CN113916568A - Brake and fatigue test system comprising same - Google Patents
Brake and fatigue test system comprising same Download PDFInfo
- Publication number
- CN113916568A CN113916568A CN202110144775.6A CN202110144775A CN113916568A CN 113916568 A CN113916568 A CN 113916568A CN 202110144775 A CN202110144775 A CN 202110144775A CN 113916568 A CN113916568 A CN 113916568A
- Authority
- CN
- China
- Prior art keywords
- valve
- brake
- port
- way valve
- communicated
- 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.)
- Pending
Links
- 238000009661 fatigue test Methods 0.000 title claims description 13
- 239000007788 liquid Substances 0.000 claims description 26
- 238000013016 damping Methods 0.000 claims description 11
- 238000004891 communication Methods 0.000 claims description 8
- 239000002828 fuel tank Substances 0.000 claims 2
- 239000012530 fluid Substances 0.000 claims 1
- 239000003921 oil Substances 0.000 description 29
- 239000010720 hydraulic oil Substances 0.000 description 12
- 238000012360 testing method Methods 0.000 description 11
- 238000012423 maintenance Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M99/00—Subject matter not provided for in other groups of this subclass
- G01M99/008—Subject matter not provided for in other groups of this subclass by doing functionality tests
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
Abstract
The invention discloses a brake, which comprises: the hydraulic control system comprises a pump assembly, an oil tank, a first one-way valve, a second one-way valve, a first electromagnetic valve, a second electromagnetic valve and a series hydraulic cylinder group. The inlet of the first one-way valve is communicated with the pump assembly, and the outlet of the second one-way valve is communicated with the oil tank. The first electromagnetic valve is a two-position three-way valve and comprises a P port, a T port and an A port, the outlet of the first one-way valve is communicated with the P port, the A port is communicated with one port of the rodless cavity of the serial hydraulic cylinder group, and the T port is communicated with the inlet of the second one-way valve. The second electromagnetic valve is a two-position two-way valve, and when the power is lost, the two ends of the second electromagnetic valve are disconnected with each other; when the power is on, the two ends of the second electromagnetic valve are communicated. Two ends of the second electromagnetic valve are respectively communicated with the other interface of the rodless cavity of the serial hydraulic cylinder group and the inlet of the second one-way valve. The device can realize yaw rapid braking of the wind turbine generator, and improves the running reliability of the wind turbine generator.
Description
Technical Field
The invention relates to a brake and a fatigue testing system comprising the same.
Background
With the development and upgrade of the wind power generation industry, large megawatt wind power generators are continuously developed at home and abroad in recent years. Because of the gradual increase of the capacity of a single machine and the increase of the number of installed machines, the safety control of the wind wheel is the central importance, and in order to ensure the normal and effective operation of the generator set, the wind wheel must be accurately controlled to rotate or stop in special states such as maintenance, and the like, so a brake is generally installed on the wind turbine generator set. The existing power device has the disadvantages of complex structure, low reliability and inconvenient maintenance. The safety and the reliability of the brake are directly related to the safety and the reliability of the operation of the wind generating set. In order to ensure the reliability of the brake, a fatigue test is performed in the design and production stage by using a testing device, so that the fatigue damage can be avoided after repeated use in the using process, and the safety of the wind generating set is not affected.
Disclosure of Invention
The invention aims to overcome the defects that the brake of the wind driven generator in the prior art is complex in structure and lacks of a fatigue testing device, and provides a brake capable of solving the problems and a fatigue testing system comprising the brake.
The invention solves the technical problems through the following technical scheme:
a brake, characterized in that it comprises:
a power module including a pump assembly for providing pressurized oil and an oil tank;
the yaw brake module comprises a first one-way valve, a second one-way valve, a first electromagnetic valve, a second electromagnetic valve and a series hydraulic cylinder group, wherein an inlet of the first one-way valve is communicated with the pump assembly, an outlet of the second one-way valve is communicated with the oil tank, the first electromagnetic valve is a two-position three-way valve and comprises a P port, a T port and an A port, an outlet of the first one-way valve is communicated with the P port, the A port is communicated with one interface of a rodless cavity of the series hydraulic cylinder group, and the T port is communicated with an inlet of the second one-way valve; when the first electromagnetic valve is powered off, the port P is communicated with the port A, and the port T is disconnected; when the first electromagnetic valve is electrified, the T port is communicated with the port A, and the P port is disconnected; the second electromagnetic valve is a two-position two-way valve, and when the power is lost, two ends of the second electromagnetic valve are disconnected with each other; when the power is on, the two ends of the second electromagnetic valve are communicated; and two ends of the second electromagnetic valve are respectively communicated with the other interface of the rodless cavity of the serial hydraulic cylinder group and the inlet of the second one-way valve.
Preferably, the yaw brake module further includes a first overflow valve, an inlet of the first overflow valve is communicated with the T port, and an outlet of the first overflow valve is communicated with the second electromagnetic valve and an inlet of the second check valve.
Preferably, the yaw brake module further comprises a first throttle valve, and two ends of the first throttle valve are respectively connected to one end of the second solenoid valve and one interface of the rodless chamber of the series hydraulic cylinder group.
Preferably, the brake further includes a second throttle valve and a damping plug, the second throttle valve and the damping plug are connected in series on a pipeline between the first check valve and the first solenoid valve, and the second throttle valve is connected to an outlet of the first check valve.
Preferably, the brake further comprises a third one-way valve, and the third one-way valve is connected between the second throttle valve and the damping plug.
Preferably, the brake further comprises a second overflow valve, and two ends of the second overflow valve are connected to the outlet of the first check valve and the inlet of the second check valve.
Preferably, the brake further comprises an accumulator in communication with the outlet of the first one-way valve.
Preferably, the brake further comprises a manual pump and a fourth one-way valve, an oil inlet of the manual pump is connected to the oil tank, an oil outlet of the manual pump is connected to an inlet of the fourth one-way valve, and an outlet of the fourth one-way valve is connected to an outlet of the first one-way valve.
Preferably, the brake further comprises a first filter assembly connected between the outlet of the pump assembly and the inlet of the first check valve, the first filter assembly comprising a first filter, a fifth check valve and a first differential pressure transmitter connected in parallel with each other.
Preferably, the brake further comprises a second filter assembly connected between the outlet of the second check valve and the oil tank, and the second filter assembly comprises a second filter, a sixth check valve and a second differential pressure transmitter which are connected in parallel.
Preferably, the brake further comprises an air cooler connected between the oil tank and the second filter assembly.
Preferably, the power module further comprises a liquid level meter mounted on the oil tank.
Preferably, the fatigue test system of the brake comprises a pressure sensor, a controller and the brake, wherein the pressure sensor is connected to the outlet of the first one-way valve, the controller is in communication connection with the pressure sensor, and the controller controls the motion state of the pump assembly.
Preferably, the power module further comprises a liquid level liquid temperature switch, and the liquid level liquid temperature switch is in communication connection with the controller.
On the basis of the common knowledge in the field, the above preferred conditions can be combined randomly to obtain the preferred embodiments of the invention.
The positive progress effects of the invention are as follows: the device can realize yaw rapid braking of the wind turbine generator, and improves the running reliability of the wind turbine generator.
Drawings
FIG. 1 is a hydraulic schematic of a fatigue testing system for a brake in a preferred embodiment of the invention.
Description of reference numerals:
Liquid level and liquid temperature 140
P port 231
A port 233
Series hydraulic cylinder group 250
First differential pressure signal transmitter 730
Second differential pressure signal generator 830
Detailed Description
The invention is further illustrated by the following examples, which are not intended to limit the scope of the invention.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
Fig. 1 shows a brake comprising: a power module 100 and a yaw brake module 200. The power module 100 includes a pump assembly 110 and a tank 120, the pump assembly 110 being for providing pressurized oil. The yaw brake module 200 includes a first check valve 210, a second check valve 220, a first solenoid valve 230, a second solenoid valve 240, and a series hydraulic cylinder bank 250. The inlet of the first check valve 210 communicates with the pump assembly 110 and the outlet of the second check valve 220 communicates with the tank 120. The first solenoid valve 230 is a two-position three-way valve, the first solenoid valve 230 comprises a P port 231, a T port 232 and an A port 233, an outlet of the first check valve 210 is communicated with the P port 231, the A port 233 is communicated with one port of a rodless cavity of the tandem hydraulic cylinder group 250, and the T port 232 is communicated with an inlet of the second check valve 220. When the first electromagnetic valve 230 is powered off, the port P231 is communicated with the port A233, and the port T232 is disconnected; when the first solenoid valve 230 is energized, the T port 232 communicates with the a port 233, and the P port 231 is disconnected. The second electromagnetic valve 240 is a two-position two-way valve, and when power is lost, two ends of the second electromagnetic valve 240 are disconnected with each other; when energized, the two ends of the second solenoid valve 240 are connected. Two ends of the second electromagnetic valve 240 are respectively communicated with the other interface of the rodless cavity of the tandem hydraulic cylinder group 250 and the inlet of the second check valve 220.
When the brake is used for yaw braking of the wind generating set, the first electromagnetic valve 230 is in a power-off state, and the port P231 is communicated with the port A233; the second solenoid valve 240 is in a power-off state, and both ends of the second solenoid valve 240 are in a disconnected state. The pump assembly 110 inputs the hydraulic oil in the oil tank 120 into the brake system, the hydraulic oil is input into the rodless chamber of the tandem hydraulic cylinder group 250 through the first check valve 210, the P port 231 and the a port 233, and the other end of the tandem hydraulic cylinder group 250 is connected with the second electromagnetic valve 240 in a disconnected state, so that the hydraulic oil can push the piston rod to move towards the rod chamber, and the yaw device can be rapidly braked. When the brake needs to be released, the first solenoid valve 230 and/or the second solenoid valve 240 need to be energized, so that the hydraulic oil in the rodless chamber quickly flows back into the oil tank 120.
In practical application, the yaw device does not need to be fully braked in a partial working state, but only needs to be in a semi-braking state under a certain pressure, in the scheme, the yaw braking module 200 further comprises a first overflow valve 260, an inlet of the first overflow valve 260 is communicated with the T port 232, and an outlet of the first overflow valve 260 is communicated with inlets of the second electromagnetic valve 240 and the second check valve 220. That is, when the first solenoid valve 230 is energized and the second solenoid valve 240 is de-energized, the rodless chamber of the tandem hydraulic cylinder group 250 communicates with the port a 233, the port T232, the first relief valve 260, and the oil tank 120, so that the hydraulic pressure in the rodless chamber of the tandem hydraulic cylinder group 250 can be maintained at the set pressure value of the first relief valve 260, and yaw half braking can be achieved.
In this embodiment, the yaw brake module 200 further includes a first throttle valve 270, and both ends of the first throttle valve 270 are respectively connected to one end of the second solenoid valve 240 and one interface of the rod-less chamber of the series hydraulic cylinder group 250. The first throttle valve 270 is mainly used for protecting the safety of the yaw brake module 200, and when a fault occurs, the first throttle valve 270 is opened in time to realize rapid pressure relief. Under normal operation, the first throttle valve 270 is in a closed state.
In addition, the brake further comprises a second throttle valve 310 and a damping plug 320, the second throttle valve 310 and the damping plug 320 are connected in series on a pipeline between the first check valve 210 and the first solenoid valve 230, and the second throttle valve 310 is connected to an outlet of the first check valve 210. The second throttle valve 310 can control the on-off of the oil inlet pipeline, and the damage of a brake device caused by the out-of-control of a hydraulic system is prevented. In addition, the damping plug 320 can reduce the impact of the pressure oil on the first solenoid valve 230 and the series hydraulic cylinder group 250, and avoid the damage of elements caused by high-pressure impact.
The brake further includes a third one-way valve 330, the third one-way valve 330 being connected between the second throttle valve 310 and the damping plug 320. The third check valve 330 can further prevent the reverse flow of oil from causing damage to the pump assembly 110.
In this embodiment, the brake further includes a second overflow valve 400, and two ends of the second overflow valve 400 are connected to the outlet of the first check valve 210 and the inlet of the second check valve 220. When the oil pressure in the system exceeds the safety pressure, the second overflow valve 400 is depressurized, so that the pressure is prevented from being continuously increased, and the safety of the system is ensured.
The brake further includes an accumulator 500, the accumulator 500 being in communication with the outlet of the first one-way valve 210. Accumulator 500 is primarily for energy conservation. When the pressure in the system reaches the set pressure value of the accumulator 500, the pump assembly 110 may be deactivated and the system pressure provided by the accumulator 500. When the pressure of accumulator 500 decreases to a certain value, pump assembly 110 is activated to provide pressure to the system and replenish the pressure of accumulator 500.
The brake further comprises a manual pump 610 and a fourth one-way valve 620, wherein an oil inlet of the manual pump 610 is connected to the oil tank 120, an oil outlet of the manual pump 610 is connected to an inlet of the fourth one-way valve 620, and an outlet of the fourth one-way valve 620 is connected to an outlet of the first one-way valve 210. In the event of a failure of the original pump assembly 110, the manual pump 610 may be activated to ensure that the brake system is still operating effectively at this time. The manual pump 610 pumps hydraulic oil and conveys the hydraulic oil into the yaw brake module 200 through the fourth check valve 620, so that the series hydraulic cylinder group 250 is driven to work, a brake function is executed, and the reliability of the brake is improved.
In order to prevent impurities in the hydraulic oil from entering the hydraulic components to cause the brake to fail, the brake further includes a first filter assembly 700, the first filter assembly 700 is connected between the outlet of the pump assembly 110 and the inlet of the first check valve 210, and the first filter assembly 700 includes a first filter 710, a fifth check valve 720 and a first differential pressure transmitter 730 which are connected in parallel. When the first filter 710 is clogged, the first differential pressure transmitter 730 transmits a signal to remind a worker to clean or replace the first filter 710.
In addition, the brake further includes a second filter assembly 800, the second filter assembly 800 is connected between the outlet of the second check valve 220 and the oil tank 120, and the second filter assembly 800 includes a second filter 810, a sixth check valve 820 and a second differential pressure transmitter 830, which are connected in parallel with each other. When the second filter 810 is clogged, the second differential pressure transmitter 830 transmits a signal to remind a worker to clean or replace the second filter 810.
In order to prevent the safety and reliability of the brake from being affected by the overhigh temperature caused by the long-term operation of the hydraulic oil, the brake further comprises an air cooler 900, and the air cooler 900 is connected between the oil tank 120 and the second filter assembly 800. The air cooler 900 can effectively reduce the temperature of the hydraulic oil in the brake and ensure that the whole system works in a safe temperature range.
In addition, the power module 100 further includes a liquid level gauge 130, and the liquid level gauge 130 is mounted on the oil tank 120. The level gauge 130 is used to measure the volume of hydraulic oil in the tank 120 to facilitate the addition or subtraction of hydraulic oil by an operator.
As will be understood in conjunction with fig. 1, the present embodiment also discloses a brake fatigue testing system, which includes a pressure sensor 1000, a controller 1100 and the brake as above. The pressure sensor 1000 is connected to the outlet of the first check valve 210, the controller 1100 is connected in communication with the pressure sensor 1000, and the controller 1100 controls the motion state of the pump assembly 110.
The fatigue testing system is used for testing, firstly, a high pressure value and a low pressure value to be tested are determined, namely, a high pressure control signal and a low pressure control signal are set in the pressure sensor 1000, when the oil pressure reaches the high pressure value, the pressure sensor 1000 sends a control signal to the controller 1100, and the pump assembly 110 is driven to stop moving; when the oil pressure reaches a low pressure value, the pressure sensor 1000 sends a control signal to the controller 1100 to start the operation of the drive pump assembly 110. And repeating the steps to detect the reliability of the brake in a normal working state. To improve the efficiency of the test, it is generally necessary to shut down the accumulator 500.
Taking this embodiment as an example, the closing pressure (185bar) and the releasing pressure (5bar) of the brake are set, the test button of the controller 1100 is pressed, and the PLC in the controller 1100 automatically controls the series hydraulic cylinder set 250 to perform the 5-185bar pressure opening and closing cycle. When the series hydraulic cylinder group 250 is closed, the first solenoid valve 230 and the second solenoid valve 240 are simultaneously de-energized, the system automatically starts the pump assembly 110, the brake pressure rises to 185bar, and when the high-point pressure value (185bar) set by the pressure sensor 1000 is reached, the pressure sensor 1000 outputs a signal to the controller 1100, so that the pump assembly 110 is controlled to stop working. At this time, the PLC automatically controls the delay time for 1s, the first electromagnetic valve 230 is electrified, the brake pressure begins to drop, when the brake pressure drops to the set pressure (5bar) of the first overflow valve 260, the low-point pressure value (5bar) set by the pressure sensor 1000 is reached, the series hydraulic cylinder group 250 is released, the pressure sensor 1000 outputs a signal to the controller 1100, the pump assembly 110 is controlled to be started, the brake pressure is increased to 185bar again, the operation is sequentially circulated, the brake opening and closing fatigue cycle test is realized, and the PLC control cabinet records the cycle fatigue test times.
In order to ensure the safety and accuracy of the test, the pipeline of the test device is generally required to be flushed, so that the pipeline is ensured to be smooth. In this scheme, when washing the pipeline before the test, first solenoid valve 230 is in the power loss state, and first choke valve 270 is in the open mode, and hydraulic oil directly passes through first check valve 210, first solenoid valve 230, series connection hydraulic cylinder group 250, first choke valve 270 and second check valve 220 after pump assembly 110 pumpingly, flows back to in oil tank 120 fast to guarantee that test system's management is unobstructed.
The automatic pressure maintaining capability of the system can be tested by utilizing the test system, in the embodiment, the pressure maintaining time and the pressure maintaining pressure are set through the operation of the control cabinet, the pump assembly 110 is automatically started, the pressure in the brake is increased to 185bar, when the pressure reaches a high-point pressure value (185bar) set by the pressure sensor 1000, the pressure sensor 1000 outputs a signal to control the pump assembly 110 to stop, the hydraulic system enters a pressure maintaining state, the PLC controls automatic timing and records a pressure difference value, and when the pressure maintaining time reaches a set value, the pressure maintaining is finished, so that the pressure maintaining capability test of the brake is realized.
In this scheme, power module 100 still includes liquid level liquid temperature 140 switch, and liquid level liquid temperature 140 switch and controller 1100 communication connection. The liquid level/temperature switch 140 can detect the liquid level and the oil temperature in the oil tank 120. When the liquid level is lower than the lowest point of the liquid level liquid temperature 140 switch, the liquid level liquid temperature 140 switch outputs a switch signal to the controller 1100, and the controller 1100 gives an alarm and stops the operation of the system so as to protect the safety of a brake hydraulic system; when the temperature is lower than the lowest point of the liquid level liquid temperature 140 switch, the liquid level liquid temperature 140 switch outputs a switch signal to the controller 1100, and the controller 1100 gives an alarm and stops the operation of the system so as to protect the safety of the brake hydraulic system.
While specific embodiments of the invention have been described above, it will be appreciated by those skilled in the art that this is by way of example only, and that the scope of the invention is defined by the appended claims. Various changes and modifications to these embodiments may be made by those skilled in the art without departing from the spirit and scope of the invention, and these changes and modifications are within the scope of the invention.
Claims (14)
1. A brake, characterized in that it comprises:
a power module including a pump assembly for providing pressurized oil and an oil tank;
the yaw brake module comprises a first one-way valve, a second one-way valve, a first electromagnetic valve, a second electromagnetic valve and a series hydraulic cylinder group, wherein an inlet of the first one-way valve is communicated with the pump assembly, an outlet of the second one-way valve is communicated with the oil tank, the first electromagnetic valve is a two-position three-way valve and comprises a P port, a T port and an A port, an outlet of the first one-way valve is communicated with the P port, the A port is communicated with one interface of a rodless cavity of the series hydraulic cylinder group, and the T port is communicated with an inlet of the second one-way valve; when the first electromagnetic valve is powered off, the port P is communicated with the port A, and the port T is disconnected; when the first electromagnetic valve is electrified, the T port is communicated with the port A, and the P port is disconnected; the second electromagnetic valve is a two-position two-way valve, and when the power is lost, two ends of the second electromagnetic valve are disconnected with each other; when the power is on, the two ends of the second electromagnetic valve are communicated; and two ends of the second electromagnetic valve are respectively communicated with the other interface of the rodless cavity of the serial hydraulic cylinder group and the inlet of the second one-way valve.
2. The brake of claim 1, wherein the yaw brake module further comprises a first overflow valve, an inlet of the first overflow valve is communicated with the T port, and an outlet of the first overflow valve is communicated with the second electromagnetic valve and an inlet of the second one-way valve.
3. The brake of claim 1, wherein the yaw brake module further comprises a first throttle valve having respective ends connected to an interface of one end of the second solenoid valve and a rod-less chamber of the tandem hydraulic cylinder bank.
4. The brake of claim 1, further comprising a second throttle and a damping choke, said second throttle and said damping choke being connected in series on a line between said first check valve and said first solenoid, said second throttle being connected to an outlet of said first check valve.
5. The brake of claim 4, further comprising a third one-way valve connected between the second throttle valve and the damping plug.
6. The brake of claim 1, further comprising a second overflow valve having both ends connected to an outlet of the first check valve and an inlet of the second check valve.
7. The brake of claim 1, further comprising an accumulator in communication with an outlet of said first one-way valve.
8. The brake of claim 1, further comprising a manual pump and a fourth one-way valve, an oil inlet of the manual pump being connected to the oil tank, an oil outlet of the manual pump being connected to an inlet of the fourth one-way valve, an outlet of the fourth one-way valve being connected to an outlet of the first one-way valve.
9. The brake of claim 1, further comprising a first filter assembly connected between the outlet of the pump assembly and the inlet of the first one-way valve, the first filter assembly including a first filter, a fifth one-way valve, and a first differential pressure transmitter connected in parallel with one another.
10. The brake of claim 1, further comprising a second filter assembly connected between an outlet of the second check valve and the fuel tank, the second filter assembly including a second filter, a sixth check valve, and a second differential pressure transmitter connected in parallel with each other.
11. The brake of claim 10 further comprising an air cooler connected between said oil tank and said second filter assembly.
12. The brake of claim 1, wherein the power module further comprises a fluid level gauge mounted on the fuel tank.
13. A fatigue testing system for a brake, comprising a pressure sensor connected to an outlet of the first one-way valve, a controller in communication with the pressure sensor, the controller controlling a state of motion of the pump assembly, and a brake according to any one of claims 1-12.
14. A fatigue testing system for a brake according to claim 13, wherein said power module further comprises a liquid level liquid temperature switch in communicative connection with said controller.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110144775.6A CN113916568A (en) | 2021-02-02 | 2021-02-02 | Brake and fatigue test system comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110144775.6A CN113916568A (en) | 2021-02-02 | 2021-02-02 | Brake and fatigue test system comprising same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113916568A true CN113916568A (en) | 2022-01-11 |
Family
ID=79232545
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110144775.6A Pending CN113916568A (en) | 2021-02-02 | 2021-02-02 | Brake and fatigue test system comprising same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113916568A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6360592B1 (en) * | 1998-11-27 | 2002-03-26 | Lucas Industries Public Limited Company | Detection and identification of pressure-sensor faults in electro-hydraulic (EHB) braking systems |
| CN101629546A (en) * | 2009-08-27 | 2010-01-20 | 湘电风能有限公司 | Integration hydraulic brake system of wind generating set |
| CN204553120U (en) * | 2015-03-18 | 2015-08-12 | 天津市精研工程机械传动有限公司 | Hydraulic system of wind power generating set |
| CN206625937U (en) * | 2017-03-28 | 2017-11-10 | 上海圣克赛斯液压机械有限公司 | A kind of wind power generating set brake system and its power set |
| CN110360171A (en) * | 2018-09-30 | 2019-10-22 | 上海圣克赛斯液压机械有限公司 | Wind-powered electricity generation brake fluid pressure station |
| CN209781131U (en) * | 2019-04-04 | 2019-12-13 | 上海圣克赛斯液压机械有限公司 | wind wheel lock brake valve group |
-
2021
- 2021-02-02 CN CN202110144775.6A patent/CN113916568A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6360592B1 (en) * | 1998-11-27 | 2002-03-26 | Lucas Industries Public Limited Company | Detection and identification of pressure-sensor faults in electro-hydraulic (EHB) braking systems |
| CN101629546A (en) * | 2009-08-27 | 2010-01-20 | 湘电风能有限公司 | Integration hydraulic brake system of wind generating set |
| CN204553120U (en) * | 2015-03-18 | 2015-08-12 | 天津市精研工程机械传动有限公司 | Hydraulic system of wind power generating set |
| CN206625937U (en) * | 2017-03-28 | 2017-11-10 | 上海圣克赛斯液压机械有限公司 | A kind of wind power generating set brake system and its power set |
| CN110360171A (en) * | 2018-09-30 | 2019-10-22 | 上海圣克赛斯液压机械有限公司 | Wind-powered electricity generation brake fluid pressure station |
| CN209781131U (en) * | 2019-04-04 | 2019-12-13 | 上海圣克赛斯液压机械有限公司 | wind wheel lock brake valve group |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110529442B (en) | Hydraulic system matched with piston mechanical fatigue test bed | |
| CN102979070B (en) | Motor system for lifting ocean platform and load unbalance monitoring and controlling method of motor system | |
| CN206035914U (en) | Four jar synchronous hydraulic system of automobile elevator | |
| CN103352900A (en) | Heavy-duty mining dump vehicle hydraulic oil cylinder/hydraulic valve test table | |
| CN101936857B (en) | Confining pressure keeping system of rock triaxial creep testing machine | |
| CN103644155A (en) | Hydraulic actuator | |
| CN104454791A (en) | Parallel-energy-saving-technology-based hydraulic device for testing durability of hydraulic pumps and overflow valves | |
| CN103089749A (en) | Portable intelligent hydraulic loading device | |
| CN110696802A (en) | Start-stop system and start-stop method of electric air compressor for new energy vehicle | |
| CN102493916B (en) | Off-course hydraulic braking device of wind generating set | |
| CN106286254B (en) | A kind of air compressor machine of full-automatic unmanned supervision | |
| CN113916568A (en) | Brake and fatigue test system comprising same | |
| CN207935183U (en) | A kind of hydraulic energy-accumulating type wind power generating set | |
| CN105716963B (en) | A kind of motor turning power hose high temperature pulse integrated test system | |
| CN202789859U (en) | Hydraulic energy-saving temperature controlling system for loader working equipment | |
| CN203463382U (en) | Low-high pressure soft start hydraulic oil source system | |
| CN208885659U (en) | Wind-powered electricity generation brake fluid pressure station | |
| CN211573920U (en) | Multifunctional hydraulic test platform | |
| CN209781131U (en) | wind wheel lock brake valve group | |
| CN104929994B (en) | Gas-liquid conversion energy-conserving work station | |
| CN209398906U (en) | A kind of hydraulic control system of Direct Travel pneumatic hydraulic actuator | |
| CN110360171A (en) | Wind-powered electricity generation brake fluid pressure station | |
| CN107795529B (en) | Electro-hydraulic actuator and method for detecting safety function of electro-hydraulic actuator | |
| CN201372815Y (en) | Integrated electro-hydraulic actuator for quick closing valve | |
| CN111412176A (en) | Turning system device of centrifugal pump and using method |
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 |