valve, and if the balance pressure difference value exceeds +/-490 Pa, opening a protective cover at the bottom of the balance valve, and adjusting a fine adjustment bolt to enable the balance pressure difference value to meet the technical requirements; starting an air compressor to pressurize the air tank, wherein the pressure of the fifth pressure gauge is respectively 0.05MPa, 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa and 0.5MPa when the pipe diameter DN25 is adopted; or the pressure of the fifth pressure gauge is respectively 0.05MPa, 0.1MPa, 0.2MPa, 0.3MPa, 0.4MPa, 0.5MPa and 0.6MPa when the pipe diameter DN40 is used, and the barometric pressure value of the fifth pressure gauge, the air side oil pressure of the second pressure gauge, the differential pressure valve oil-hydrogen differential pressure of the differential pressure gauge, the outlet pressure of the hydrogen side oil pump of the third pressure gauge, the hydrogen side oil pressure of the fourth pressure gauge, the hydrogen side oil temperature of the second platinum thermal resistor, the balance valve flow of the second flow transmitter and the balance pressure of the balance gauge are recorded; closing the air compressor and the second air inlet valve, opening the first air outlet valve for exhausting, wherein the pressure of the fifth pressure gauge is respectively 0.5MPa, 0.4MPa, 0.3MPa, 0.2MPa, 0.1MPa and 0.05MPa when the pipe diameter DN25 is adopted; or the pressure of the fifth pressure gauge PI505 is respectively 0.6MPa, 0.5MPa, 0.4MPa, 0.3MPa, 0.2MPa, 0.1MPa and 0.05MPa when the pipe diameter DN40 is used, and various values are recorded; the second flow regulating valve is regulated to ensure that the flow of the second flow transmitter is 8L/min, 16L/min, 19L/min and 25L/min respectively when the pipe diameter DN25 is adopted; when the pipe diameter DN40 is 30L/min, 50L/min and 83L/min, repeating the steps of air pressure filling and air pressure reducing for test and recording; in the test process, along with the change of the flow of the balance valve, the third pressure gauge of the outlet pressure of the oil pump also changes, and when the flow is set, the second bypass valve is properly adjusted in a fine mode, and the outlet pressure of the oil pump at the hydrogen side is controlled to be 0.6Mpa when the pipe diameter DN25 is set; the pipe diameter DN40 is 1.1Mpa; the qualification requirements are as follows: under the condition that the oil-hydrogen pressure difference is kept unchanged, the pressure balance value of the balance valve is required to be within the range of +/-490 Pa in the rising and falling processes of the pressure in the engine at each balance valve flow check point.
2. A method of testing a balance valve according to claim 1, wherein: the balance valve single machine test comprises the following steps:
s1, static test is carried out to simulate the static working condition of a generator;
starting a second oil pump, and adjusting a second bypass valve to enable the outlet pressure of the second oil pump, namely the numerical value of a third pressure gauge, to be 0.15MPa when the pipe diameter DN25 is provided, and to be 0.2MPa when the pipe diameter DN40 is provided; starting an air compressor to charge air into the air tank BB003 to 84KPa when the pipe diameter DN25 is reached, and to charge air into 100KPa when the pipe diameter DN40 is reached; the second flow regulating valve is regulated, so that the second flow transmitter displays the flow as 19L/min when the pipe diameter DN25 is provided, and 83L/min when the pipe diameter DN40 is provided; closing the middle valves of the third valve group and the fourth valve group, observing the differential pressure value of the balance valve, and if the differential pressure value exceeds +/-490 Pa, opening a protective cover at the bottom of the balance valve, and adjusting a fine adjustment bolt to ensure that the balance accuracy meets the technical requirement; adjusting the second bypass valve to enable the outlet pressure of the third pressure gauge on the second oil pump to be 0.15Mpa when the pipe diameter DN25 is used; when the pipe diameter DN40 is respectively 0.2Mpa, 0.3Mpa, 0.4Mpa, 0.5Mpa and 0.62Mpa, corresponding second flow transmitter flow, balance accuracy of the balance meter and values of air side oil pressure of the fifth pressure meter, namely pressure of a gas tank, hydrogen side oil pressure of the fourth pressure meter and hydrogen side oil temperature of the second platinum thermal resistor are recorded; the qualification requirements are as follows: under the condition that the flow of the balance valve is kept unchanged at the maximum, the pressure balance value of the balance valve is required to be within a range of +/-490 Pa pressure difference in the whole pressure increasing and reducing process;
s2, a dynamic test is performed to simulate the working condition of the generator during rotation;
starting a second oil pump, and adjusting a second bypass valve to enable the outlet pressure of the second oil pump, namely the numerical value of a third pressure gauge, to be 0.15MPa when the pipe diameter DN25 is provided, and to be 0.2MPa when the pipe diameter DN40 is provided; starting an air compressor to charge the air tank to 84KPa when the pipe diameter DN25 is reached, and 100KPa when the pipe diameter DN40 is reached; the second flow regulating valve is regulated, so that the second flow transmitter displays that the flow is 19L/min when the pipe diameter DN25 is provided and 83L/min when the pipe diameter DN40 is provided; closing the middle valves of the third valve group and the fourth valve group, observing the differential pressure value of the balance valve, and if the differential pressure value exceeds +/-490 Pa, opening a protective cover at the bottom of the balance valve, and adjusting a fine adjustment bolt to ensure that the balance accuracy meets the technical requirement; the second flow regulating valve is regulated to enable the flow of the second flow transmitter to be 8L/min when the pipe diameter DN25 is provided, and be 16L/min, 19L/min, 25L/min, 30L/min, 50L/min and 83L/min when the pipe diameter DN40 is provided, and the balance pressure difference of the balance meter under the corresponding flow of the second flow transmitter, the air side oil pressure of the fifth pressure meter, the hydrogen side oil pressure of the fourth pressure meter and the hydrogen side oil temperature of the second platinum thermal resistor are recorded; in the test process, along with the change of the flow of the balance valve, the outlet pressure of the second oil pump, namely the numerical value of the third pressure gauge, is also changed, when the flow is set, the second bypass valve is properly adjusted in a fine mode, and the outlet pressure of the second oil pump is controlled to be 0.15MPa when the pipe diameter DN25 is kept, and 0.2MPa when the pipe diameter DN40 is kept; the qualification requirements are as follows: under the condition that the oil-hydrogen pressure difference is kept unchanged, the pressure balance value of the balance valve needs to be within the range of +/-490 Pa pressure difference in the whole flow rising and falling process.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111667610.3A CN114354179B (en) | 2021-12-30 | 2021-12-30 | Balance valve testing system and method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111667610.3A CN114354179B (en) | 2021-12-30 | 2021-12-30 | Balance valve testing system and method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114354179A CN114354179A (en) | 2022-04-15 |
| CN114354179B true CN114354179B (en) | 2023-09-26 |
Family
ID=81106132
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111667610.3A Active CN114354179B (en) | 2021-12-30 | 2021-12-30 | Balance valve testing system and method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114354179B (en) |
Citations (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4792911A (en) * | 1986-01-17 | 1988-12-20 | Westinghouse Electric Corp. | Diagnostic apparatus for an electric generator seal oil system |
| CN2809378Y (en) * | 2005-01-12 | 2006-08-23 | 刘敬善 | Full-functional counterweight type balance valve |
| CN200949657Y (en) * | 2006-07-05 | 2007-09-19 | 李峰 | Hydrogen cooling turbine generator seal oil numerical control device |
| CN201600238U (en) * | 2010-01-18 | 2010-10-06 | 北京艾迪西暖通科技有限公司 | Balanced valve test device |
| CN201682346U (en) * | 2010-05-25 | 2010-12-22 | 王彦军 | Double flowing ring sealing oil system of hydrogen cooling turbogenerator |
| CN203225616U (en) * | 2013-02-04 | 2013-10-02 | 哈尔滨电机厂有限责任公司 | 600MW nuclear power conventional island auxiliary generator seal oil system |
| CN103674541A (en) * | 2013-12-31 | 2014-03-26 | 卓旦春 | Method for testing performance of differential pressure valve |
| CN103983447A (en) * | 2014-05-27 | 2014-08-13 | 牡丹江市康兴电站设备制造有限公司 | Performance test bench for differential valve of power station oil seal system |
| CN104019075A (en) * | 2014-06-05 | 2014-09-03 | 常德中联重科液压有限公司 | Testing system for balance valve |
| CN105954016A (en) * | 2016-04-27 | 2016-09-21 | 中广核核电运营有限公司 | Fault analyzing method and offline detection device for liquid level control valve of oil tank of an oil sealing system |
| CN205841771U (en) * | 2016-08-03 | 2016-12-28 | 华北电力科学研究院有限责任公司 | Thermal power plant's electromotor double-flow se al oil |
| CN207064805U (en) * | 2017-04-18 | 2018-03-02 | 中国船舶重工集团公司第七一九研究所 | A kind of automatic flow control valve pilot system |
| CN207145619U (en) * | 2017-09-02 | 2018-03-27 | 上海鹭发电气(集团)有限公司 | Generator hydrogen cooling system sealing oil system |
| CN207569206U (en) * | 2017-10-20 | 2018-07-03 | 珠海市钰海电力有限公司 | For the balance valve system of hydrogen cooled generator hydrogen-side seal oil system |
| CN109990987A (en) * | 2017-12-28 | 2019-07-09 | 江苏核电有限公司 | A kind of generator sealing bearing bush experimental rig and test method |
| CN110375984A (en) * | 2019-08-02 | 2019-10-25 | 合肥通用机械研究院有限公司 | A kind of complete series balanced valve test macro and test method |
| CN209742978U (en) * | 2018-11-29 | 2019-12-06 | 河北冀研能源科学技术研究院有限公司 | Double-flow ring sealing oil system of steam turbine generator set |
| CN110966796A (en) * | 2019-12-05 | 2020-04-07 | 福建工程学院 | Direct expansion type ground source pump refrigerant leakage prevention device and method thereof |
| CN212643545U (en) * | 2020-07-02 | 2021-03-02 | 哈尔滨电机厂有限责任公司 | Pressure difference valve device of gas turbine generator |
| CN216869999U (en) * | 2021-12-30 | 2022-07-01 | 哈尔滨哈控实业有限公司 | Balance valve test system |
-
2021
- 2021-12-30 CN CN202111667610.3A patent/CN114354179B/en active Active
Patent Citations (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4792911A (en) * | 1986-01-17 | 1988-12-20 | Westinghouse Electric Corp. | Diagnostic apparatus for an electric generator seal oil system |
| CN2809378Y (en) * | 2005-01-12 | 2006-08-23 | 刘敬善 | Full-functional counterweight type balance valve |
| CN200949657Y (en) * | 2006-07-05 | 2007-09-19 | 李峰 | Hydrogen cooling turbine generator seal oil numerical control device |
| CN201600238U (en) * | 2010-01-18 | 2010-10-06 | 北京艾迪西暖通科技有限公司 | Balanced valve test device |
| CN201682346U (en) * | 2010-05-25 | 2010-12-22 | 王彦军 | Double flowing ring sealing oil system of hydrogen cooling turbogenerator |
| CN203225616U (en) * | 2013-02-04 | 2013-10-02 | 哈尔滨电机厂有限责任公司 | 600MW nuclear power conventional island auxiliary generator seal oil system |
| CN103674541A (en) * | 2013-12-31 | 2014-03-26 | 卓旦春 | Method for testing performance of differential pressure valve |
| CN103983447A (en) * | 2014-05-27 | 2014-08-13 | 牡丹江市康兴电站设备制造有限公司 | Performance test bench for differential valve of power station oil seal system |
| CN104019075A (en) * | 2014-06-05 | 2014-09-03 | 常德中联重科液压有限公司 | Testing system for balance valve |
| CN105954016A (en) * | 2016-04-27 | 2016-09-21 | 中广核核电运营有限公司 | Fault analyzing method and offline detection device for liquid level control valve of oil tank of an oil sealing system |
| CN205841771U (en) * | 2016-08-03 | 2016-12-28 | 华北电力科学研究院有限责任公司 | Thermal power plant's electromotor double-flow se al oil |
| CN207064805U (en) * | 2017-04-18 | 2018-03-02 | 中国船舶重工集团公司第七一九研究所 | A kind of automatic flow control valve pilot system |
| CN207145619U (en) * | 2017-09-02 | 2018-03-27 | 上海鹭发电气(集团)有限公司 | Generator hydrogen cooling system sealing oil system |
| CN207569206U (en) * | 2017-10-20 | 2018-07-03 | 珠海市钰海电力有限公司 | For the balance valve system of hydrogen cooled generator hydrogen-side seal oil system |
| CN109990987A (en) * | 2017-12-28 | 2019-07-09 | 江苏核电有限公司 | A kind of generator sealing bearing bush experimental rig and test method |
| CN209742978U (en) * | 2018-11-29 | 2019-12-06 | 河北冀研能源科学技术研究院有限公司 | Double-flow ring sealing oil system of steam turbine generator set |
| CN110375984A (en) * | 2019-08-02 | 2019-10-25 | 合肥通用机械研究院有限公司 | A kind of complete series balanced valve test macro and test method |
| CN110966796A (en) * | 2019-12-05 | 2020-04-07 | 福建工程学院 | Direct expansion type ground source pump refrigerant leakage prevention device and method thereof |
| CN212643545U (en) * | 2020-07-02 | 2021-03-02 | 哈尔滨电机厂有限责任公司 | Pressure difference valve device of gas turbine generator |
| CN216869999U (en) * | 2021-12-30 | 2022-07-01 | 哈尔滨哈控实业有限公司 | Balance valve test system |
Non-Patent Citations (4)
| Title |
|---|
| 200MW 汽轮发电机密封油系统的改造;桂喜良;大电机技术(第06期);52-57 * |
| Effective utilisation of butanol along with gasoline in a spark ignition engine through a dual injection system;T. Venugopal，A. Ramesh;Applied Thermal Engineering;第59卷(第1-2期);550-558 * |
| 发电机双流环式密封油系统氢侧油路平衡故障的分析;田阳;;发电设备(第05期);62-64 * |
| 基于变频调速技术的平衡阀动态流量特性测试;臧飞，郭健翔，徐文，付珊;青岛理工大学学报;第37卷(第1期);82-85 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114354179A (en) | 2022-04-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6314794B1 (en) | Method and apparatus for detecting leaks in heat exchangers for motor vehicles | |
| CN108708802B (en) | Low-temperature high-speed end face sealing test device for liquid rocket engine turbo pump | |
| CN113790852B (en) | Detection method of detection device for detecting performance of pressure reducing valve | |
| CN209910924U (en) | Check valve gas testing system | |
| US5600996A (en) | Method and apparatus for testing the tightness of housings | |
| CN103398830B (en) | A kind of grease chamber's sealing leak hunting method of load ratio bridging switch | |
| CN216869999U (en) | Balance valve test system | |
| CN112240819A (en) | Valve detection system | |
| CN114354179B (en) | Balance valve testing system and method | |
| CN206311283U (en) | The system for being detected for motor controller sealing property and looking for leak source | |
| US4474049A (en) | Meter proving method | |
| CN109441795A (en) | A kind of automatic gearbox lubricating oil pump full performance test platform | |
| RU138285U1 (en) | STAND FOR TESTING TURBOCHARGERS OF INTERNAL COMBUSTION ENGINES | |
| CN105300614A (en) | Vehicle LNG gas cylinder multifunctional valve test system and test method | |
| CN110491532B (en) | Nuclear power station main pump leakage abnormity processing system and method | |
| CN210071254U (en) | Differential pressure type air tightness tester | |
| CN108072499A (en) | A kind of bilayer air-conditioner pipe air tightness detection system and method | |
| CN209294023U (en) | Automatic gearbox lubricating oil pump full performance test platform | |
| CN113898568B (en) | Nuclear power main pump No. 1 sealing reliability evaluation test method | |
| CN110611969B (en) | Induction coil cooling and pressure-bearing system of induction heating equipment | |
| CN111896191A (en) | On-site calibration method and auxiliary calibration equipment for integral oil tank leakage detection equipment | |
| CN213516235U (en) | Device for sealing test of graphite sealing device | |
| CN213274739U (en) | Static pressure dry gas seal test device for kettle | |
| CN114659821B (en) | System and method for detecting performance of hydrogenation equipment | |
| CN216717745U (en) | Device for detecting leakage of TCA heat exchanger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |