Deep sea gearbox transmission efficiency test system and test method using same

Abstract

The invention discloses a deep sea gearbox transmission efficiency test system and a test method using the same, and the system comprises a hydraulic oil tank, a pressure cylinder, a first hydraulic motor and a second hydraulic motor which are located in the pressure cylinder, and a first hydraulic pipeline which enables the first hydraulic motor and the hydraulic oil tank to be connected in series to form a loop. The second hydraulic motor and the hydraulic oil tank are connected in series through the second hydraulic pipeline to form a loop, and a proportional overflow valve is connected in series on the second hydraulic pipeline between an outlet of the second hydraulic motor and the hydraulic oil tank; under a target working condition and a target deep sea pressure condition, a first hydraulic motor and a second hydraulic motor are respectively connected in series with two gearboxes to be tested, and output shafts of the first hydraulic motor and the second hydraulic motor are directly connected. The transmission efficiency of the gearbox to be tested is calculated according to the pressure difference between the inlet and the outlet of the first hydraulic motor and the pressure difference between the inlet and the outlet of the second hydraulic motor, and the cost of the test system is reduced while the working condition requirement and the test requirement are met.

Description

Technical Field

[0001] This invention relates to the field of gearbox performance testing technology, and in particular to a deep-sea gearbox transmission efficiency testing system and a testing method using the same. Background Technology

[0002] The deep-sea environment is characterized by high pressure, placing extremely high demands on the reliability and performance of deep-sea equipment. As a core transmission component of deep-sea robots, underwater vehicles, and other equipment, the transmission efficiency of the deep-sea gearbox directly affects the energy utilization rate and service life of the entire system.

[0003] Traditional gearbox testing equipment is usually conducted under normal pressure. The gearboxes to be tested are connected back to back. One motor is used as the drive motor and connected to one gearbox, while another motor is used as the load motor and connected to the other gearbox to provide load torque for the test. Torque sensors and speed sensors are set at the connection between the motor and the gearbox. During the test, the difference in torque values ​​measured by the two sensors is used to calculate the transmission efficiency of the gearbox under test.

[0004] If the above testing method is applied to the deep-sea pressure environment to test the transmission efficiency of the gearbox, the motor, torque sensor, and speed sensor need to be in an environment with a pressure as high as 30 MPa, which greatly increases the requirements for the motor and sensors and increases the cost of the testing system. Summary of the Invention

[0005] In response to the shortcomings of the existing production technology, the applicant provides a deep-sea gearbox transmission efficiency testing system and a testing method thereof, which meets the operating conditions and testing requirements of gearboxes used in deep-sea equipment while reducing the cost of the testing system.

[0006] The technical solution adopted in this invention is as follows: A deep-sea gearbox transmission efficiency testing system includes a hydraulic tank and a pressure cylinder, as well as a first hydraulic motor and a second hydraulic motor located within the pressure cylinder. The pressure cylinder provides a target deep-sea pressure, and the pressure within the hydraulic tank is equal to the target deep-sea pressure. The system also includes: A first hydraulic pipeline is formed by connecting the first hydraulic motor and the hydraulic oil tank in series to form a circuit. A first hydraulic pump is connected in series on the first hydraulic pipeline, and a first detection device is provided for detecting the pressure difference between the inlet and outlet of the first hydraulic motor. In addition, a second hydraulic pipeline is provided to connect the second hydraulic motor and the hydraulic oil tank in series to form a circuit. A proportional relief valve is connected in series on the second hydraulic pipeline between the outlet of the second hydraulic motor and the hydraulic oil tank. A second detection device for detecting the pressure difference between the inlet and outlet of the second hydraulic motor is provided on the second hydraulic pipeline. Specifically, under the target operating conditions and the target deep-sea pressure conditions: When the first and second hydraulic motors are connected in series with the two gearboxes under test, the output shafts of the first and second hydraulic motors rotate at the same speed, and the pressure difference between the inlet and outlet of the first hydraulic motor is [value missing]. The pressure difference between the inlet and outlet of the second hydraulic motor is ; When the output shafts of the first and second hydraulic motors are directly connected, the pressure difference between the inlet and outlet of the first hydraulic motor is: The pressure difference between the inlet and outlet of the second hydraulic motor is ; Then, the transmission efficiency of the gearbox under test (a).

[0007] The target operating conditions include the rotational speed of the first hydraulic motor. To test the system load ,in: (b) In equation (b), This refers to the displacement of the first hydraulic pump. The rotational speed of the first hydraulic pump. The volumetric efficiency of the first hydraulic pump. This refers to the displacement of the first hydraulic motor. The rotational speed of the first hydraulic motor. The volumetric efficiency of the first hydraulic motor; (c) In equation (c), The inlet and outlet pressure difference of the second hydraulic motor. This refers to the displacement of the second hydraulic motor. The total efficiency of the second hydraulic motor.

[0008] The testing system also includes: A first shut-off valve located outside the pressure cylinder, the inlet and outlet of the first shut-off valve being connected to the first hydraulic pipeline, and the first shut-off valve being connected in parallel with the first hydraulic motor; In addition, a second shut-off valve and a replenishment pipeline, wherein a second hydraulic pipeline between the second shut-off valve and the second hydraulic motor is connected to one end of the replenishment pipeline, and the other end of the replenishment pipeline is connected to the hydraulic oil tank, and a second hydraulic pump is connected in series on the replenishment pipeline.

[0009] The hydraulic oil tank is located inside the pressure cylinder, and a first compensator is installed inside the pressure cylinder. The first compensator is connected to the hydraulic oil tank to transmit the pressure inside the pressure cylinder to the hydraulic oil tank. It also includes a second compensator located inside the pressure cylinder, which is connected to the gearbox under test and transmits the pressure inside the pressure cylinder to the gearbox under test.

[0010] The first compensator and the second compensator have the same structure. The first compensator includes a housing, and a fixed structure is provided inside the housing. A movable part is sealed and installed on the fixed structure. The combination of the fixed structure and the movable part divides the inner cavity of the housing into a first chamber and a second chamber. The housing is provided with a first interface and a second interface. The first interface communicates with the first chamber, and the second interface communicates with the second chamber. The position of the movable part relative to the fixed structure changes, thereby making the pressure in the first chamber and the second chamber equal. The first interface of the first compensator is connected to the hydraulic oil tank, and the second interface of the first compensator is connected to the pressure cylinder; The first interface of the second compensator is connected to the gearbox under test, and the second interface of the second compensator is connected to the pressure cylinder.

[0011] It also includes a first overflow pipeline, one end of which is connected to the first hydraulic pipeline between the inlet of the first hydraulic motor and the outlet of the first hydraulic pump, and the other end of which is connected to the hydraulic oil tank. A first safety valve is provided on the first overflow pipeline.

[0012] It also includes a second overflow line, both ends of which are connected to the second hydraulic line, and the second overflow line is connected in parallel with the proportional overflow valve. A second safety valve is provided on the second overflow line.

[0013] The first hydraulic pipeline is equipped with a first inlet pressure sensor for detecting the inlet pressure of the first hydraulic motor and a first outlet pressure sensor for detecting the outlet pressure of the first hydraulic motor. The second hydraulic pipeline is equipped with a second inlet pressure sensor for detecting the inlet pressure of the second hydraulic motor and a second outlet pressure sensor for detecting the outlet pressure of the second hydraulic motor.

[0014] A testing method using any of the above-described deep-sea gearbox transmission efficiency testing systems includes the following steps: Test system calibration: The output shafts of the first and second hydraulic motors are directly connected. The first and second hydraulic motors are then enclosed within a pressure cylinder, and the pressure inside the cylinder is increased to the target deep-sea pressure, making the pressure in the hydraulic tank equal to the target deep-sea pressure. Then start the first hydraulic pump and adjust its speed so that the first hydraulic motor's speed is... Adjust the opening pressure of the proportional relief valve to make the load of the test system... , After the test system stabilizes, record the pressure difference between the inlet and outlet of the first hydraulic motor. The pressure difference between the inlet and outlet of the second hydraulic motor ; Gearbox under test: The first and second hydraulic motors are connected in series with two gearboxes under test. The output shafts of the first and second hydraulic motors rotate at the same speed. The first and second hydraulic motors and the gearboxes under test are enclosed in a pressure cylinder, and the pressure inside the pressure cylinder is increased to the target deep-sea pressure. The pressure inside the hydraulic tank is equal to the target deep-sea pressure. Then start the first hydraulic pump and adjust its speed so that the first hydraulic motor's speed is... Adjust the opening pressure of the proportional relief valve to make the load of the test system... , After the test system stabilizes, record the pressure difference between the inlet and outlet of the first hydraulic motor. The pressure difference between the inlet and outlet of the second hydraulic motor ; Calculation of the transmission efficiency of the gearbox under test: Under the target operating conditions and the target deep-sea pressure conditions The transmission efficiency of the gearbox under test is (a).

[0015] Before performing the test system calibration procedure or the test procedure for the gearbox under test, if there is no hydraulic oil in the second hydraulic line, perform the following steps: Open the first shut-off valve, close the second shut-off valve, start the second hydraulic pump, drive the second hydraulic motor to move, and at the same time, the hydraulic oil enters the second hydraulic pipeline and flows back into the hydraulic oil tank after passing through the proportional relief valve. Then, the first shut-off valve is closed, the second shut-off valve is opened, and the second hydraulic pump is shut down.

[0016] The beneficial effects of this invention are as follows: This invention features a compact and reasonable structure, and is easy to operate. By using hydraulic motors as the drive mechanism and load component when testing gearboxes, two hydraulic motors are placed inside a high-pressure cylinder, while the pipelines connected to the hydraulic motors, as well as the sensors, valves, pumps, and other devices related to the two hydraulic motors, are placed outside the pressure cylinder. This reduces the cost of system components. The transmission efficiency of the gearbox is calculated by the pressure difference between the inlet and outlet of the two hydraulic motors. This invention meets the operating conditions and testing requirements of gearboxes used in deep-sea equipment while reducing the cost of the testing system.

[0017] Furthermore, the present invention also has the following advantages: (1) By monitoring the speed of the first hydraulic pump in the drive circuit, the speed of the first hydraulic motor located in the pressure cylinder is controlled to achieve speed control in the target working condition. By monitoring the flow rate and pressure of the second hydraulic motor in the load circuit and calculating the power of the second hydraulic motor, the load in the load circuit can be quantitatively adjusted, which facilitates the quantitative adjustment of the load of the test system in the target working condition, and thus enables the testing of gearbox transmission efficiency under different load conditions.

[0018] (2) By setting up a replenishment pipeline connecting the second hydraulic pipeline and the hydraulic oil tank, and setting up a second hydraulic pump on the replenishment pipeline, a hydraulic circuit is formed to drive the second hydraulic motor to move, so that the load circuit is quickly filled with hydraulic oil, shortening the time from the start-up to the stabilization process of the test system.

[0019] (2) The test method for gearbox transmission efficiency is divided into two stages: the first stage is to calibrate the efficiency of the hydraulic motor in the test system, and the second stage is to test the transmission efficiency of the gearbox under test. The first stage test eliminates the interference of the hydraulic motor's own efficiency on the gearbox test and obtains the efficiency of the hydraulic motor under different working conditions. The second stage test, based on the known hydraulic motor efficiency, tests the total efficiency of the test system containing the deep-sea gearbox, and then separates the transmission efficiency of the gearbox, cleverly eliminating the interference of the hydraulic motor efficiency and improving the reliability of the test data. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the structure of the present invention (during the testing of the gearbox under test).

[0021] Figure 2 This is a schematic diagram of the structure of the present invention (test system calibration).

[0022] Figure 3 This is a schematic diagram of the hydraulic oil flow in the pipeline of the present invention (during the testing of the gearbox under test).

[0023] Figure 4 This is a schematic diagram of hydraulic oil flow in the pipeline of the present invention (when the load circuit pressure is too high).

[0024] Figure 5 This is a schematic diagram of hydraulic oil flow in the pipeline of the present invention (when replenishing oil in the load circuit).

[0025] Figure 6 This is a schematic diagram of the structure of a first compensator according to an embodiment of the present invention.

[0026] Figure 7 This is a schematic diagram of the structure of the first compensator according to another embodiment of the present invention.

[0027] in: 1. First hydraulic motor; 11. First hydraulic line; 111. First inlet pressure sensor; 112. First outlet pressure sensor; 113. First flow sensor; 12. First shut-off valve; 13. First overflow line; 131. First safety valve; 14. First hydraulic pump; 2. Gearbox under test; 21. Second compensator; 3. Coupling; 4. Second hydraulic motor; 41. Second hydraulic line; 411. Second inlet pressure sensor; 412. Second outlet pressure sensor; 413. Second flow sensor; 42. Proportional relief valve; 43. Second relief line; 431. Second safety valve; 44. Second shut-off valve; 45. Second hydraulic pump; 46. Replenishment line; 5. Hydraulic oil tank; 51. First compensator; 511. First interface; 512. Outer shell; 513. First chamber; 514. Second chamber; 515. Second interface; 516. Fixed structure; 517. Moving parts; 6. Pressure cylinder. Detailed Implementation

[0028] The specific embodiments of the present invention will now be described with reference to the accompanying drawings.

[0029] Example 1: like Figures 1-2 As shown, the deep-sea gearbox transmission efficiency testing system of this embodiment includes a hydraulic oil tank 5 and a pressure cylinder 6, as well as a first hydraulic motor 1 and a second hydraulic motor 4 located inside the pressure cylinder 6. The pressure cylinder 6 is used to provide the target deep-sea pressure, and the pressure inside the hydraulic oil tank 5 is equal to the target deep-sea pressure. It also includes a first hydraulic pipeline 11 that connects the first hydraulic motor 1 and the hydraulic oil tank 5 in series to form a circuit. A first hydraulic pump 14 is connected in series on the first hydraulic pipeline 11 outside the pressure cylinder 6, and a first detection device is provided for detecting the pressure difference between the inlet and outlet of the first hydraulic motor 1.

[0030] Specifically, the inlet of the first hydraulic pump 14 is connected to the hydraulic oil tank 5, the outlet of the first hydraulic pump 14 is connected to the inlet of the first hydraulic motor 1, the outlet of the first hydraulic motor 1 is connected to the hydraulic oil tank 5, and the circuit formed by the first hydraulic pipeline 11 connected in series is the drive circuit, which provides the power source for the entire test system through the first hydraulic pump 14.

[0031] The testing system also includes a second hydraulic pipeline 41 that connects the second hydraulic motor 4 and the hydraulic oil tank 5 in series to form a loop. A proportional relief valve 42 is connected in series on the second hydraulic pipeline 41 between the outlet of the second hydraulic motor 4 and the hydraulic oil tank 5. A second detection device for detecting the pressure difference between the inlet and outlet of the second hydraulic motor 4 is provided on the second hydraulic pipeline 41 outside the pressure cylinder 6.

[0032] Specifically, the inlet and outlet of the second hydraulic motor 4 are both connected to the hydraulic oil tank 5 through the second hydraulic pipeline 41. The circuit formed by the second hydraulic pipeline 41 in series is a load circuit, simulating the load part in the transmission system. Under the action of the proportional relief valve 42 located on the outlet side of the second hydraulic motor 4, the pressure in the load circuit is adjusted, thereby changing the magnitude of the load provided by the load circuit.

[0033] Specifically, under the target operating conditions and the target deep-sea pressure conditions: When the first hydraulic motor 1 and the second hydraulic motor 4 are connected in series with the two gearboxes 2 under test, the output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 rotate at the same speed, and the pressure difference between the inlet and outlet of the first hydraulic motor 1 is... The pressure difference between the inlet and outlet of the second hydraulic motor 4 is ; When the output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 are directly connected, the pressure difference between the inlet and outlet of the first hydraulic motor 1 is: The pressure difference between the inlet and outlet of the second hydraulic motor 4 is ; Then, the transmission efficiency of the gearbox 2 under test is... (a).

[0034] Specifically, the hydraulic oil tank 5 can be located outside the pressure cylinder 6. The hydraulic oil tank 5 is pressurized by a pressurizing device. The gearbox 2 under test can be connected to a gear oil pressurization system to ensure that the internal pressure of the gearbox 2 under test is equal to the deep-sea pressure simulated in the pressure cylinder 6. All sensors involved in the testing system are located outside the pressure cylinder 6, such as the first detection device and the second detection device. All valves that need to be operated are located outside the pressure cylinder 6, reducing the requirements for electronic components and facilitating operation and data transmission. The first hydraulic pump 14 used to drive the first hydraulic motor 1 is located outside the pressure cylinder 6 and is in an atmospheric pressure environment.

[0035] Pressure cylinder 6 is used to simulate a specific pressure environment and provide the required pressure conditions for testing deep-sea gearboxes. Pressure cylinder 6 is made of high-strength alloy steel and can withstand the ultra-high pressure environment of deep sea. The internal space dimensions of pressure cylinder 6 are designed according to the specifications of the internal components to be installed, ensuring that the gearbox 2 under test can be installed and disassembled smoothly. The pipes passing through the side wall of pressure cylinder 6 are sealed to the side wall of pressure cylinder 6 through the chamber fitting. This part is existing technology and will not be described in detail here.

[0036] Hydraulic motors are commonly used drive mechanisms in deep-sea equipment. These mechanisms are widely used in equipment operating in deep-sea environments. Compared to existing technologies that directly drive gearboxes with motors, this significantly reduces the cost of testing systems.

[0037] The target operating conditions include the rotational speed of the gearbox 2 under test and the magnitude of the load provided by the load circuit. The transmission efficiency of the gearbox 2 under test can be tested according to the specific test operating conditions and the rotational speed and load magnitude.

[0038] The calculation formula (a) for transmission efficiency is derived, assuming that the test system of this embodiment is running under a specific target working condition, specifically including two parts of analysis.

[0039] Part 1: Testing the overall transmission efficiency of the testing system: When the output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 are directly connected, such as Figure 2 As shown, the output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 are connected by a coupling 3; (1) In the formula, The overall efficiency of the test system is determined when the output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 are directly connected. The power of the second hydraulic motor 4, The power of the first hydraulic motor 1.

[0040] (2) in, The transmission efficiency of the transmission components of the test system is tested when the gearbox under test 2 is not installed.

[0041] (3) (4) (5) In the above formula, The pressure difference between the inlet and outlet of the second hydraulic motor 4. The flow rate of the second hydraulic motor 4, The displacement of the second hydraulic motor 4. The rotational speed of the second hydraulic motor 4, The total efficiency of the second hydraulic motor 4. For the volumetric efficiency of the second hydraulic motor 4, The mechanical efficiency of the second hydraulic motor 4.

[0042] (6) (7) (8) In the above formula, The pressure difference between the inlet and outlet of the first hydraulic motor 1 The flow rate of the first hydraulic motor 1, The displacement of the first hydraulic motor 1, The rotational speed of the first hydraulic motor 1 The total efficiency of the first hydraulic motor 1, The volumetric efficiency of the first hydraulic motor 1 The mechanical efficiency of the first hydraulic motor 1.

[0043] Substituting equations (2)-(8) into equation (1), we get: (9) Part Two: Testing the overall transmission efficiency of the system after installing the two gearboxes to be tested. When the first hydraulic motor 1 and the second hydraulic motor 4 are connected in series with the two gearboxes 2 under test, the output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 rotate at the same speed. Figure 1 As shown; (10) In the formula, The power of the first hydraulic motor 1, The power of the second hydraulic motor 4.

[0044] (11) (12) (13) In the above formula, The pressure difference between the inlet and outlet of the second hydraulic motor 4. The flow rate of the second hydraulic motor 4, The displacement of the second hydraulic motor 4. The rotational speed of the second hydraulic motor 4, The total efficiency of the second hydraulic motor 4. For the volumetric efficiency of the second hydraulic motor 4, The mechanical efficiency of the second hydraulic motor 4.

[0045] (14) (15) (16) In the above formula, The pressure difference between the inlet and outlet of the first hydraulic motor 1 The flow rate of the first hydraulic motor 1, The displacement of the first hydraulic motor 1, The rotational speed of the first hydraulic motor 1 The total efficiency of the first hydraulic motor 1, The volumetric efficiency of the first hydraulic motor 1 The mechanical efficiency of the first hydraulic motor 1.

[0046] Substituting equations (11)-(16) into equation (10), we get: (17) again, (18) in, To determine the overall transmission efficiency after installing two gearboxes 2 to be tested. To obtain the transmission efficiency of the transmission components of the test system when the gearbox under test 2 is not installed in the first part, The efficiency of the gearbox 2 under test is given.

[0047] In the two parts mentioned above, the first hydraulic motor 1 and the second hydraulic motor 4 have the same rotational speed. Since the operating conditions of the test system are the same in the two parts, the rotational speed, displacement and efficiency parameters of the first hydraulic motor 1 and the second hydraulic motor 4 are the same. That is, according to equations (18), (17) and (9), we can obtain: (a) This embodiment uses hydraulic motors as the drive mechanism and load component when testing the gearbox. Two hydraulic motors are placed inside a high-pressure cylinder 6, while the pipelines connected to the hydraulic motors, as well as the sensors, valves, pumps, and other devices related to the two hydraulic motors, are placed outside the pressure cylinder 6. This reduces the cost of system components. The gearbox transmission efficiency is calculated by the pressure difference between the inlet and outlet of the two hydraulic motors. This approach meets the operating conditions and testing requirements of gearboxes used in deep-sea equipment while reducing the cost of the testing system.

[0048] This embodiment uses pressure cylinder 6 to simulate a specific pressure environment, allowing the deep-sea gearbox to be tested under conditions close to actual working conditions. This accurately reflects the impact of the pressure environment on the transmission efficiency of the deep-sea gearbox, improving the reliability and effectiveness of the test results.

[0049] Example 2: like Figures 1-2 As shown, based on Embodiment 1, the deep-sea gearbox transmission efficiency testing system of this embodiment also includes a first flow sensor 113 installed on the first hydraulic pipeline 11. The first flow sensor 113 is used to detect the flow rate of hydraulic oil flowing through the first hydraulic motor 1. In addition, a second flow sensor 413 is provided on the second hydraulic line 41. The second flow sensor 413 is used to detect the flow rate of hydraulic oil flowing through the second hydraulic motor 4. Specifically, the second flow sensor 413 is provided on the second hydraulic line 41 between the outlet of the second hydraulic motor 4 and the proportional relief valve 42.

[0050] The target operating condition includes the rotational speed of the first hydraulic motor 1. To test the system load ,in: (b) In equation (b), The displacement of the first hydraulic pump 14, The rotational speed of the first hydraulic pump 14 The volumetric efficiency of the first hydraulic pump 14 The displacement of the first hydraulic motor 1, The rotational speed of the first hydraulic motor 1 The volumetric efficiency of the first hydraulic motor 1; (c) In equation (c), The inlet and outlet pressure difference of the second hydraulic motor 4 The displacement of the second hydraulic motor (4) The total efficiency of the second hydraulic motor 4.

[0051] The derivation of equation (b) is as follows: The flow rate of the first hydraulic pump 14 is: (19) In the above formula, The flow rate of the first hydraulic pump 14, in units of: ; The displacement of the first hydraulic pump 14, in units of: ; The rotational speed of the first hydraulic pump 14, in units of: ; The volumetric efficiency of the first hydraulic pump 14.

[0052] The flow rate of the first hydraulic motor 1 is: (20) In the above formula, The flow rate of the first hydraulic motor 1, in units of: ; The displacement of the first hydraulic motor 1, in units of: ; The rotational speed of the first hydraulic motor 1, in units of: ; The volumetric efficiency of the first hydraulic motor 1.

[0053] The flow rate of the first hydraulic pump 14 is the same as that of the first hydraulic motor 1, that is: ,but: (twenty one) According to equation (21), we can calculate: (b) In the above formula, the volumetric efficiency of the first hydraulic motor 1 is... and the volumetric efficiency of the first hydraulic pump 14 Typical parameters from the factory specifications, such as the volumetric efficiency of the first hydraulic pump 14. The volumetric efficiency of the first hydraulic motor 1 is 90%. It is 95%.

[0054] The derivation of equation (c) is as follows: The power of the second hydraulic motor 4, which is driven to rotate in the load circuit, is: (11) In the above formula, , The pressure difference between the inlet and outlet of the second hydraulic motor 4. The flow rate of the second hydraulic motor 4, The total efficiency of the second hydraulic motor 4.

[0055] The overall efficiency of the second hydraulic motor 4 is a typical parameter in the factory specifications.

[0056] The power of the second hydraulic motor 4 can be equivalent to the load size of the load circuit.

[0057] That is, the load of the test system is obtained. , (c) The load in the load circuit is adjusted by controlling the proportional relief valve 42 to regulate the pressure difference between the inlet and outlet of the second hydraulic motor 4. The size, and thus the operating parameters of the test.

[0058] Specifically, the first hydraulic motor 1 and the second hydraulic motor 4 have the same specifications. The first flow sensor 113 and the second flow sensor 413 are used for flow detection in the first hydraulic line 11 and the second hydraulic line 41, respectively. This allows the system to determine whether the drive circuit and the load circuit are at the same load level and to monitor the operation of the test system.

[0059] The rotational speed of the first hydraulic motor 1 in the target working condition The adjustment variable is the speed of the first hydraulic pump 14. This can be achieved by monitoring the speed of the motor of the first hydraulic pump 14. The adjustment does not require speed detection of the output shaft of the first hydraulic motor 1.

[0060] Load of the test system under target operating conditions The regulating variable is the pressure difference between the inlet and outlet of the second hydraulic motor 4. This can be achieved by adjusting the opening pressure of the proportional relief valve 42. The adjustment of the speed of the first hydraulic motor 1 Under constant conditions, the pressure in the load circuit is regulated by adjusting the opening pressure of the proportional relief valve 42. The hydraulic oil overflowing from the proportional relief valve 42 flows back to the hydraulic oil tank 5 through the pipeline; the load in the load circuit This refers to the power of the second hydraulic motor 4 when it is used as a pump. After the change, the first hydraulic pump 14 in the drive circuit adaptively changes its output power. Specifically, the first hydraulic pump 14 is a fixed displacement pump.

[0061] For the rotational speed of the first hydraulic motor 1 in the target working condition When the load is a certain value, There can be many different situations, such as load. It can be the rotation speed The corresponding values ​​of 25%, 50%, 75%, and 100% of the rated power of the second hydraulic motor 4 were used to divide the target working conditions in detail, and multiple gearbox transmission efficiency tests were conducted.

[0062] The rotational speed of the first hydraulic motor 1 located in the pressure cylinder 6 is monitored by the rotational speed of the first hydraulic pump 14 in the drive circuit, thereby controlling the rotational speed under the target working condition. By monitoring the flow rate and pressure of the second hydraulic motor 4 in the load circuit and calculating the power of the second hydraulic motor 4, the magnitude of the load in the load circuit can be quantitatively adjusted, which facilitates the quantitative adjustment of the load of the test system under the target working condition, and thus enables the testing of the gearbox transmission efficiency under different load conditions.

[0063] The aforementioned adjustments to speed and power under target operating conditions are intended to constrain the transmission system used by the gearbox to a certain operating level, and to allow for multiple tests of gearbox transmission efficiency at different operating levels, thereby obtaining multiple sets of analyzable and comparable test data, making the transmission efficiency test more scientific and effective.

[0064] Furthermore, the testing system also includes: a first shut-off valve 12 located outside the pressure cylinder 6, the inlet and outlet of the first shut-off valve 12 being connected to the first hydraulic pipeline 11, and the first shut-off valve 12 being connected in parallel with the first hydraulic motor 1; and a second shut-off valve 44 and a replenishment pipeline 46, the second hydraulic pipeline 41 between the second shut-off valve 44 and the second hydraulic motor 4 being connected to one end of the replenishment pipeline 46, the other end of the replenishment pipeline 46 being connected to the hydraulic oil tank 5, and a second hydraulic pump 45 being connected in series on the replenishment pipeline 46.

[0065] When the test system is started for the first time, since there is no hydraulic oil in the second hydraulic line 41, a replenishment line 46 connecting the second hydraulic line 41 and the hydraulic oil tank 5 is set up, and a second hydraulic pump 45 is set on the replenishment line 46 to form a hydraulic circuit that drives the second hydraulic motor 4 to move, so that the load circuit is quickly filled with hydraulic oil, shortening the time from the start-up to the stabilization process of the test system.

[0066] like Figure 5 As shown, the working process of the test system in this embodiment when replenishing hydraulic oil to the load circuit is as follows: With the first shut-off valve 12 open and the second shut-off valve 44 closed, the second hydraulic pump 45 is started, driving the second hydraulic motor 4. Simultaneously, hydraulic oil enters the second hydraulic pipeline 41, passes through the proportional relief valve 42, and flows back into the hydraulic oil tank 5, thus completing the replenishment of hydraulic oil to the load circuit. Before conducting the efficiency test, the first shut-off valve 12 is closed, the second shut-off valve 44 is open, and the second hydraulic pump 45 is in the off state.

[0067] Furthermore, the hydraulic oil tank 5 is located inside the pressure cylinder 6, and the pressure cylinder 6 is equipped with a first compensator 51. The first compensator 51 is connected to the hydraulic oil tank 5 to transmit the pressure inside the pressure cylinder 6 to the hydraulic oil tank 5. It also includes a second compensator 21 located inside the pressure cylinder 6. The second compensator 21 is connected to the gearbox 2 under test and transmits the pressure inside the pressure cylinder 6 to the gearbox 2 under test.

[0068] The hydraulic oil tank 5 is placed in the pressure cylinder 6, and the pressure in the pressure cylinder 6 is transmitted to the hydraulic oil tank 5 through the first compensator 51. This reduces the difficulty of maintaining the gear oil pressure in the hydraulic oil tank 5 and meets the relevant sealing requirements of the hydraulic oil tank 5.

[0069] For example, such as Figures 6-7 As shown, the first compensator 51 and the second compensator 21 have the same structure. The first compensator 51 includes a housing 512, and a fixed structure 516 is provided inside the housing 512. A movable part 517 is sealed and installed on the fixed structure 516. The combination structure of the fixed structure 516 and the movable part 517 divides the inner cavity of the housing 512 into a first chamber 513 and a second chamber 514. The housing 512 is provided with a first interface 511 and a second interface 515. The first interface 511 communicates with the first chamber 513, and the second interface 515 communicates with the second chamber 514. The position of the movable part 517 relative to the fixed structure 516 changes, thereby making the pressure in the first chamber 513 and the second chamber 514 equal. The first interface 511 of the first compensator 51 is connected to the hydraulic oil tank 5, and the second interface 515 of the first compensator 51 is connected to the pressure cylinder 6. The first interface 511 of the second compensator 21 is connected to the gearbox 2 under test, and the second interface 515 of the second compensator 21 is connected to the pressure cylinder 6.

[0070] Specifically, such as Figure 6 The fixed structure 516 shown can be a tubular structure, and the movable part 517 is a piston that is slidably and limitably installed in the through hole of the fixed structure 516, so that the position of the movable part 517 relative to the fixed structure 516 can change; for example Figure 7 As shown, in another embodiment, the fixed structure 516 can be a fixed ring fixed inside the outer shell 512, and the movable part 517 is a rubber hemispherical shell structure installed in the inner hole of the fixed ring, which can undergo elastic deformation, so that the position of the movable part 517 relative to the fixed structure 516 can change.

[0071] Furthermore, it also includes a first overflow pipe 13, a first hydraulic pipe 11 between the inlet of the first hydraulic motor 1 and the outlet of the first hydraulic pump 14 is connected to one end of the first overflow pipe 13, the other end of the first overflow pipe 13 is connected to the hydraulic oil tank 5, and a first safety valve 131 is provided on the first overflow pipe 13.

[0072] Specifically, the first safety valve 131 is an overflow valve, used to ensure the safety of the test system and prevent the pressure in the first hydraulic line 11 from exceeding the design value. The overflowed hydraulic oil is introduced into the hydraulic oil tank 5 through the pipeline.

[0073] Furthermore, it also includes a second overflow pipe 43, both ends of which are connected to the second hydraulic pipe 41, and the second overflow pipe 43 is connected in parallel with the proportional overflow valve 42. A second safety valve 431 is provided on the second overflow pipe 43.

[0074] Specifically, the second safety valve 431 is a relief valve used to ensure the safety of the test system and prevent the pressure in the second relief pipeline 43 from exceeding the design value. The overflowed hydraulic oil is introduced into the hydraulic oil tank 5 through the pipeline. Figure 4 As shown.

[0075] For example, such as Figures 1-2 As shown, the first hydraulic line 11 is provided with a first inlet pressure sensor 111 for detecting the inlet pressure of the first hydraulic motor 1, and a first outlet pressure sensor 112 for detecting the outlet pressure of the first hydraulic motor 1. The second hydraulic line 41 is equipped with a second inlet pressure sensor 411 for detecting the inlet pressure of the second hydraulic motor 4 and a second outlet pressure sensor 412 for detecting the outlet pressure of the second hydraulic motor 4.

[0076] For the first hydraulic motor 1, driven by the first hydraulic pump 14, the pressure value of the first inlet pressure sensor 111 is greater than the pressure value of the first outlet pressure sensor 112. For the second hydraulic motor 4, as the load in the test system, under the driving action of the first hydraulic motor 1, the second hydraulic motor 4 functions similarly to a pump. The pressure value of the second outlet pressure sensor 412 is greater than the pressure value of the second inlet pressure sensor 411. The calculated pressure difference between the inlet and outlet of the first hydraulic motor 1... And the pressure difference between the inlet and outlet of the second hydraulic motor 4 All are positive values.

[0077] Specifically, the first inlet pressure sensor 111, the first outlet pressure sensor 112, the second inlet pressure sensor 411, and the second outlet pressure sensor 412 are all located outside the pressure cylinder 6.

[0078] Example 3: This embodiment utilizes the testing method of the deep-sea gearbox transmission efficiency testing system of Embodiment 2 above, including the following steps: Test system calibration: The output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 are directly connected. The first hydraulic motor 1 and the second hydraulic motor 4 are enclosed in the pressure cylinder 6, and the pressure inside the pressure cylinder 6 is increased to the target deep-sea pressure. The pressure inside the hydraulic oil tank 5 is equal to the target deep-sea pressure. Then start the first hydraulic pump 14 and adjust its speed so that the speed of the first hydraulic motor 1 is [missing value]. Adjust the opening pressure of the proportional relief valve 42 to make the load of the test system... , After the test system stabilizes, record the pressure difference between the inlet and outlet of the first hydraulic motor 1. The pressure difference between the inlet and outlet of the second hydraulic motor 4 ; Specifically, after directly connecting the output shafts of the first hydraulic motor 1 and the second hydraulic motor 4, and after the testing system is installed, multiple sets of different values ​​of target deep-sea pressure and rotational speed of the first hydraulic motor 1 can be measured. and the load of the test system under conditions and The numerical values ​​were measured and recorded.

[0079] Test of gearbox 2: like Figure 3As shown, the first hydraulic motor 1 and the second hydraulic motor 4 are connected in series with two gearboxes 2 to be tested. The output shafts of the first hydraulic motor 1 and the second hydraulic motor 4 rotate at the same speed. The first hydraulic motor 1, the second hydraulic motor 4, and the gearboxes 2 to be tested are enclosed in a pressure cylinder 6, and the pressure inside the pressure cylinder 6 is increased to the target deep-sea pressure. The pressure inside the hydraulic oil tank 5 is equal to the target deep-sea pressure. Then start the first hydraulic pump 14 and adjust its speed so that the speed of the first hydraulic motor 1 is [missing value]. Adjust the opening pressure of the proportional relief valve (42) to make the load of the test system... , After the test system stabilizes, record the pressure difference between the inlet and outlet of the first hydraulic motor 1. The pressure difference between the inlet and outlet of the second hydraulic motor 4 ; Specifically, after connecting the first hydraulic motor 1 and the second hydraulic motor 4 in series with the two gearboxes 2 to be tested, and after the test system is installed, perform multiple sets of different values ​​of the target deep-sea pressure and the rotational speed of the first hydraulic motor 1, as in the "Test System Calibration". and the load of the test system under conditions and The numerical values ​​were measured and recorded.

[0080] Calculation of transmission efficiency of gearbox 2 under test: Under the target operating conditions and the target deep-sea pressure conditions The transmission efficiency of the gearbox 2 under test is (a); Specifically, the target deep-sea pressure and the rotational speed of the first hydraulic motor 1 are calculated based on the pressure difference values ​​measured under different conditions in the "Test System Calibration" and "Gearbox 2 Under Test" steps. and the load of the test system Transmission efficiency of gearbox 2 under test conditions To evaluate the transmission performance of deep-sea gearboxes under different deep-sea environmental conditions.

[0081] The gearbox transmission efficiency test method is generally divided into two stages: the first stage is to calibrate the efficiency of the hydraulic motor in the test system, and the second stage is to test the transmission efficiency of the gearbox under test. The first stage test eliminates the interference of the hydraulic motor's own efficiency on the gearbox test and obtains the efficiency of the hydraulic motor under different working conditions. The second stage test, based on the known hydraulic motor efficiency, tests the total efficiency of the test system including the deep-sea gearbox, and then separates the transmission efficiency of the gearbox, cleverly eliminating the interference of the hydraulic motor efficiency and improving the reliability of the test data.

[0082] In addition, such as Figure 5 As shown, before the calibration of the test system or the test of the gearbox 2, when there is no hydraulic oil in the second hydraulic line 41, the following steps are performed: the first shut-off valve 12 is opened, the second shut-off valve 44 is closed, the second hydraulic pump 45 is started, and the second hydraulic motor 4 is driven to move. At the same time, the hydraulic oil enters the second hydraulic line 41 and flows back into the hydraulic oil tank 5 after passing through the proportional relief valve 42; then, the first shut-off valve 12 is closed, the second shut-off valve 44 is opened, and the second hydraulic pump 45 is turned off.

[0083] Then, the test system calibration and the test gearbox 2 test steps are carried out. The power unit quickly fills the load circuit with hydraulic oil, shortening the time from start-up to stabilization of the test system.

[0084] The above description is an explanation of the present invention and not a limitation thereof. The scope of the present invention is defined by the claims. Within the scope of protection of the present invention, any form of modification may be made.

Claims

1. A deep-sea gearbox transmission efficiency testing system, characterized in that: Includes a hydraulic tank (5) and a pressure cylinder (6), and a first hydraulic motor (1) and a second hydraulic motor (4) located within the pressure cylinder (6). The pressure cylinder (6) is used to provide the target deep-sea pressure. The pressure in the hydraulic tank (5) is equal to the target deep-sea pressure. It also includes: A first hydraulic pipeline (11) is connected in series with the first hydraulic motor (1) and the hydraulic oil tank (5) to form a circuit. A first hydraulic pump (14) is connected in series on the first hydraulic pipeline (11), and a first detection device is provided for detecting the pressure difference between the inlet and outlet of the first hydraulic motor (1). In addition, a second hydraulic pipeline (41) is connected in series with the second hydraulic motor (4) and the hydraulic oil tank (5) to form a circuit. A proportional relief valve (42) is connected in series on the second hydraulic pipeline (41) between the outlet of the second hydraulic motor (4) and the hydraulic oil tank (5). A second detection device for detecting the pressure difference between the inlet and outlet of the second hydraulic motor (4) is provided on the second hydraulic pipeline (41). Specifically, under the target operating conditions and the target deep-sea pressure conditions: When the first hydraulic motor (1) and the second hydraulic motor (4) are connected in series with the two gearboxes (2) to be tested, the output shafts of the first hydraulic motor (1) and the second hydraulic motor (4) rotate at the same speed, and the pressure difference between the inlet and outlet of the first hydraulic motor (1) is... The pressure difference between the inlet and outlet of the second hydraulic motor (4) is ; When the output shafts of the first hydraulic motor (1) and the second hydraulic motor (4) are directly connected, the pressure difference between the inlet and outlet of the first hydraulic motor (1) is: The pressure difference between the inlet and outlet of the second hydraulic motor (4) is ; Then, the transmission efficiency of the gearbox (2) under test. (a).

2. The deep-sea gearbox transmission efficiency testing system as described in claim 1, characterized in that: The target operating condition includes the rotational speed of the first hydraulic motor (1). To test the system load ,in: （b） In equation (b), The displacement of the first hydraulic pump (14) The rotational speed of the first hydraulic pump (14), The volumetric efficiency of the first hydraulic pump (14) The displacement of the first hydraulic motor (1) The rotational speed of the first hydraulic motor (1) is... The volumetric efficiency of the first hydraulic motor (1); （c） In equation (c), The inlet and outlet pressure difference of the second hydraulic motor (4) The displacement of the second hydraulic motor (4) The total efficiency of the second hydraulic motor (4).

3. The deep-sea gearbox transmission efficiency testing system as described in claim 2, characterized in that: The testing system also includes: The first shut-off valve (12) is located outside the pressure cylinder (6). The inlet and outlet of the first shut-off valve (12) are connected to the first hydraulic pipeline (11), and the first shut-off valve (12) is connected in parallel with the first hydraulic motor (1). In addition, a second shut-off valve (44) and a replenishment line (46) are provided. A second hydraulic line (41) between the second shut-off valve (44) and the second hydraulic motor (4) is connected to one end of the replenishment line (46), and the other end of the replenishment line (46) is connected to the hydraulic oil tank (5). A second hydraulic pump (45) is connected in series on the replenishment line (46).

4. The deep-sea gearbox transmission efficiency testing system as described in claim 1, characterized in that: The hydraulic oil tank (5) is located inside the pressure cylinder (6). A first compensator (51) is provided inside the pressure cylinder (6). The first compensator (51) is connected to the hydraulic oil tank (5) to transmit the pressure inside the pressure cylinder (6) to the hydraulic oil tank (5). It also includes a second compensator (21) located inside the pressure cylinder (6), the second compensator (21) being connected to the gearbox (2) under test, and transmitting the pressure inside the pressure cylinder (6) to the gearbox (2) under test.

5. The deep-sea gearbox transmission efficiency testing system as described in claim 4, characterized in that: The first compensator (51) has the same structure as the second compensator (21). The first compensator (51) includes a housing (512). A fixed structure (516) is provided inside the housing (512). A movable part (517) is sealed and installed on the fixed structure (516). The combination structure of the fixed structure (516) and the movable part (517) divides the inner cavity of the housing (512) into a first chamber (513) and a second chamber (514). The housing (512) is provided with a first interface (511) and a second interface (515). The first interface (511) is connected to the first chamber (513), and the second interface (515) is connected to the second chamber (514). The position of the movable part (517) relative to the fixed structure (516) changes, thereby making the pressure of the first chamber (513) and the second chamber (514) equal. The first interface (511) of the first compensator (51) is connected to the hydraulic oil tank (5), and the second interface (515) of the first compensator (51) is connected to the pressure cylinder (6). The first interface (511) of the second compensator (21) is connected to the gearbox (2) under test, and the second interface (515) of the second compensator (21) is connected to the pressure cylinder (6).

6. The deep-sea gearbox transmission efficiency testing system as described in claim 1, characterized in that: It also includes a first overflow pipe (13), one end of the first hydraulic pipe (11) between the inlet of the first hydraulic motor (1) and the outlet of the first hydraulic pump (14) is connected to the first overflow pipe (13), the other end of the first overflow pipe (13) is connected to the hydraulic oil tank (5), and a first safety valve (131) is provided on the first overflow pipe (13).

7. The deep-sea gearbox transmission efficiency testing system as described in claim 1, characterized in that: It also includes a second overflow pipe (43), both ends of which are connected to the second hydraulic pipe (41), and the second overflow pipe (43) is connected in parallel with the proportional overflow valve (42), and a second safety valve (431) is provided on the second overflow pipe (43).

8. The deep-sea gearbox transmission efficiency testing system as described in claim 1, characterized in that: The first hydraulic line (11) is provided with a first inlet pressure sensor (111) for detecting the inlet pressure of the first hydraulic motor (1) and a first outlet pressure sensor (112) for detecting the outlet pressure of the first hydraulic motor (1). The second hydraulic line (41) is equipped with a second inlet pressure sensor (411) for detecting the inlet pressure of the second hydraulic motor (4) and a second outlet pressure sensor (412) for detecting the outlet pressure of the second hydraulic motor (4).

9. A testing method using the deep-sea gearbox transmission efficiency testing system as described in claim 3, characterized in that: Includes the following steps: Test system calibration: The output shafts of the first hydraulic motor (1) and the second hydraulic motor (4) are directly connected. The first hydraulic motor (1) and the second hydraulic motor (4) are enclosed in a pressure cylinder (6). The pressure inside the pressure cylinder (6) is increased to the target deep-sea pressure, and the pressure inside the hydraulic oil tank (5) is equal to the target deep-sea pressure. Then start the first hydraulic pump (14) and adjust the speed of the first hydraulic pump (14) so ​​that the speed of the first hydraulic motor (1) is [missing value]. Adjust the opening pressure of the proportional relief valve (42) to make the load of the test system... , After the test system stabilizes, record the pressure difference between the inlet and outlet of the first hydraulic motor (1). The pressure difference between the inlet and outlet of the second hydraulic motor (4) ; Test of gearbox (2) under test: The first hydraulic motor (1) and the second hydraulic motor (4) are connected in series with two gearboxes (2) to be tested. The output shafts of the first hydraulic motor (1) and the second hydraulic motor (4) rotate at the same speed. The first hydraulic motor (1), the second hydraulic motor (4) and the gearboxes (2) to be tested are enclosed in a pressure cylinder (6). The pressure inside the pressure cylinder (6) is increased to the target deep-sea pressure, and the pressure inside the hydraulic oil tank (5) is equal to the target deep-sea pressure. Then start the first hydraulic pump (14) and adjust the speed of the first hydraulic pump (14) so ​​that the speed of the first hydraulic motor (1) is [missing value]. Adjust the opening pressure of the proportional relief valve (42) to make the load of the test system... , After the test system stabilizes, record the pressure difference between the inlet and outlet of the first hydraulic motor (1). The pressure difference between the inlet and outlet of the second hydraulic motor (4) ; Calculation of transmission efficiency of gearbox (2) under test: Under the target operating conditions and the target deep-sea pressure conditions The transmission efficiency of the gearbox (2) under test is (a).

10. The test method as described in claim 9, characterized in that: Before performing the test system calibration step or the test step of the gearbox under test (2), if there is no hydraulic oil in the second hydraulic line (41), perform the following steps: Open the first shut-off valve (12), close the second shut-off valve (44), start the second hydraulic pump (45), drive the second hydraulic motor (4) to move, and at the same time, the hydraulic oil enters the second hydraulic pipeline (41), passes through the proportional relief valve (42), and flows back into the hydraulic oil tank (5). Then, the first shut-off valve (12) is closed, the second shut-off valve (44) is opened, and the second hydraulic pump (45) is shut off.

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