CN107327430B - Hydraulic comprehensive test system for power recovery - Google Patents
Hydraulic comprehensive test system for power recovery Download PDFInfo
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- CN107327430B CN107327430B CN201710624880.3A CN201710624880A CN107327430B CN 107327430 B CN107327430 B CN 107327430B CN 201710624880 A CN201710624880 A CN 201710624880A CN 107327430 B CN107327430 B CN 107327430B
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- 238000011084 recovery Methods 0.000 title claims abstract description 95
- 238000012360 testing method Methods 0.000 title claims abstract description 24
- 239000003638 chemical reducing agent Substances 0.000 claims abstract description 38
- 239000003921 oil Substances 0.000 claims description 267
- 230000001502 supplementing effect Effects 0.000 claims description 25
- 239000010720 hydraulic oil Substances 0.000 claims description 18
- 239000002699 waste material Substances 0.000 abstract description 5
- 238000004064 recycling Methods 0.000 abstract description 3
- 238000004134 energy conservation Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 239000013589 supplement Substances 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
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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
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/021—Gearings
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/025—Test-benches with rotational drive means and loading means; Load or drive simulation
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/26—Power control functions
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a hydraulic comprehensive test system for power recovery, which comprises a main oil pump, a tested hydraulic motor, a tested speed reducer, a loading hydraulic motor, a power recovery motor, a main oil way, a power recovery oil way and an axial force loading device, wherein the main oil pump is connected with the main oil way; the main oil circuit comprises the main oil pump, a main oil circuit bridge type loop and a tested hydraulic motor; the oil outlet of the main oil pump is connected to the oil inlet of the tested hydraulic motor through a main oil circuit bridge type loop, and the oil outlet of the tested hydraulic motor is connected back to the oil inlet of the main oil pump through the main oil circuit bridge type loop. According to the invention, the load is simulated by using the loading hydraulic motor, partial power is recycled by using the power recycling oil way to drive the main oil pump, so that the performance and service life of the hydraulic motor and the speed reducer are tested, the waste of energy is avoided, the energy saving and emission reduction advantages are realized, and in addition, the performance and service life of the speed reducer under the condition of axial force can be tested.
Description
Technical Field
The invention belongs to the technical field of hydraulic equipment testing, and particularly relates to a hydraulic comprehensive testing system for power recovery.
Background
After the hydraulic motor and the speed reducer are manufactured, the service life of the hydraulic motor and the speed reducer under the industrial control conditions of specified pressure, rotation speed and the like needs to be detected, and therefore a test bed is needed to test the hydraulic motor and the speed reducer. In the conventional hydraulic motor and speed reducer combined test stand, a load is simulated by using a proportional relief valve. However, with the test bed, the proportional overflow valve generates heat to cause the oil temperature to rise, namely, most of energy is converted into heat energy by the proportional overflow valve in the test process, so that the energy waste is caused, namely, the existing test bed is not energy-saving enough, and the energy waste is relatively large.
Under the actual working condition of the speed reducer, the speed reducer cannot be guaranteed to be in a flat state all the time, once the speed reducer is in an inclined state, the machine shell can apply axial force to the shaft of the speed reducer necessarily due to gravity, and at the moment, the working condition changes, so that the performance and the service life of the speed reducer can be influenced necessarily.
However, the existing hydraulic test system can only test the performance and service life of the speed reducer under the condition of no axial force.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide a hydraulic comprehensive test system for power recovery.
In order to solve the technical problems, the invention adopts the following technical scheme:
the utility model provides a hydraulic pressure integrated test system of power recovery which characterized in that: the device comprises a main oil pump, a tested hydraulic motor, a tested speed reducer, a loading hydraulic motor, a power recovery motor, a main oil circuit, a power recovery oil circuit and an axial force loading device;
the main oil circuit comprises the main oil pump, a main oil circuit bridge type loop and the tested hydraulic motor; an oil outlet of the main oil pump is connected to an oil inlet of the tested hydraulic motor through the main oil circuit bridge type loop, and the oil outlet of the tested hydraulic motor is connected back to the oil inlet of the main oil pump through the main oil circuit bridge type loop;
the power recovery oil circuit comprises the loading hydraulic motor, a power recovery bridge circuit and the power recovery motor; the oil outlet of the loading hydraulic motor is connected to the oil inlet of the power recovery motor through the power recovery bridge circuit, and the oil outlet of the power recovery motor is connected back to the oil inlet of the loading hydraulic motor through the power recovery bridge circuit;
the tested hydraulic motor, the tested speed reducer, the loading speed reducer and the loading hydraulic motor are sequentially and rigidly connected; the power recovery motor is also rigidly connected with the main oil pump;
the axial force loading device comprises a hydraulic oil cylinder, a loading bracket, a loading oil pump, a loading filter, a loading electromagnetic directional valve, a loading overflow valve and a hydraulic lock;
the piston rod of the hydraulic oil cylinder is connected with the loading bracket, and the loading bracket is connected to the shell of the tested speed reducer;
an oil inlet of the loading oil pump is connected to a main oil tank through a ball valve, an oil outlet of the loading oil pump is connected to the loading filter through a loading one-way valve, and the loading filter is simultaneously connected with the loading overflow valve and a P oil port of the loading electromagnetic reversing valve; the hydraulic oil cylinder is characterized in that the loading overflow valve is connected back to the main oil tank, an oil port A of the loading electromagnetic reversing valve is connected to a forward oil port of the hydraulic oil cylinder through a positive side one-way valve of the hydraulic lock, an oil port B of the loading electromagnetic reversing valve is connected to a reverse oil port of the hydraulic oil cylinder through a reverse side one-way valve of the hydraulic lock, and an oil port O of the loading electromagnetic reversing valve is connected back to the main oil tank.
According to the technical scheme, the performance and the service life of the hydraulic motor and the speed reducer can be tested, the load is simulated by using the loading hydraulic motor, partial power is recycled by using the power recycling oil way to drive the main oil pump, the energy waste is avoided, the system has the advantages of energy conservation and emission reduction, in addition, the system can also load the axial force of the speed reducer, the performance and the service life of the speed reducer under the condition of being subjected to the axial force are tested, and the system has the advantage of wide testing application.
Drawings
Fig. 1 is a diagram of a hydraulic system of the present invention.
Detailed Description
As shown in fig. 1, the hydraulic integrated test system for power recovery of the present invention includes a main oil pump 33, a tested hydraulic motor 69, a tested speed reducer 67.2, a loading speed reducer 67.1, a loading hydraulic motor 64, a power recovery motor 38, a main oil path, a power recovery oil path, a make-up oil path, and an axial force loading device.
The main oil path is a closed circulation oil path, and includes a main oil pump 33, a main oil path bridge circuit, and a hydraulic motor 69 to be tested. The oil outlet of the main oil pump 33 is connected to the oil inlet of the tested hydraulic motor 69 via a main oil path bridge circuit 33.1, and the oil outlet of the tested hydraulic motor 69 is connected to the oil inlet of the main oil pump 33 via a main oil path bridge circuit.
The main oil circuit bridge type loop is formed by serially connecting a first hydraulic control check valve 44.5, a second hydraulic control check valve 44.6, a third hydraulic control check valve 44.7 and a fourth hydraulic control check valve 44.8, wherein a first node of a main oil circuit is arranged between the first hydraulic control check valve 44.5 and the second hydraulic control check valve 44.6, a second node of the main oil circuit is arranged between the second hydraulic control check valve 44.6 and the third hydraulic control check valve 44.7, a third node of the main oil circuit is arranged between the third hydraulic control check valve 44.7 and the fourth hydraulic control check valve 44.8, and a fourth node of the main oil circuit is arranged between the fourth hydraulic control check valve 44.8 and the first hydraulic control check valve 44.5. The first hydraulic control check valve 44.5, the second hydraulic control check valve 44.6, the third hydraulic control check valve 44.7 and the fourth hydraulic control check valve 44.8 are respectively controlled to be opened and closed by a two-position four-way electromagnetic reversing valve.
Specifically, the oil outlet of the main oil pump 33 is connected to the main oil passage first node of the main oil passage bridge circuit, the main oil passage second node of the main oil passage bridge circuit is connected to the oil inlet of the hydraulic motor 69 to be measured, the oil outlet of the hydraulic motor 69 to be measured is connected to the main oil passage fourth node of the main oil passage bridge circuit, and the main oil passage third node of the main oil passage bridge circuit is connected to the oil inlet of the main oil pump 33.
Therefore, the main oil path is divided into four sections, namely, the oil path between the oil outlet of the main oil pump 33 and the first node of the main oil path bridge circuit is the first main oil path section 101, the oil path between the second node of the main oil path bridge circuit and the oil inlet of the tested hydraulic motor 69 is the second main oil path section 102, the oil path between the oil outlet of the tested hydraulic motor and the fourth node of the main oil path bridge circuit is the third main oil path section 103, and the oil path between the third node of the main oil path bridge circuit and the oil inlet of the main oil pump 33 is the fourth main oil path section 104.
The tested hydraulic motor 69, the tested speed reducer 67.2, the loading speed reducer 67.1 and the loading hydraulic motor 64 are rigidly connected in sequence. The power recovery motor 38 is also rigidly coupled to the main oil pump 33.
The power recovery circuit is also a closed circuit including the charge hydraulic motor 64, the power recovery bridge circuit, and the power recovery motor 38. The oil outlet of the loading hydraulic motor 64 is connected to the oil inlet of the power recovery motor 38 via a power recovery bridge circuit 64.1, and the oil outlet of the power recovery motor 38 is connected to the oil inlet of the loading hydraulic motor 64 via a power recovery bridge circuit 64.1.
The power recovery bridge circuit 64.1 is formed by serially connecting a fifth pilot operated check valve 44.1, a sixth pilot operated check valve 44.2, a seventh pilot operated check valve 44.3 and an eighth pilot operated check valve 44.4. There is a recovery first node between the fifth pilot operated check valve 44.1 and the sixth pilot operated check valve 44.2, a recovery second node between the sixth pilot operated check valve 44.2 and the seventh pilot operated check valve 44.3, a recovery third node between the seventh pilot operated check valve 44.3 and the eighth pilot operated check valve 44.4, and a recovery fourth node between the eighth pilot operated check valve 44.4 and the fifth pilot operated check valve 44.1. The fifth pilot operated check valve 44.1, the sixth pilot operated check valve 44.2, the seventh pilot operated check valve 44.3 and the eighth pilot operated check valve 44.4 are also controlled to open and close by a two-position four-way electromagnetic directional valve respectively.
Specifically, the oil outlet of the charge hydraulic motor 64 is connected to the recovery fourth node of the power recovery bridge circuit, the recovery third node of the power recovery bridge circuit is connected to the oil inlet of the power recovery motor 38, the oil outlet of the power recovery motor 38 is connected to the recovery first node of the power recovery bridge circuit, and the recovery second node of the power recovery bridge circuit is connected to the oil inlet of the charge hydraulic motor 64.
Therefore, the power recovery oil path is also divided into four sections, namely, the oil path between the oil outlet of the loading hydraulic motor 64 and the recovery fourth node of the power recovery bridge circuit is a first recovery oil path section 201, the oil path between the recovery third node of the power recovery bridge circuit and the oil inlet of the power recovery motor 38 is a second recovery oil path section 202, the oil path between the oil outlet of the power recovery motor 38 and the recovery first node of the power recovery bridge circuit is a third recovery oil path section 203, and the fourth recovery oil path section 204 of the oil path between the recovery second node of the power recovery bridge circuit and the oil inlet of the loading hydraulic motor 64.
The oil supplementing path comprises an oil supplementing pump 6, an oil supplementing filter 12, a main oil supplementing bridge type loop and a loading oil supplementing bridge type loop.
The main oil compensating bridge circuit is formed by connecting a first check valve 26.1, a second check valve 26.2, a third check valve 26.3 and a fourth check valve 26.4 in series to form a closed loop. A first node for main oil compensation is arranged between the first check valve 26.1 and the second check valve 26.2, a second node for main oil compensation is arranged between the second check valve 26.2 and the third check valve 26.3, a third node for main oil compensation is arranged between the third check valve 26.3 and the fourth check valve 26.4, and a fourth node for main oil compensation is arranged between the fourth check valve 26.4 and the first check valve 26.1.
A first proportional relief valve 27.1 is connected between the main oil-compensating second node and the main oil-compensating fourth node.
The loading oil supplementing bridge circuit is formed by connecting a fifth one-way valve 26.5, a sixth one-way valve 26.6, a seventh one-way valve 26.7 and an eighth one-way valve 26.8 in series to form a closed loop. A first node for filling oil is arranged between the fifth one-way valve 26.5 and the sixth one-way valve 26.6, a second node for filling oil is arranged between the sixth one-way valve 26.6 and the seventh one-way valve 26.7, a third node for filling oil is arranged between the seventh one-way valve 26.7 and the eighth one-way valve 26.8, and a fourth node for filling oil is arranged between the eighth one-way valve 26.8 and the fifth one-way valve 26.5.
A second proportional relief valve 27.2 is connected between the second and fourth load make-up nodes.
The main oil-supplementing bridge type loop and the loading oil-supplementing bridge type loop have the function of automatically selecting the trend of an oil way, an oil pressure safety value is set for the proportional overflow valve, when the hydraulic pressure on one side is too high and exceeds the oil pressure safety value set by the proportional overflow valve, the proportional hydraulic valve is opened, the bridge type loop is conducted, hydraulic oil is directly released to the other side, and pressure relief is achieved to achieve safety protection.
The oil supplementing pump 6 is driven by a motor to work. The oil inlet of the oil supplementing pump 6 is connected to the main oil tank 1 through a ball valve, the oil outlet is connected to the oil supplementing filter 12 through an oil supplementing main one-way valve 11, and the oil supplementing filter 12 is simultaneously connected to an oil supplementing first one-way valve 25.1, an oil supplementing second one-way valve 25.2, an oil supplementing third one-way valve 25.3, an oil supplementing fourth one-way valve 25.4 and an oil supplementing main overflow valve 17. The main relief valve 17 is connected back to the main tank 1. The oil-supplementing main overflow valve 17 can protect an oil path, and when the oil pressure in the oil path is higher than the oil-supplementing main overflow valve 17, the oil-supplementing main overflow valve 17 is opened to release pressure to the oil path.
The first oil compensating check valve 25.1 is then simultaneously connected to the third main oil compensating node and the fourth main oil section 104, the second oil compensating check valve 25.2 is simultaneously connected to the first main oil compensating node and the first main oil path section 101, the third oil compensating check valve 25.3 is simultaneously connected to the third loading oil compensating node and the fourth recovery oil section 204, and the fourth oil compensating check valve 25.4 is simultaneously connected to the first loading oil compensating node and the first recovery oil section 201.
The axial force loading device comprises a hydraulic cylinder 63, a loading bracket 63.1, a loading oil pump 75, a loading filter 73, a loading electromagnetic directional valve 71, a loading overflow valve 72 and a hydraulic lock.
The piston rod of the hydraulic cylinder 63 is connected with a loading bracket 63.1, and the loading bracket 63.1 is connected to the shell of the tested speed reducer 67.2.
The charge oil pump 75 is driven by a motor. The oil inlet of the charge oil pump 75 is connected to the main oil tank 1 via a ball valve, and the oil outlet is connected to the charge filter 73 via a charge check valve 74. The loading filter 73 is connected with the loading overflow valve 72 and the P oil port of the loading electromagnetic directional valve 91 at the same time; the charge relief valve 72 is connected back to the main tank 1. The oil port A of the loading electromagnetic directional valve 71 is connected to the forward oil port of the hydraulic cylinder 63 through a positive side check valve 70.1 of the hydraulic lock, the oil port B of the loading electromagnetic directional valve 71 is connected to the reverse oil port of the hydraulic cylinder 63 through a reverse side check valve 70.2 of the hydraulic lock, and the oil port O of the loading electromagnetic directional valve 71 is connected back to the main oil tank 1.
The working mode of the hydraulic comprehensive test system for power recovery of the invention is as follows:
firstly, the oil supplementing pump 6 is started, and the first oil supplementing one-way valve 25.1, the second oil supplementing one-way valve 25.2, the third oil supplementing one-way valve 25.3 and the fourth oil supplementing one-way valve 25.4 are opened to supply oil to the main oil way and the power recovery oil way through the oil supplementing filter 12.
When the main oil path and the power recovery oil path reach preset pressure values, the main oil pump 33 is started, hydraulic oil from the oil outlet of the main oil pump 33 drives the tested hydraulic motor 69 to rotate through a main oil path bridge circuit, and the hydraulic oil returns to the oil inlet of the main oil pump 33 through the main oil path bridge circuit to form closed circulation.
The tested hydraulic motor 69 drives the tested speed reducer 67.2 and further drives the loading speed reducer 67.1 to rotate, the loading speed reducer drives the loading hydraulic motor 64 to rotate, hydraulic oil drives the power recovery motor 38 through the power recovery bridge type loop, and the purpose that part of the power of the main oil pump drives the power recovery motor 38 is achieved through the rigid connection of the power recovery motor 38 and the main oil pump 33, so that the purpose of power recovery is achieved.
Meanwhile, the set pressure of the second proportional overflow valve 27.2 can be adjusted by adjusting the displacement of the power recovery motor 38 and matching the proportion, so that the effects of realizing power recovery and realizing proportional loading required by a test can be achieved.
If the hydraulic oil is reduced and the pressure is insufficient due to leakage in the main oil way and the power recovery oil way, the oil supplementing way can supplement oil in the main oil way and the power recovery oil way so as to meet the running requirement of the system.
The hydraulic oil cylinder 63 is supplied with oil through the loading oil pump 75, forward extension and reverse retraction of the hydraulic oil cylinder 63 are realized through switching of the loading electromagnetic reversing valve 73, loading force is transmitted to a shell of the tested speed reducer 67.2 through the loading support 63.1, and the performance and the service life of the tested speed reducer 67.2 under axial stress are tested.
A bridge circuit control oil path is also included, and the bridge circuit control oil path comprises a control oil pump 48 and a control filter 47. The control oil pump 48 is driven by a motor, an oil inlet of the control oil pump 48 is connected with the main oil tank 1 through a ball valve, an oil outlet of the control oil pump 48 is connected with a control filter 47, and the control filter 47 is respectively connected with each two-position four-way electromagnetic reversing valve in a main oil circuit bridge type loop and a power recovery bridge type loop through a control one-way valve 46. Through the bridge circuit control oil circuit, the opening and closing of each hydraulic control one-way valve in the main oil circuit bridge circuit and the power recovery bridge circuit can be controlled, so that the flow direction of hydraulic oil is controlled.
In the hydraulic system of the invention, pressure gauges and pressure sensors are respectively distributed at each monitoring point.
According to the invention, the performance and service life of the hydraulic motor and the speed reducer can be tested, the load is simulated by using the loading hydraulic motor, partial power is recycled by using the power recycling oil way to drive the main oil pump, the energy waste is avoided, the system has the advantages of energy conservation and emission reduction, in addition, the system can also load the axial force of the speed reducer, the performance and service life of the speed reducer under the condition of being subjected to the axial force are tested, and the system has the advantage of wide testing application.
However, it will be appreciated by persons skilled in the art that the above embodiments are provided for illustration of the invention and not for limitation thereof, and that changes and modifications to the above described embodiments are intended to fall within the scope of the appended claims as long as they fall within the true spirit of the invention.
Claims (4)
1. The utility model provides a hydraulic pressure integrated test system of power recovery which characterized in that: the device comprises a main oil pump, a tested hydraulic motor, a tested speed reducer, a loading hydraulic motor, a power recovery motor, a main oil circuit, a power recovery oil circuit, an axial force loading device and an oil supplementing pump;
the main oil circuit comprises the main oil pump, a main oil circuit bridge type loop and the tested hydraulic motor; an oil outlet of the main oil pump is connected to an oil inlet of the tested hydraulic motor through the main oil circuit bridge type loop, and the oil outlet of the tested hydraulic motor is connected back to the oil inlet of the main oil pump through the main oil circuit bridge type loop;
the power recovery oil circuit comprises the loading hydraulic motor, a power recovery bridge circuit and the power recovery motor; the oil outlet of the loading hydraulic motor is connected to the oil inlet of the power recovery motor through the power recovery bridge circuit, and the oil outlet of the power recovery motor is connected back to the oil inlet of the loading hydraulic motor through the power recovery bridge circuit;
the tested hydraulic motor, the tested speed reducer, the loading speed reducer and the loading hydraulic motor are sequentially and rigidly connected; the power recovery motor is also rigidly connected with the main oil pump;
the axial force loading device comprises a hydraulic oil cylinder, a loading bracket, a loading oil pump, a loading filter, a loading electromagnetic directional valve, a loading overflow valve and a hydraulic lock;
the piston rod of the hydraulic oil cylinder is connected with the loading bracket, and the loading bracket is connected to the shell of the tested speed reducer;
an oil inlet of the loading oil pump is connected to a main oil tank through a ball valve, an oil outlet of the loading oil pump is connected to the loading filter through a loading one-way valve, and the loading filter is simultaneously connected with the loading overflow valve and a P oil port of the loading electromagnetic reversing valve; the hydraulic oil cylinder is characterized in that the loading overflow valve is connected back to a main oil tank, an oil port A of the loading electromagnetic reversing valve is connected to a forward oil port of the hydraulic oil cylinder through a forward side one-way valve of the hydraulic lock, an oil port B of the loading electromagnetic reversing valve is connected to a reverse oil port of the hydraulic oil cylinder through a reverse side one-way valve of the hydraulic lock, and an oil port O of the loading electromagnetic reversing valve is connected back to the main oil tank;
the oil supplementing pump supplies oil to the main oil way and the power recovery oil way.
2. The power recovery hydraulic integrated test system of claim 1, wherein: the main oil circuit bridge type loop is formed by connecting a first hydraulic control one-way valve, a second hydraulic control one-way valve, a third hydraulic control one-way valve and a fourth hydraulic control one-way valve in series, a main oil circuit first node is arranged between the first hydraulic control one-way valve and the second hydraulic control one-way valve, a main oil circuit second node is arranged between the second hydraulic control one-way valve and the third hydraulic control one-way valve, a main oil circuit third node is arranged between the third hydraulic control one-way valve and the fourth hydraulic control one-way valve, and a main oil circuit fourth node is arranged between the fourth hydraulic control one-way valve and the first hydraulic control one-way valve; the first hydraulic control one-way valve, the second hydraulic control one-way valve, the third hydraulic control one-way valve and the fourth hydraulic control one-way valve are respectively controlled to be opened and closed through a two-position four-way electromagnetic reversing valve.
3. The power recovery hydraulic integrated test system of claim 2, wherein: the power recovery bridge type loop is formed by connecting a fifth hydraulic control one-way valve, a sixth hydraulic control one-way valve, a seventh hydraulic control one-way valve and an eighth hydraulic control one-way valve in series; a recovery first node is arranged between the fifth hydraulic control check valve and the sixth hydraulic control check valve, a recovery second node is arranged between the sixth hydraulic control check valve and the seventh hydraulic control check valve, a recovery third node is arranged between the seventh hydraulic control check valve and the eighth hydraulic control check valve, and a recovery fourth node is arranged between the eighth hydraulic control check valve and the fifth hydraulic control check valve; the fifth hydraulic control one-way valve, the sixth hydraulic control one-way valve, the seventh hydraulic control one-way valve and the eighth hydraulic control one-way valve are respectively controlled to be opened and closed by a two-position four-way electromagnetic reversing valve.
4. The hydraulic motor and speed reducer integrated test stand of claim 3, wherein: the bridge type loop control oil way comprises a control oil pump and a control filter; the oil inlet of the control oil pump is connected with the main oil tank through a ball valve, the oil outlet of the control oil pump is connected with the control filter, and the control filter is respectively connected with each two-position four-way electromagnetic reversing valve in the main oil circuit bridge type loop and the power recovery bridge type loop through a control one-way valve.
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| CN201710624880.3A CN107327430B (en) | 2017-07-27 | 2017-07-27 | Hydraulic comprehensive test system for power recovery |
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