CN114922883B - Hydraulic system and method for measuring abrasion characteristics of hydraulic fluid - Google Patents
Hydraulic system and method for measuring abrasion characteristics of hydraulic fluid Download PDFInfo
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- CN114922883B CN114922883B CN202210588229.6A CN202210588229A CN114922883B CN 114922883 B CN114922883 B CN 114922883B CN 202210588229 A CN202210588229 A CN 202210588229A CN 114922883 B CN114922883 B CN 114922883B
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- 239000012530 fluid Substances 0.000 title claims abstract description 134
- 238000000034 method Methods 0.000 title claims abstract description 22
- 238000005299 abrasion Methods 0.000 title description 3
- 239000007788 liquid Substances 0.000 claims abstract description 227
- 238000011084 recovery Methods 0.000 claims description 11
- 230000008569 process Effects 0.000 claims description 9
- 238000007599 discharging Methods 0.000 claims description 8
- 238000004891 communication Methods 0.000 claims description 3
- 238000000691 measurement method Methods 0.000 claims 1
- 238000005259 measurement Methods 0.000 abstract description 7
- 239000003921 oil Substances 0.000 description 8
- 238000012360 testing method Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 2
- 239000010729 system oil Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000001351 cycling effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 238000010079 rubber tapping Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a hydraulic system and a method for measuring the wear characteristics of hydraulic fluid, wherein the hydraulic system comprises the following components: the liquid inlet of the hydraulic pump is communicated with the liquid tank, and the liquid outlet of the hydraulic pump is communicated with the liquid tank; the liquid inlet of the electro-hydraulic proportional overflow valve is communicated with the liquid return port of the hydraulic pump, and the liquid discharge port of the electro-hydraulic proportional overflow valve is communicated with the liquid tank; the liquid return port of the electro-hydraulic proportional overflow valve can be selectively communicated with the liquid tank or communicated with the liquid inlet and return port of the pressure liquid tank, and the liquid inlet and return port of the pressure liquid tank can also be communicated with the liquid tank. The diversified circulation in the invention can ensure that more hydraulic fluid participates in the pump circulation, thereby improving the accuracy of the measurement of the wear characteristics of the hydraulic fluid. In addition, if current is input into the proportional electromagnet of the electro-hydraulic proportional relief valve due to misoperation, hydraulic fluid is relieved through the plug-in type two-way electromagnetic relief valve, so that load starting of a hydraulic system is avoided.
Description
Technical Field
The invention relates to the technical field of oil products and hydraulic component tests, in particular to a hydraulic system and a method for measuring the wear characteristics of hydraulic fluid.
Background
The hydraulic fluid is a working medium of a hydraulic system and has the functions of energy transmission and lubrication. The correct selection and use of hydraulic fluid is of great importance for improving the working performance and reliability, safety and life-prolonging of the hydraulic system, and therefore the determination of the wear characteristics of the hydraulic fluid is becoming very important.
In the existing hydraulic system for measuring the wear characteristics of hydraulic fluid, an oil pump pumps the hydraulic fluid in an oil tank into a system oil path, the hydraulic fluid returns to the oil tank after passing through the system oil path, the hydraulic fluid is circulated in a unitized mode, and finally the wear characteristics of the hydraulic fluid are judged by measuring the wear amount of the oil pump. However, there is a problem in that only a part of the hydraulic fluid in the tank participates in the circulation, which results in insufficient accuracy in the measurement of the wear characteristics of the hydraulic fluid.
Therefore, how to ensure that as much hydraulic fluid as possible in the oil tank participates in the circulation, thereby improving the accuracy of the measurement of the wear characteristics of the hydraulic fluid is a critical problem to be solved urgently by those skilled in the art.
Disclosure of Invention
The invention aims to ensure that as much hydraulic fluid as possible in an oil tank participates in circulation, thereby improving the accuracy of the measurement of the wear characteristics of the hydraulic fluid. In order to achieve the above purpose, the present invention provides the following technical solutions:
a hydraulic system for determining wear characteristics of hydraulic fluid, comprising:
The liquid inlet of the hydraulic pump is communicated with the liquid tank, and the liquid outlet of the hydraulic pump is communicated with the liquid tank;
The liquid inlet of the electro-hydraulic proportional overflow valve is communicated with the liquid return port of the hydraulic pump, and the liquid discharge port of the electro-hydraulic proportional overflow valve is communicated with the liquid tank;
The liquid return port of the electro-hydraulic proportional overflow valve can be selectively communicated with the liquid tank or communicated with the liquid inlet and return port of the pressure liquid tank, and the liquid inlet and return port of the pressure liquid tank can also be communicated with the liquid tank.
Preferably, a liquid return port of the electro-hydraulic proportional overflow valve is communicated with the liquid tank through a first plug-in type two-way electromagnetic valve, and the first plug-in type two-way electromagnetic valve comprises a first electromagnetic reversing valve for controlling on-off of the first plug-in type two-way electromagnetic valve; and the liquid return port of the electro-hydraulic proportional overflow valve is communicated with the liquid inlet and return port of the pressure liquid tank through a first plug-in type two-way valve.
Preferably, a one-way throttle valve is arranged on the liquid path between the first plug-in type two-way valve and the pressure liquid tank, the one-way throttle valve comprises a one-way valve and a throttle valve which are arranged in parallel, the one-way valve is used for filling liquid into the pressure liquid tank, and the throttle valve is used for enabling the pressure liquid tank to drain liquid in a preset time.
Preferably, a liquid return port of a throttle valve in the one-way throttle valve is communicated with the liquid tank through a second plug-in type two-way electromagnetic valve, and the second plug-in type two-way electromagnetic valve comprises a second electromagnetic reversing valve for controlling on-off of the second plug-in type two-way electromagnetic valve.
Preferably, the hydraulic pump is connected with the hydraulic motor, and the hydraulic pump is connected with the hydraulic motor;
the hydraulic motor's feed liquor mouth with the return liquid mouth intercommunication of hydraulic pump, hydraulic motor's drain hole with the liquid case intercommunication, hydraulic motor's return liquid mouth on the one hand through first cartridge formula two-way solenoid valve with the liquid case intercommunication, hydraulic motor's return liquid mouth on the other hand through first cartridge formula two-way valve with the feed liquor mouth intercommunication that returns of pressure fluid reservoir.
Preferably, after a liquid return path of the hydraulic motor and a liquid return path of the electro-hydraulic proportional overflow valve are intersected to form a first intersection, the first intersection is communicated with a liquid inlet and a liquid return port of the pressure liquid tank through the first plug-in type two-way valve; a first flow sensor is arranged on a liquid path between the first junction and the first plug-in type two-way valve; a second flow sensor is arranged on a liquid path between the liquid discharge port of the hydraulic motor and the liquid tank; and a third flow sensor is arranged on a liquid path between a liquid discharge port of the electro-hydraulic proportional overflow valve and the liquid tank.
Preferably, the automatic control device further comprises a plug-in type two-way electromagnetic overflow valve, wherein the plug-in type two-way electromagnetic overflow valve comprises a third electromagnetic directional valve for controlling the on-off of the plug-in type two-way electromagnetic overflow valve and further comprises an overflow valve; the liquid inlet of the plug-in type two-way electromagnetic overflow valve is communicated with the liquid return port of the hydraulic pump, and the liquid return port of the plug-in type two-way electromagnetic overflow valve is communicated with the liquid tank.
Preferably, the hydraulic pump further comprises a second plug-in type two-way valve, wherein the liquid return port of the hydraulic pump is respectively communicated with the liquid inlet of the plug-in type two-way electromagnetic overflow valve, the liquid inlet of the electro-hydraulic proportional overflow valve and the liquid inlet of the hydraulic motor through the second plug-in type two-way valve.
Preferably, a liquid path between a liquid return port of the hydraulic pump and a liquid inlet of the second plug-in type two-way valve is connected with a pressure sensor, and the pressure sensor is in communication connection with the electro-hydraulic proportional overflow valve.
The invention also discloses a measuring method, which is characterized by comprising the intermittent circulation of hydraulic fluid, wherein the intermittent circulation of the hydraulic fluid comprises the following steps:
s1: maintaining a preset current in a proportional electromagnet in the electro-hydraulic proportional overflow valve;
S2: in the front period of the cycle, the electromagnet DT1 of the first electromagnetic directional valve is powered off, the electromagnet DT2 of the second electromagnetic directional valve is powered off, the electromagnet DT3 of the third electromagnetic directional valve is powered off, hydraulic fluid output by the hydraulic pump respectively enters the electro-hydraulic proportional overflow valve and the hydraulic motor after passing through the second plug-in type two-way valve, and the hydraulic fluid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor is gathered and sequentially passes through the first flow sensor, the first plug-in type two-way valve and the one-way throttle valve to enter the pressure liquid tank;
S3: in the latter period of the cycle period, the electromagnet DT1 of the first electromagnetic directional valve is powered on, the electromagnet DT2 of the second electromagnetic directional valve is powered on, and the electromagnet DT3 of the third electromagnetic directional valve is powered off; hydraulic fluid output by the hydraulic pump passes through the second plug-in type two-way valve and then enters the electro-hydraulic proportional overflow valve and the hydraulic motor respectively, and the hydraulic fluid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor is converged and then flows back into the fluid tank through the first plug-in type two-way electromagnetic valve; meanwhile, the hydraulic liquid in the pressure liquid tank flows back to the liquid tank through the one-way throttle valve and the second plug-in type two-way electromagnetic valve in sequence.
Preferably, the pressure sensor is used for carrying out closed-loop control on the input current of the electro-hydraulic proportional relief valve; and controlling the liquid discharging time of the pressure liquid tank by adjusting a throttle valve in the one-way throttle valve.
Preferably, the method further comprises the steps of starting a hydraulic system, loading the hydraulic system and recovering power;
The starting of the hydraulic system comprises: the electromagnet of the first electromagnetic reversing valve is powered on, the electromagnet of the second electromagnetic reversing valve is powered off, the electromagnet of the third electromagnetic reversing valve is powered on, and the input current of the proportional electromagnet in the electro-hydraulic proportional overflow valve is zero; the hydraulic fluid flowing out of the liquid return port of the hydraulic pump passes through the second plug-in type two-way valve and then enters the plug-in type two-way electromagnetic overflow valve, the electro-hydraulic proportional overflow valve and the hydraulic motor respectively; the hydraulic liquid flowing out of the plug-in type two-way electromagnetic overflow valve flows back into the liquid tank, and the hydraulic liquid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor flows back into the liquid tank through the first plug-in type two-way electromagnetic valve after being collected;
The loading and power recovery of the hydraulic system comprises: the electromagnet of the first electromagnetic reversing valve is powered on, the electromagnet of the second electromagnetic reversing valve is powered off, and the electromagnet of the third electromagnetic reversing valve is powered off; the hydraulic fluid flowing out of the hydraulic pump passes through the second plug-in type two-way valve and then enters the electro-hydraulic proportional overflow valve and the hydraulic motor respectively, and the hydraulic fluid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor is converged and then flows back into the fluid tank through the first plug-in type two-way electromagnetic valve; then, inputting preset current to a proportional electromagnet of the electro-hydraulic proportional overflow valve so that the hydraulic pump outputs hydraulic fluid with preset pressure, and loading a hydraulic system is realized; in the process of loading the hydraulic system, the hydraulic motor does work to the hydraulic pump through the gear box so as to realize power recovery.
According to the technical scheme, in the hydraulic system, the hydraulic fluid flows back into the fluid tank through the electro-hydraulic proportional overflow valve after passing through the return port of the hydraulic pump in the starting stage and the loading stage of the hydraulic system. After the hydraulic system enters an intermittent cycle period, the hydraulic fluid is filled into the pressure fluid tank through the hydraulic pump and the electrohydraulic proportional relief valve in the front period of the intermittent cycle period. And discharging the liquid from the pressure liquid tank to the liquid tank at the later period of the intermittent circulation period, and simultaneously, returning part of the liquid in the liquid tank into the liquid tank through the hydraulic pump and the electro-hydraulic proportional overflow valve so as to participate in circulation. From the above process, it can be seen that one part of the hydraulic fluid participates in the circulation of filling and discharging of the pressure fluid tank, and the other part of the hydraulic fluid participates in the circulation of the hydraulic pump, the electro-hydraulic proportional overflow valve and the fluid tank. The diversified circulation in the invention can ensure that more hydraulic fluid participates in the pump circulation, thereby improving the accuracy of the measurement of the wear characteristics of the hydraulic fluid.
In addition, the hydraulic liquid flowing out from the liquid outlet of the hydraulic pump is divided into three liquid paths, one path enters the plug-in type two-way electromagnetic overflow valve, the other path enters the hydraulic motor, and the other path enters the electro-hydraulic proportional overflow valve. If current is input into the proportional electromagnet of the electro-hydraulic proportional overflow valve due to misoperation, hydraulic fluid is decompressed through the plug-in type two-way electromagnetic overflow valve, and accordingly load starting of a hydraulic system is avoided.
Drawings
In order to more clearly illustrate the solution of the embodiments of the present invention, the following description will briefly explain the drawings needed to be used in the embodiments, it being evident that the drawings in the following description are only some embodiments of the present invention and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic structural diagram of a hydraulic system for measuring wear characteristics of hydraulic fluid according to an embodiment of the present invention.
Wherein 1 is a hydraulic pump, 2 is an electrohydraulic proportional overflow valve, 3 is a pressure liquid tank, 4 is a first plug-in type two-way electromagnetic valve, 5 is a first electromagnetic directional valve, 6 is a first plug-in type two-way valve, 7 is a gear box, 8 is a motor, 9 is a hydraulic motor, 10 is a first flow sensor, 11 is a second flow sensor, 12 is a third flow sensor, 13 is a plug-in type two-way electromagnetic overflow valve, 14 is a third electromagnetic directional valve, 15 is an overflow valve, 16 is a second plug-in type two-way valve, 17 is a one-way throttle valve, 18 is a second plug-in type two-way electromagnetic valve, 19 is a second electromagnetic directional valve, 20 is a first junction, 21 is a second junction, 22 is a liquid tank, 23 is a pressure sensor, 101 is a liquid suction port of the hydraulic pump, 102 is a liquid discharge port of the hydraulic pump, 901 is a liquid discharge port of the hydraulic motor, DT1 is an electromagnet of the first electromagnetic directional valve, DT2 is an electromagnet of the second electromagnetic directional valve, DT3 is an electromagnet of the third electromagnetic directional valve, and MR is an electromagnet of the electrohydraulic proportional overflow valve.
Detailed Description
The invention discloses a hydraulic system for measuring the wear characteristics of hydraulic fluid, which can ensure that as much hydraulic fluid as possible in an oil tank participates in circulation, thereby improving the accuracy of measuring the wear characteristics of the hydraulic fluid. The invention also discloses a measuring method.
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to fall within the scope of the invention.
Furthermore, descriptions in this disclosure of "first," "second," and the like are provided for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature.
The invention discloses a hydraulic system for measuring the wear characteristics of hydraulic fluid, which comprises: a hydraulic pump 1, an electrohydraulic proportional overflow valve 2 and a pressure liquid tank 3. The liquid inlet of the hydraulic pump 1 is communicated with the liquid tank 22, and the liquid outlet of the hydraulic pump 1 is communicated with the liquid tank 22. The liquid inlet of the electro-hydraulic proportional overflow valve 2 is communicated with the liquid return port of the hydraulic pump 1, and the liquid discharge port of the electro-hydraulic proportional overflow valve 2 is communicated with the liquid tank 22. The liquid return port of the electro-hydraulic proportional overflow valve 2 can be selectively communicated with the liquid tank 22 or communicated with the liquid inlet and return port of the pressure liquid tank 3. The liquid inlet and return port of the pressure liquid tank 3 can also be communicated with a liquid tank 22.
In the hydraulic system of the present invention, the hydraulic fluid flows back to the tank 22 through the electro-hydraulic proportional relief valve 2 after passing through the return port of the hydraulic pump 1 in the start-up phase and the loading phase of the hydraulic system. After the hydraulic system enters an intermittent cycle, the hydraulic pump 1 and the electrohydraulic proportional relief valve 2 are used for filling the pressure liquid tank 3 in the front period of the intermittent cycle. The pressure tank 3 discharges liquid to the liquid tank 22 at a later period of the intermittent cycle. At the same time, the rest of the hydraulic fluid in the fluid tank 22 flows back into the fluid tank 22 through the hydraulic pump 1 and the electro-hydraulic proportional overflow valve 2 to participate in the circulation. From the above process, it can be seen that a part of the hydraulic fluid participates in the circulation of filling and discharging the pressure fluid tank 3, and another part of the hydraulic fluid participates in the circulation of the hydraulic pump 1, the electro-hydraulic proportional relief valve 2 and the fluid tank 22. The diversified circulation in the invention can ensure that more hydraulic fluid participates in the pump circulation, thereby improving the accuracy of the measurement of the wear characteristics of the hydraulic fluid.
In the start-up phase of the hydraulic system, the input current of the proportional electromagnet MR in the electro-hydraulic proportional relief valve 2 is zero, and the output pressure of the hydraulic pump 1 is zero, so that the unloading start is realized. In the loading stage of the hydraulic system, a preset current is input into the proportional electromagnet MR of the electro-hydraulic proportional relief valve 2 so that the hydraulic pump 1 outputs a preset pressure, thereby ensuring that the hydraulic system circulates under the preset pressure.
It should be noted that the pressure tank 3 is pre-filled with a certain amount of air to buffer the liquid filling of the pressure tank 3. In addition, the hydraulic pump 1 may be preferably a plunger pump.
The liquid return port of the electrohydraulic proportional overflow valve 2 is connected to a liquid tank 22 via a first plug-in two-way solenoid valve 4. The first plug-in type two-way electromagnetic valve 4 comprises a first electromagnetic reversing valve 5 for controlling the on-off of the first plug-in type two-way electromagnetic valve 4. The liquid return port of the electro-hydraulic proportional overflow valve 2 is communicated with the liquid inlet and return port of the pressure liquid tank 3 through a first plug-in type two-way valve 6.
In the starting phase, loading phase and the later period of the intermittent cycle period of the hydraulic system, the electromagnet DT1 of the first electromagnetic directional valve 5 of the first plug-in type two-way electromagnetic valve 4 is controlled to be electrified, so that the hydraulic liquid flowing out of the electro-hydraulic proportional overflow valve 2 can flow back into the liquid tank 22. When the electromagnet DT1 of the first electromagnetic directional valve 5 of the first plug-in type two-way electromagnetic valve 4 is controlled to lose electricity in the front period of the intermittent cycle, the hydraulic liquid flowing out of the electro-hydraulic proportional overflow valve 2 enters the pressure liquid tank 3 through the first plug-in type two-way valve 6, so that the liquid filling of the pressure liquid tank 3 is realized.
The first plug-in two-way valve 6 has the function of a one-way valve, and prevents the hydraulic fluid in the pressure fluid tank 3 from flowing back into the hydraulic pump 1 through the electro-hydraulic proportional relief valve 2.
A one-way throttle valve 17 is arranged on the liquid path between the first plug-in type two-way valve 6 and the pressure liquid tank 3. The unidirectional throttle valve 17 specifically includes a unidirectional valve and a throttle valve, which are arranged in parallel. During the filling of the pressure tank 3, the hydraulic fluid can enter the pressure tank 3 through the one-way valve. During the discharging of the pressure tank 3, the hydraulic fluid flowing out from the fluid inlet and outlet of the pressure tank 3 flows into the fluid tank 22 through the throttle valve.
The time of the intermittent cycle is determined, and the preceding period and the following period of the intermittent cycle are also determined. The hydraulic fluid charged into the pressure tank 3 is completely discharged in the latter period. It is thus possible to ensure that the hydraulic fluid in the pressure tank 3 is completely discharged in the latter period by adjusting the opening degree of the throttle valve in the one-way throttle valve 17.
During the discharging process of the pressure liquid tank 3, the hydraulic liquid in the pressure liquid tank 3 flows into the second plug-in type two-way electromagnetic valve 18 through the throttle valve in the one-way throttle valve 17, and then flows into the liquid tank 22 through the second plug-in type two-way electromagnetic valve 18. The second plug-in type two-way electromagnetic valve 18 comprises a second electromagnetic directional valve 19, and the second electromagnetic directional valve 19 is used for controlling the on-off of the second plug-in type two-way electromagnetic valve 18. The electromagnet DT2 of the second electromagnetic directional valve 19 is in a power-off state during the start-up phase, the loading phase, and the period of the intermittent cycle of the hydraulic system. At the latter stage of the intermittent cycle, the electromagnet DT2 of the second electromagnetic directional valve 19 is powered to realize the tapping of the pressure tank 3.
The hydraulic system of the invention has very high working power, so the power consumption is very high. In addition, since the heat generation amount of the hydraulic system is large, a large amount of cooling water is required to cool the hydraulic fluid. This results in very high operating costs for the hydraulic system. In order to save the cost, and simultaneously, the invention is provided with a power recovery module in the hydraulic system in order to meet the actual working conditions of industry. The power recovery module comprises in particular a hydraulic motor 9 and a gearbox 7. The output of the gearbox 7 is connected to the hydraulic pump 1, and the input of the gearbox 7 is connected to an electric motor 8 on the one hand and to a hydraulic motor 9 on the other hand. Similar to the connection mode of the electrohydraulic proportional overflow valve 2, the liquid inlet of the hydraulic motor 9 is communicated with the liquid return port of the hydraulic pump 1, and the liquid return port of the hydraulic motor 9 is communicated with the liquid tank 22 through the first plug-in type two-way electromagnetic valve 4 on one hand and the liquid inlet and return port of the pressure liquid tank 3 through the first plug-in type two-way valve 6 on the other hand.
In the start-up phase of the hydraulic system, the input current to the proportional solenoid MR in the electromagnetic proportional relief valve 2 is zero, and therefore the output pressure of the hydraulic pump 1 is also zero. A part of the hydraulic fluid flowing out from the hydraulic pump 1 flows back into the tank 22 after passing through the hydraulic motor 9. Since the pressure of the hydraulic fluid is zero, the hydraulic motor 9 does not perform work at this time, and power recovery is not performed. In the loading phase and the intermittent circulation phase of the hydraulic system, a preset current is input to the proportional electromagnet MR in the electro-hydraulic proportional relief valve 2, so that the hydraulic pump 1 outputs a preset pressure, and the hydraulic motor 9 works under the action of the preset pressure, thereby realizing power recovery. The input power of the hydraulic pump 1 is the sum of the output power of the motor 8 and the recovered power of the hydraulic motor 9.
From the above description, it can be known that the liquid return port of the electro-hydraulic proportional overflow valve 2 and the liquid return port of the hydraulic motor 9 can be communicated with the liquid inlet and return port of the pressure liquid tank 3 through the first plug-in type two-way valve 6. Based on the consideration of simplifying the liquid path structure, the invention limits the liquid return path of the hydraulic motor 9 to be intersected with the liquid return path of the electro-hydraulic proportional overflow valve 2 to form a first intersection point 20, and then the first intersection point is communicated with the liquid inlet and the liquid return port of the pressure liquid tank 3 through the first plug-in type two-way valve 6. Based on the consideration of simplified liquid path structure, the invention limits the liquid return path of the hydraulic motor 9 to be communicated with the liquid inlet of the first plug-in type two-way electromagnetic valve 4 after being intersected with the liquid return path of the electro-hydraulic proportional overflow valve 2 to form a second intersection point 21.
The present invention provides a first flow sensor 10 in the fluid path between the first junction 20 and the first plug-in two-way valve 6. A second flow sensor 11 is provided in the fluid path between the drain of the hydraulic motor 9 and the tank 22. A third flow sensor 12 is provided in the liquid path between the drain port of the electro-hydraulic proportional relief valve 2 and the liquid tank 22. The present invention characterizes the output flow of the hydraulic pump 1 by the sum of the measurements of the first flow sensor 10, the second flow sensor 11 and the third flow sensor 12. The wear characteristics of the hydraulic fluid can be measured by the variation of the test time and the output flow rate of the hydraulic pump 1.
From the above description, it is clear that it is necessary to ensure zero input current to the proportional solenoid MR in the electro-hydraulic proportional relief valve 2 during the start-up phase of the hydraulic system, so as to achieve an unloaded start-up of the motor 8. However, in the actual operation, a certain current is input to the electro-hydraulic proportional relief valve 2 due to misoperation, so that load starting occurs, and a safety problem is caused. In order to avoid the load starting, the invention makes the following design: the invention is additionally provided with the plug-in type two-way electromagnetic overflow valve 13. The cartridge type two-way electromagnetic spill valve 13 includes a third electromagnetic directional valve 14 and a spill valve 15. The third electromagnetic directional valve 14 is used for controlling the on-off of the plug-in type two-way electromagnetic relief valve 13. The relief valve 15 is used to conduct when the pressure in the liquid path exceeds the upper pressure limit value, so that the plug-in type two-way electromagnetic relief valve 13 conducts to perform relief pressure. The liquid inlet of the plug-in type two-way electromagnetic overflow valve 13 is communicated with the liquid return port of the hydraulic pump 1, and the liquid return port of the plug-in type two-way electromagnetic overflow valve 13 is communicated with the liquid tank 22.
The plug-in type two-way electromagnetic relief valve 13 is connected with the electro-hydraulic proportional relief valve 2 and the hydraulic motor 9 in parallel. In the start-up phase of the hydraulic system, the electromagnet DT3 of the third electromagnetic directional valve 14 is energized. The hydraulic fluid flowing out from the return port of the hydraulic pump 1 is divided into three fluid paths, one path enters the plug-in type two-way electromagnetic relief valve 13, the other path enters the hydraulic motor 9, and the other path enters the electro-hydraulic proportional relief valve 2. If current is input into the proportional electromagnet of the electro-hydraulic proportional relief valve 2 due to misoperation at the moment, hydraulic fluid is relieved through the plug-in type two-way electromagnetic relief valve 13, so that the load starting of a hydraulic system is avoided.
The electromagnet DT3 of the third electromagnetic directional valve 14 is in a power-off state in both the charging stage and the intermittent circulation stage of the hydraulic system. The cartridge type two-way electromagnetic spill valve 13 at this time functions as a safety valve.
The invention also provides a second plug-in two-way valve 16 at the liquid return port of the hydraulic pump 1. The liquid return port of the hydraulic pump 1 is respectively communicated with the liquid inlet of the plug-in type two-way electromagnetic overflow valve 13, the liquid inlet of the electro-hydraulic proportional overflow valve 2 and the liquid inlet of the hydraulic motor 9 through a second plug-in type two-way valve 16. The second cartridge type two-way valve 16 functions as a check valve to prevent the hydraulic fluid from flowing back into the hydraulic pump 1, thereby ensuring stable operation of the hydraulic system.
The valve referred to herein includes a cartridge type two-way valve, a cartridge type two-way electromagnetic valve, and a cartridge type two-way electromagnetic spill valve. The plug-in type two-way valve has the advantages of large circulation capacity and small pressure loss, and is suitable for a large-flow hydraulic system. The plug-in type two-way valve is equivalent to a large-sized one-way valve. The plug-in type two-way electromagnetic valve is characterized in that an electromagnetic reversing valve is arranged on the basis of the plug-in type two-way valve, and the on-off of the plug-in type two-way electromagnetic valve is controlled through the electromagnetic reversing valve. The plug-in type two-way electromagnetic overflow valve is characterized in that an overflow valve is arranged on the basis of a plug-in type two-way electromagnetic valve, so that the on-off of the plug-in type two-way electromagnetic overflow valve can be controlled through an electromagnetic reversing valve of the plug-in type two-way electromagnetic overflow valve, and the overflow of the plug-in type two-way electromagnetic overflow valve is controlled through the overflow valve, namely, the overflow valve is a pilot valve of the plug-in type two-way electromagnetic overflow valve, and the plug-in type two-way electromagnetic overflow valve has the function of a safety valve.
As is apparent from the above description, the hydraulic pump 1 is caused to output a preset pressure by inputting a preset current to the proportional solenoid MR of the electro-hydraulic proportional relief valve 2. The present invention has been devised in order to ensure that the hydraulic pump 1 can accurately output a preset pressure as follows: the hydraulic pump 1 is connected with a pressure sensor 23 on a liquid path between a liquid return port of the hydraulic pump 1 and a liquid inlet port of a second plug-in type two-way valve 16, the pressure sensor 23 is used for detecting the output pressure of the hydraulic pump 1, and the pressure sensor 23 is in communication connection with an electrohydraulic proportional overflow valve 2. The pressure sensor 23 and the electrohydraulic proportional relief valve 2 form closed loop control. If the pressure sensor 23 detects that the output pressure of the hydraulic pump 1 is smaller than the preset pressure, the input current to the proportional solenoid MR of the electro-hydraulic proportional relief valve 2 is increased. If the pressure sensor 23 detects that the output pressure of the hydraulic pump 1 is greater than the preset pressure, the input current to the proportional solenoid MR of the electro-hydraulic proportional relief valve 2 is reduced.
The invention also discloses a measuring method based on the hydraulic system for measuring the wear characteristics of the hydraulic fluid, which sequentially comprises the steps of starting the hydraulic system, loading and power recovery of the hydraulic system and intermittent circulation of the hydraulic fluid.
Starting a hydraulic system: the electromagnet DT1 of the first electromagnetic directional valve 5 is powered on, the electromagnet DT2 of the second electromagnetic directional valve 19 is powered off, and the electromagnet DT3 of the third electromagnetic directional valve 14 is powered on. Meanwhile, the input current of the proportional electromagnet MR in the electro-hydraulic proportional relief valve 2 is zero. The motor 8 is started, and the hydraulic pump 1 and the hydraulic motor 9 are driven to rotate through the gear box 7. The liquid inlet of the hydraulic pump 1 absorbs hydraulic liquid from the liquid tank 22, and the hydraulic liquid output by the liquid return port of the hydraulic pump 1 is divided into three night paths after passing through the second plug-in type two-way valve 16: one path sequentially passes through the hydraulic motor 9 and the first plug-in type two-way electromagnetic valve 4 and then flows back to the liquid tank 22, the other path passes through the plug-in type two-way electromagnetic overflow valve 13 and then returns to the liquid tank 22, and the other path sequentially passes through the electro-hydraulic proportional overflow valve 2 and the first plug-in type two-way electromagnetic valve 4 and then flows back to the liquid tank 22. In the process, since the input current of the proportional electromagnet MR of the electro-hydraulic proportional overflow valve 2 is zero, the output pressure of the hydraulic pump 1 is zero, so that the unloading starting of the motor 8 is realized, and the hydraulic system has no pressure impact.
If a certain current is input to the proportional electromagnet MR of the electro-hydraulic proportional relief valve 2 due to misoperation, hydraulic fluid is unloaded through the plug-in electromagnetic relief valve 15, so that the load start of the motor 8 is avoided, and the safe start of the hydraulic system is ensured.
Loading and power recovery of the hydraulic system: the electromagnet DT1 of the first electromagnetic directional valve 5 is powered on, the electromagnet DT2 of the second electromagnetic directional valve 19 is powered off, and the electromagnet DT3 of the third electromagnetic directional valve 14 is powered off. The hydraulic fluid discharged from the hydraulic pump 1 is split into two fluid paths after passing through the second plug-in two-way valve 16: one path of the water flows back to the liquid tank 22 after sequentially passing through the hydraulic motor 9 and the first plug-in type two-way electromagnetic valve 4. One path of the liquid flows back into the liquid tank 22 after passing through the electro-hydraulic proportional overflow valve 2 and the first plug-in type two-way electromagnetic valve 4 in sequence. And then, inputting preset current to the proportional electromagnet MR of the electro-hydraulic proportional relief valve 2 so as to enable the hydraulic pump 1 to output hydraulic fluid with preset pressure, thereby realizing loading of a hydraulic system. The closed-loop control of the electro-hydraulic proportional relief valve 2 by the pressure sensor 23 can enable the hydraulic pump 1 to accurately output a preset pressure so as to enable the hydraulic system to test under the preset pressure.
The rotational speed of the hydraulic pump 1 is controlled by a motor 8. Part of the output power of the hydraulic pump 1 is lost by the electro-hydraulic proportional overflow valve 2, so that the hydraulic fluid heats, the rest of the output power is converted into mechanical energy through the hydraulic motor 9 and is returned to the input end of the hydraulic pump 1 through the gear box 7, and the power recovery of a hydraulic system is realized. The input power of the hydraulic pump 1 is the sum of the output power of the motor 8 and the recovered power of the hydraulic motor 9, irrespective of the mechanical friction loss and the volume loss.
Intermittent cycling of hydraulic system: the preset current in the proportional solenoid MR in the electro-hydraulic proportional relief valve 2 is maintained so that the output pressure of the hydraulic pump 1 is maintained at the preset pressure. In one embodiment of the invention, the intermittent cycle period of the hydraulic fluid in the hydraulic system is 1min. In the first 45s of the 1min cycle period, the electromagnet DT1 of the first electromagnetic directional valve 5 is powered off, the electromagnet DT2 of the second electromagnetic directional valve 19 is powered off, and the electromagnet DT3 of the third electromagnetic directional valve 14 is powered off. The hydraulic fluid output by the hydraulic pump 1 passes through a second plug-in type two-way valve 16 and then enters the electro-hydraulic proportional overflow valve 2 and the hydraulic motor 9 respectively. The hydraulic fluid flowing out from the electro-hydraulic proportional relief valve 2 and the hydraulic motor 9 is collected and then sequentially enters the pressure fluid tank 3 through the first flow sensor 10, the first plug-in type two-way valve 6 and the one-way throttle valve 17 so as to fill the pressure fluid tank 3.
In the rear 15s, the electromagnet DT1 of the first electromagnetic directional valve 5 is powered on, the electromagnet DT2 of the second electromagnetic directional valve 19 is powered on, and the electromagnet DT3 of the third electromagnetic directional valve 14 is powered off. The hydraulic fluid output by the hydraulic pump 1 is divided into two fluid paths after passing through the second plug-in type two-way valve 16: one path of the water flows back to the liquid tank 22 after passing through the hydraulic motor 9 and the first plug-in type two-way electromagnetic valve 4 in sequence. One path of the liquid flows back to the liquid tank 22 after passing through the electro-hydraulic proportional overflow valve 2 and the first plug-in type two-way electromagnetic valve 4 in sequence. Simultaneously, the hydraulic fluid in the pressure fluid tank 3 flows back to the fluid tank 22 through the one-way throttle valve 17 and the second plug-in type two-way electromagnetic valve 18 in sequence under the action of air pressure. The drain time of the pressure tank 3 can be set by adjusting the opening degree of the throttle valve in the one-way throttle valve 17. The hydraulic fluid in the fluid tank 22 can be fully circulated in the hydraulic system by the reciprocating operation, so that the test result of the hydraulic fluid abrasion special direction is accurate and reliable.
Finally, it is also noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises an element.
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (12)
1. A hydraulic system for determining wear characteristics of a hydraulic fluid, comprising:
The liquid inlet of the hydraulic pump is communicated with the liquid tank, and the liquid outlet of the hydraulic pump is communicated with the liquid tank;
The liquid inlet of the electro-hydraulic proportional overflow valve is communicated with the liquid return port of the hydraulic pump, and the liquid discharge port of the electro-hydraulic proportional overflow valve is communicated with the liquid tank;
The liquid return port of the electro-hydraulic proportional overflow valve can be selectively communicated with the liquid tank or communicated with the liquid inlet and return port of the pressure liquid tank, and the liquid inlet and return port of the pressure liquid tank can also be communicated with the liquid tank.
2. The hydraulic system for measuring the wear characteristics of hydraulic fluid according to claim 1, wherein a fluid return port of the electro-hydraulic proportional relief valve is communicated with the fluid tank through a first plug-in type two-way electromagnetic valve on one hand, and the first plug-in type two-way electromagnetic valve comprises a first electromagnetic directional valve for controlling on-off of the first plug-in type two-way electromagnetic valve; and the liquid return port of the electro-hydraulic proportional overflow valve is communicated with the liquid inlet and return port of the pressure liquid tank through a first plug-in type two-way valve.
3. The hydraulic system for measuring wear characteristics of hydraulic fluid according to claim 2, wherein a one-way throttle valve is provided on a fluid path between the first cartridge-type two-way valve and the pressure tank, the one-way throttle valve including a one-way valve and a throttle valve provided in parallel, the one-way valve being for filling the pressure tank with fluid, the throttle valve being for discharging the pressure tank with fluid within a preset time.
4. The hydraulic system for measuring wear characteristics of hydraulic fluid according to claim 3, wherein the return port of the throttle valve in the one-way throttle valve is communicated with the fluid tank through a second cartridge type two-way electromagnetic valve, and the second cartridge type two-way electromagnetic valve comprises a second electromagnetic directional valve for controlling on-off of the second cartridge type two-way electromagnetic valve.
5. The hydraulic system for determining wear characteristics of a hydraulic fluid according to claim 4, further comprising a hydraulic motor and a gearbox, an output of said gearbox being connected to said hydraulic pump, an input of said gearbox being connected to an electric motor on the one hand and to said hydraulic motor on the other hand;
the hydraulic motor's feed liquor mouth with the return liquid mouth intercommunication of hydraulic pump, hydraulic motor's drain hole with the liquid case intercommunication, hydraulic motor's return liquid mouth on the one hand through first cartridge formula two-way solenoid valve with the liquid case intercommunication, hydraulic motor's return liquid mouth on the other hand through first cartridge formula two-way valve with the feed liquor mouth intercommunication that returns of pressure fluid reservoir.
6. The hydraulic system for measuring the wear characteristics of hydraulic fluid according to claim 5, wherein the return fluid path of the hydraulic motor is communicated with the return fluid inlet of the pressure fluid tank through the first plug-in type two-way valve after being intersected with the return fluid path of the electro-hydraulic proportional overflow valve to form a first intersection; a first flow sensor is arranged on a liquid path between the first junction and the first plug-in type two-way valve; a second flow sensor is arranged on a liquid path between the liquid discharge port of the hydraulic motor and the liquid tank; and a third flow sensor is arranged on a liquid path between a liquid discharge port of the electro-hydraulic proportional overflow valve and the liquid tank.
7. The hydraulic system for measuring wear characteristics of hydraulic fluid according to claim 6, further comprising a cartridge type two-way electromagnetic relief valve including a third electromagnetic directional valve for controlling on-off of the cartridge type two-way electromagnetic relief valve, further comprising a relief valve; the liquid inlet of the plug-in type two-way electromagnetic overflow valve is communicated with the liquid return port of the hydraulic pump, and the liquid return port of the plug-in type two-way electromagnetic overflow valve is communicated with the liquid tank.
8. The hydraulic system for measuring wear characteristics of hydraulic fluid according to claim 7, further comprising a second cartridge type two-way valve, wherein the return port of the hydraulic pump is respectively communicated with the inlet port of the cartridge type two-way electromagnetic spill valve, the inlet port of the electro-hydraulic proportional spill valve, and the inlet port of the hydraulic motor through the second cartridge type two-way valve.
9. The hydraulic system for determining wear characteristics of hydraulic fluid according to claim 8, wherein a pressure sensor is connected to a fluid path between a return port of the hydraulic pump and a fluid inlet port of the second cartridge two-way valve, the pressure sensor being in communication with the electro-hydraulic proportional relief valve.
10. A method for measuring the wear characteristics of a hydraulic fluid using the hydraulic system according to claim 9, comprising intermittent circulation of the hydraulic fluid, the intermittent circulation of the hydraulic fluid comprising the steps of:
s1: maintaining a preset current in a proportional electromagnet in the electro-hydraulic proportional overflow valve;
S2: in the front period of the cycle, the electromagnet DT1 of the first electromagnetic directional valve is powered off, the electromagnet DT2 of the second electromagnetic directional valve is powered off, the electromagnet DT3 of the third electromagnetic directional valve is powered off, hydraulic fluid output by the hydraulic pump respectively enters the electro-hydraulic proportional overflow valve and the hydraulic motor after passing through the second plug-in type two-way valve, and the hydraulic fluid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor is gathered and sequentially passes through the first flow sensor, the first plug-in type two-way valve and the one-way throttle valve to enter the pressure liquid tank;
S3: in the latter period of the cycle period, the electromagnet DT1 of the first electromagnetic directional valve is powered on, the electromagnet DT2 of the second electromagnetic directional valve is powered on, and the electromagnet DT3 of the third electromagnetic directional valve is powered off; hydraulic fluid output by the hydraulic pump passes through the second plug-in type two-way valve and then enters the electro-hydraulic proportional overflow valve and the hydraulic motor respectively, and the hydraulic fluid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor is converged and then flows back into the fluid tank through the first plug-in type two-way electromagnetic valve; meanwhile, the hydraulic liquid in the pressure liquid tank flows back to the liquid tank through the one-way throttle valve and the second plug-in type two-way electromagnetic valve in sequence.
11. The measurement method according to claim 10, wherein the input current of the electro-hydraulic proportional relief valve is closed-loop controlled by the pressure sensor; and controlling the liquid discharging time of the pressure liquid tank by adjusting a throttle valve in the one-way throttle valve.
12. The method of claim 10, further comprising starting a hydraulic system, loading the hydraulic system, and recovering power;
The starting of the hydraulic system comprises: the electromagnet of the first electromagnetic reversing valve is powered on, the electromagnet of the second electromagnetic reversing valve is powered off, the electromagnet of the third electromagnetic reversing valve is powered on, and the input current of the proportional electromagnet in the electro-hydraulic proportional overflow valve is zero; the hydraulic fluid flowing out of the liquid return port of the hydraulic pump passes through the second plug-in type two-way valve and then enters the plug-in type two-way electromagnetic overflow valve, the electro-hydraulic proportional overflow valve and the hydraulic motor respectively; the hydraulic liquid flowing out of the plug-in type two-way electromagnetic overflow valve flows back into the liquid tank, and the hydraulic liquid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor flows back into the liquid tank through the first plug-in type two-way electromagnetic valve after being collected;
The loading and power recovery of the hydraulic system comprises: the electromagnet of the first electromagnetic reversing valve is powered on, the electromagnet of the second electromagnetic reversing valve is powered off, and the electromagnet of the third electromagnetic reversing valve is powered off; the hydraulic fluid flowing out of the hydraulic pump passes through the second plug-in type two-way valve and then enters the electro-hydraulic proportional overflow valve and the hydraulic motor respectively, and the hydraulic fluid flowing out of the electro-hydraulic proportional overflow valve and the hydraulic motor is converged and then flows back into the fluid tank through the first plug-in type two-way electromagnetic valve; afterwards, the preset current is input to a proportional electromagnet of the electro-hydraulic proportional overflow valve, so that the hydraulic pump outputs hydraulic fluid with preset pressure, and loading of a hydraulic system is realized; in the process of loading the hydraulic system, the hydraulic motor does work to the hydraulic pump through the gear box so as to realize power recovery.
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102937125A (en) * | 2012-11-06 | 2013-02-20 | 三一重工股份有限公司 | Testing system of hydraulic motor |
| CN106151171A (en) * | 2016-07-04 | 2016-11-23 | 意宁液压股份有限公司 | A kind of hydraulic motor and hydraulic pump universal test hydraulic system |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4335328A1 (en) * | 1993-10-18 | 1995-04-20 | Battenfeld Gmbh | Hydraulic operating system for injection molding machines |
| CN103807223B (en) * | 2014-02-10 | 2015-10-28 | 太原理工大学 | Single oil hydraulic motor double-loop control system |
| CN106762979B (en) * | 2016-12-08 | 2018-05-01 | 燕山大学 | A kind of electrical power reclaiming type hydraulic pump motor reliability test and method |
| CN107132340A (en) * | 2017-05-09 | 2017-09-05 | 济南大学 | A kind of assay method of hydraulic fluid wearing character |
| CN106940276A (en) * | 2017-05-09 | 2017-07-11 | 济南大学 | A kind of hydraulic fluid wearing character determines device and its application method |
| CN210003606U (en) * | 2019-06-25 | 2020-01-31 | 湖南省产商品质量监督检验研究院 | hydraulic cylinder durability testing device with power recovery function |
| CN114458661B (en) * | 2021-03-03 | 2024-03-29 | 凌云(宜昌)航空装备工程有限公司 | Towing type oil pump truck system and control method |
| CN113669328B (en) * | 2021-08-23 | 2023-11-21 | 徐州徐工挖掘机械有限公司 | Device for detecting performance of breather valve of oil tank and test method thereof |
| CN114017535A (en) * | 2021-12-02 | 2022-02-08 | 大连大高阀门股份有限公司 | Hydraulic control system of gas-liquid linkage driving device |
-
2022
- 2022-05-27 CN CN202210588229.6A patent/CN114922883B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102937125A (en) * | 2012-11-06 | 2013-02-20 | 三一重工股份有限公司 | Testing system of hydraulic motor |
| CN106151171A (en) * | 2016-07-04 | 2016-11-23 | 意宁液压股份有限公司 | A kind of hydraulic motor and hydraulic pump universal test hydraulic system |
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