A hydraulic motor

Abstract

A hydraulic motor, the hydraulic motor comprising: a piston motor, a variable control valve, a servo valve, a stop valve and a safety valve; a high-pressure oil port of a hydraulic oil source is connected to the piston motor after passing through the stop valve, a first working port and a second working port of the variable control valve are connected to working ports of the piston motor, a third working port and a fourth working port of the variable control valve are connected to working ports of the servo valve, a fifth working port of the variable control valve is connected to an oil outlet of the stop valve, a sixth working port of the variable control valve is connected to a low-pressure oil port of the hydraulic oil source, the oil outlet of the stop valve is connected to the fifth working port of the variable control valve, and an unloading control oil port of the stop valve is connected to the low-pressure oil port of the hydraulic oil source. This design can not only achieve bidirectional variable control of the hydraulic motor through the proportional positions of the variable control valve and the servo valve, but also precisely perform stepless speed regulation on the piston motor by changing the loading amplitude of the servo valve.

Description

Technical Field

[0001] The present invention relates to a hydraulic actuator, belonging to the technical field of hydraulic components, and particularly to a hydraulic motor. Background Art

[0002] Marine deck cranes on ships are one of the important equipment of ships. They usually need to perform actions such as hoisting, luffing, and slewing. The core actuators of the hoisting and slewing mechanisms are generally completed by hydraulic motors.

[0003] During use, deck cranes often encounter different working conditions. For example, there is a need to adjust low-speed heavy-load, high-speed light-load, and fine hoisting, etc. In order to adapt to different working conditions, it is necessary to control the speed of the hydraulic motor. However, traditional hydraulic motors only have single-speed or double-speed. In order to meet the precise speed control requirements of users, it is usually necessary to configure throttle valves, balance valves, etc. to adjust the speed of the hydraulic motor. This structure has large energy losses and large heat generation.

[0004] For deck cranes with high requirements for speed control, energy conservation, etc. during use, there is an urgent need for a hydraulic motor with high-precision control, bidirectional stepless speed regulation, high dynamic response, and the ability to store and recover energy.

[0005] The invention patent application with the application number 201310499591.7 and the application date of October 22, 2013, discloses a hydraulic motor speed regulation system, a speed regulation method, and a lifting device. The hydraulic motor speed regulation system includes: a first hydraulic pump; a hydraulic motor including a lowering port and a raising port; a first reversing valve connected between the hydraulic motor and the first hydraulic pump, with the oil inlet connected to the output end of the first hydraulic pump, the first working oil port connected to the lowering port of the hydraulic motor, and the second working oil port connected to the raising port of the hydraulic motor; a flow control valve connected to the hydraulic pipeline between the first reversing valve and the hydraulic motor to control the hydraulic flow at the raising port; a pressure control mechanism connected to the control end of the flow control valve to control the opening degree of the flow control valve; and a controller to obtain the hydraulic flow of the first reversing valve. Although this design can adjust the opening degree of the flow control valve through the hydraulic flow control pressure control mechanism, this design still has the following defects:

[0006] It can only control the variable magnitude of the hydraulic motor and cannot control the variable direction of the hydraulic motor, so that the hydraulic motor can achieve bidirectional variable.

[0007] Disclosing the information of this background art section is only intended to increase the understanding of the overall background of the present application, and should not be regarded as an admission or any form of implication that this information constitutes the prior art already known to those of ordinary skill in the art. Summary of the Invention

[0008] The object of the present invention is to overcome the drawback in the prior art that only the variable magnitude of a hydraulic motor can be controlled, and the variable direction of the hydraulic motor cannot be controlled, and to provide a hydraulic motor that can control the variable magnitude and variable direction of the hydraulic motor.

[0009] To achieve the above object, the technical solution of the present invention is as follows:

[0010] A hydraulic motor, the hydraulic motor comprising: a piston motor, a variable control valve, a servo valve, a check valve and a safety valve; the low-pressure oil port of the piston motor is communicated with the low-pressure oil port of a hydraulic oil source, the high-pressure oil port of the piston motor is communicated with the working port of the check valve, the first working port of the variable control valve is communicated with the first working port A of the piston motor, the second working port of the variable control valve is communicated with the second working port B of the piston motor, the third working port of the variable control valve is communicated with the first working port of the servo valve, the fourth working port of the variable control valve is communicated with the second working port of the servo valve, the fifth working port of the variable control valve is communicated with the oil outlet of the check valve, the sixth working port of the variable control valve is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the servo valve is communicated with the high-pressure oil port of the hydraulic oil source, the oil outlet of the servo valve is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the check valve is communicated with the high-pressure oil port of the hydraulic oil source, the oil outlet of the check valve is communicated with the fifth working port of the variable control valve, the unloading control oil port of the check valve is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the safety valve is communicated with the high-pressure oil port of the piston motor, and the oil discharge port of the safety valve is communicated with the low-pressure oil port of the hydraulic oil source.

[0011] The check valve includes an electromagnetic directional valve, a shuttle valve, a two-way cartridge valve and a proximity switch. The electromagnetic directional valve is a two-position three-way electromagnetic directional valve. The oil inlet of the shuttle valve is communicated with the high-pressure oil port of the hydraulic oil source. The oil outlet of the shuttle valve is communicated with the A port of the variable control valve. The oil inlet of the electromagnetic directional valve is communicated with the oil outlet of the shuttle valve. The working port of the electromagnetic directional valve is communicated with the spring chamber of the two-way cartridge valve. The oil drain port of the electromagnetic directional valve is communicated with the low-pressure oil port of the hydraulic oil source. The spring chamber of the two-way cartridge valve is communicated with the low-pressure oil port of the hydraulic oil source. The springless chamber of the two-way cartridge valve is communicated with the high-pressure oil port of the hydraulic oil source. The springless chamber of the two-way cartridge valve is communicated with the oil inlet of the piston motor. The detection end of the proximity switch is in driving cooperation with the valve core of the two-way cartridge valve. The proximity switch is signal-connected to an external electric control system.

[0012] The plunger motor includes a motor oil cylinder, a power output shaft, a swash plate and a variable oil cylinder. The oil inlet of the motor oil cylinder is communicated with the springless chamber of the two-way cartridge valve. The oil outlet of the motor oil cylinder is communicated with the low-pressure oil port of the hydraulic oil source. The power output shaft of the motor oil cylinder is fixedly connected to the rotation center of the swash plate. The swash plate is in transmission cooperation with the piston rod of the variable oil cylinder. The first working port A of the variable oil cylinder is communicated with the first working port of the variable control valve. The second working port B is communicated with the second working port of the variable control valve.

[0013] The variable control valve is a two-position six-way electromagnetic reversing valve. The variable control valve is signal-connected to an external electric control system. The first working port of the variable control valve is communicated with the first working port A of the variable oil cylinder. The second working port of the variable control valve is communicated with the second working port B of the variable oil cylinder. The third working port of the variable control valve is communicated with the first working port of the servo valve. The fourth working port of the variable control valve is communicated with the second working port of the servo valve. The fifth working port of the variable control valve is communicated with the oil outlet of the stop valve. The sixth working port of the variable control valve is communicated with the low-pressure oil port of the hydraulic oil source. The servo valve is a four-position four-way reversing valve with a displacement sensor.

[0014] The safety valve includes a first safety valve group and a second safety valve group. The structures of the first safety valve group and the second safety valve group are the same.

[0015] The first safety valve group includes an electromagnetic reversing valve, a first overflow valve, a second overflow valve and a two-way cartridge valve. The oil inlet of the two-way cartridge valve is communicated with the high-pressure oil port of the plunger motor. The oil outlet of the two-way cartridge valve is communicated with the oil inlet of the second overflow valve. The drain port of the two-way cartridge valve is communicated with the low-pressure oil port of the hydraulic oil source. The oil outlet of the second overflow valve is communicated with the low-pressure oil port of the hydraulic oil source. The oil inlet of the electromagnetic reversing valve is communicated with the oil outlet of the two-way cartridge valve. The oil outlet of the electromagnetic reversing valve is communicated with the low-pressure oil port of the hydraulic oil source. The working port of the electromagnetic reversing valve is communicated with the oil inlet of the first overflow valve. The oil outlet of the first overflow valve is communicated with the low-pressure oil port of the hydraulic oil source.

[0016] The hydraulic motor further includes a make-up check valve. The oil inlet of the make-up check valve is communicated with the low-pressure oil port of the hydraulic oil source. The oil outlet of the make-up check valve is communicated with the high-pressure oil port of the plunger motor.

[0017] The plunger motor further includes a swing angle sensor. The detection end of the swing angle sensor is arranged perpendicular to the telescopic rod of the plunger motor. The touch rod of the swing angle sensor is in transmission cooperation with the piston rod of the variable oil cylinder. The swing angle sensor is signal-connected to an external electric control system.

[0018] The plunger motor further includes a rotational speed sensor. The power output shaft of the plunger motor is in transmission cooperation with the detection end of the rotational speed sensor, and the rotational speed sensor is signal-connected to an external electronic control system.

[0019] The plunger motor further includes two pressure measuring oil ports, which are respectively used to measure the working pressures of the left and right chambers of the variable cylinder.

[0020] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0021] 1. In a hydraulic motor of the present invention, the high-pressure oil output by the hydraulic oil source enters the oil inlet of the plunger motor after passing through the stop valve to drive the plunger motor to work. At the same time, the high-pressure oil output by the hydraulic oil source enters the first working port A and the second working port B of the plunger motor after passing through the variable control valve and the servo valve. The operator can control the variable size and variable direction of the plunger motor by adjusting the proportional positions of the variable control valve and the servo valve, thereby realizing the bidirectional variable control of the hydraulic motor. Therefore, this design can realize the bidirectional variable control of the hydraulic motor through the proportional positions of the variable control valve and the servo valve.

[0022] 2. In a hydraulic motor of the present invention, the first working port of the servo valve is connected to the third working port of the variable control valve, the second working port of the servo valve is connected to the fourth working port of the variable control valve, the oil inlet of the servo valve is connected to the high-pressure oil port of the hydraulic oil source, and the oil outlet of the servo valve is connected to the low-pressure oil port of the hydraulic oil source. The operator can accurately control the speed of the plunger motor variable by controlling the loading amplitude of the servo valve, realizing stepless speed regulation of the plunger motor. Therefore, this design can accurately perform stepless speed regulation on the plunger motor by changing the loading amplitude of the servo valve.

[0023] 3. In a hydraulic motor of the present invention, when the variable control valve electromagnet is in the proportional right position state, the forward displacement of the plunger motor decreases. When the forward displacement of the plunger motor is less than zero, the plunger motor accelerates in the reverse direction. At this time, the plunger motor can convert the gravitational potential energy of the suspended object falling into kinetic energy and output it externally, realizing the gravitational potential energy recovery function. Therefore, this design can make the forward displacement of the plunger motor less than zero through the variable control valve, thereby realizing the gravitational potential energy recovery function and effectively improving the energy-saving effect of the system.

[0024] 4. In a hydraulic motor of the present invention, the oil inlet of the oil replenishing check valve is connected to the low-pressure oil port of the hydraulic oil source, and the oil outlet of the oil replenishing check valve is connected to the high-pressure oil port of the piston motor. When the high-pressure oil circuit of the hydraulic oil source leaks or the hydraulic oil source stops supplying oil due to power failure or other reasons, the pressure in the high-pressure oil circuit of the hydraulic oil source will abnormally decrease, resulting in the abnormal operation of all solenoid valves in the system. At this time, the pressure of the low-pressure oil port of the hydraulic oil source is normal, and the low-pressure oil opens the oil replenishing check valve to replenish oil to the high-pressure oil port of the piston motor, so that the pressures at the inlet and outlet of the piston motor are balanced, avoiding the piston motor from being damaged due to air suction. Therefore, the oil replenishing check valve of this design can balance the pressures at the inlet and outlet of the piston motor when the high-pressure oil circuit of the hydraulic oil source is damaged, avoiding the piston motor from being damaged due to air suction. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 is the hydraulic schematic diagram of the present invention.

[0026] Figure 2 is Figure 1 the hydraulic schematic diagram of the stop valve therein.

[0027] Figure 3 is Figure 1 the hydraulic schematic diagram of the piston motor therein.

[0028] Figure 4 is Figure 1 the hydraulic schematic diagram of the variable control valve therein.

[0029] Figure 5 is Figure 1 the hydraulic schematic diagram of the servo valve therein.

[0030] Figure 6 is Figure 1 the hydraulic schematic diagram of the safety valve therein.

[0031] In the figure: piston motor 1, motor oil cylinder 11, power output shaft 12, swash plate 13, variable oil cylinder 14, swing angle sensor 15, rotational speed sensor 16, variable control valve 2, servo valve 3, stop valve 4, electromagnetic directional valve 41, shuttle valve 42, two-way cartridge valve 43, proximity switch 44, safety valve 5, first safety valve group 51, second safety valve group 52, electromagnetic directional valve 53, first overflow valve 54, second overflow valve 55, two-way cartridge valve 56, oil replenishing check valve 6. DETAILED DESCRIPTION OF THE INVENTION

[0032] The present invention will be further described in detail below with reference to the drawings and the specific embodiments.

[0033] Refer to Figures 1 to 6, a hydraulic motor, the hydraulic motor comprising: a piston motor 1, a variable control valve 2, a servo valve 3, a stop valve 4 and a safety valve 5; the low-pressure oil port of the piston motor 1 is communicated with the low-pressure oil port of a hydraulic oil source, the high-pressure oil port of the piston motor 1 is communicated with the working port of the stop valve 4, the first working port of the variable control valve 2 is communicated with the first working port A of the piston motor 1, the second working port of the variable control valve 2 is communicated with the second working port B of the piston motor 1, the third working port of the variable control valve 2 is communicated with the first working port of the servo valve 3, the fourth working port of the variable control valve 2 is communicated with the second working port of the servo valve 3, the fifth working port of the variable control valve 2 is communicated with the oil outlet of the stop valve 4, the sixth working port of the variable control valve 2 is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the servo valve 3 is communicated with the high-pressure oil port of the hydraulic oil source, the oil outlet of the servo valve 3 is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the stop valve 4 is communicated with the high-pressure oil port of the hydraulic oil source, the oil outlet of the stop valve 4 is communicated with the fifth working port of the variable control valve 2, the unloading control oil port of the stop valve 4 is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the safety valve 5 is communicated with the high-pressure oil port of the piston motor 1, and the oil discharge port of the safety valve 5 is communicated with the low-pressure oil port of the hydraulic oil source.

[0034] The stop valve 4 comprises an electromagnetic directional valve 41, a shuttle valve 42, a two-way cartridge valve 43 and a proximity switch 44. The electromagnetic directional valve 41 is a two-position three-way electromagnetic directional valve. The oil inlet of the shuttle valve 42 is communicated with the high-pressure oil port of the hydraulic oil source. The oil outlet of the shuttle valve 42 is communicated with the A3 port of the variable control valve 2. The oil inlet of the electromagnetic directional valve 41 is communicated with the oil outlet of the shuttle valve 42. The working port of the electromagnetic directional valve 41 is communicated with the spring chamber of the two-way cartridge valve 43. The oil drain port of the electromagnetic directional valve 41 is communicated with the low-pressure oil port of the hydraulic oil source. The spring chamber of the two-way cartridge valve 43 is communicated with the low-pressure oil port of the hydraulic oil source. The springless chamber of the two-way cartridge valve 43 is communicated with the high-pressure oil port of the hydraulic oil source. The springless chamber of the two-way cartridge valve 43 is communicated with the oil inlet of the piston motor 1. The detection end of the proximity switch 44 is in driving cooperation with the valve core of the two-way cartridge valve 43. The proximity switch 44 is signal-connected to an external electric control system.

[0035] The plunger motor 1 includes a motor oil cylinder 11, a power output shaft 12, a swash plate 13 and a variable oil cylinder 14. The oil inlet of the motor oil cylinder 11 is communicated with the springless chamber of the two-way cartridge valve 43. The oil outlet of the motor oil cylinder 11 is communicated with the low-pressure oil port of the hydraulic oil source. The power output shaft 12 of the motor oil cylinder 11 is fixedly connected to the rotation center of the swash plate 13. The swash plate 13 is in transmission cooperation with the piston rod of the variable oil cylinder 14. The first working port A of the variable oil cylinder 14 is communicated with the first working port of the variable control valve 2. The second working port B is communicated with the second working port of the variable control valve 2.

[0036] The variable control valve 2 is a two-position six-way electromagnetic reversing valve. The variable control valve 2 is signal-connected to an external electric control system. The first working port of the variable control valve 2 is communicated with the first working port A of the variable oil cylinder 14. The second working port of the variable control valve 2 is communicated with the second working port B of the variable oil cylinder 14. The third working port of the variable control valve 2 is communicated with the first working port of the servo valve 3. The fourth working port of the variable control valve 2 is communicated with the second working port of the servo valve 3. The fifth working port of the variable control valve 2 is communicated with the oil outlet of the stop valve 4. The sixth working port of the variable control valve 2 is communicated with the low-pressure oil port of the hydraulic oil source. The servo valve 3 is a four-position four-way reversing valve with a displacement sensor.

[0037] The safety valve 5 includes a first safety valve group 51 and a second safety valve group 52. The structures of the first safety valve group 51 and the second safety valve group 52 are the same.

[0038] The first safety valve group 51 includes an electromagnetic reversing valve 53, a first overflow valve 54, a second overflow valve 55 and a two-way cartridge valve 56. The oil inlet of the two-way cartridge valve 56 is communicated with the high-pressure oil port of the plunger motor 1. The oil outlet of the two-way cartridge valve 56 is communicated with the oil inlet of the second overflow valve 55. The oil drain port of the two-way cartridge valve 56 is communicated with the low-pressure oil port of the hydraulic oil source. The oil outlet of the second overflow valve 55 is communicated with the low-pressure oil port of the hydraulic oil source. The oil inlet of the electromagnetic reversing valve 53 is communicated with the oil outlet of the two-way cartridge valve 56. The oil outlet of the electromagnetic reversing valve 53 is communicated with the low-pressure oil port of the hydraulic oil source. The working port of the electromagnetic reversing valve 53 is communicated with the oil inlet of the first overflow valve 54. The oil outlet of the first overflow valve 54 is communicated with the low-pressure oil port of the hydraulic oil source.

[0039] The hydraulic motor further includes a make-up check valve 6. The oil inlet of the make-up check valve 6 is communicated with the low-pressure oil port of the hydraulic oil source. The oil outlet of the make-up check valve 6 is communicated with the high-pressure oil port of the plunger motor 1.

[0040] The plunger motor 1 further includes a swing angle sensor 15. The detection end of the swing angle sensor 15 is arranged perpendicular to the telescopic rod of the plunger motor 1. The touch rod of the swing angle sensor 15 is in transmission cooperation with the piston rod of the variable oil cylinder 14. The swing angle sensor 15 is signal-connected to an external electronic control system.

[0041] The plunger motor 1 further includes a rotational speed sensor 16. The power output shaft 12 of the plunger motor 1 is in transmission cooperation with the detection end of the rotational speed sensor 16. The rotational speed sensor 16 is signal-connected to an external electronic control system.

[0042] The plunger motor 1 further includes two pressure measurement oil ports, which are respectively used to measure the working pressures of the left and right chambers of the variable oil cylinder 14.

[0043] The principle of the present invention is described as follows:

[0044] During the use process of this design, there are standby conditions, winch ascending conditions, and winch descending conditions. Among them, the standby condition is as follows:

[0045] The high-pressure oil output by the hydraulic oil source enters the oil inlet of the electromagnetic directional valve 41 and the spring chamber of the two-way cartridge valve 43. When the electromagnetic directional valve 41, the variable control valve 2, and the servo valve 3 are not powered on, the spool of the electromagnetic directional valve 41 is in the right position, and the variable control valve 2 is opened. At this time, the oil inlet and the working port of the electromagnetic directional valve 41 are connected, and the high-pressure oil enters the spring chamber of the two-way cartridge valve 43 through the working port of the electromagnetic directional valve 41 to push the spool of the two-way cartridge valve 43, so that the two-way cartridge valve 43 is closed. At the same time, the high-pressure oil output by the hydraulic oil source enters the variable oil cylinder 14 through the variable control valve 2, driving the variable oil cylinder 14 to vary, forcing the plunger motor 1 to be in the maximum displacement state. Since the negative load of the winch is lower than the maximum displacement state of the plunger motor 1, the plunger motor 1 remains stationary.

[0046] The winch ascending condition is as follows:

[0047] The high-pressure oil output by the hydraulic oil source enters the oil inlet of the electromagnetic directional valve 41 and the spring chamber of the two-way cartridge valve 43. When the electromagnetic directional valve 41 is energized, the spool of the electromagnetic directional valve 41 is in the left position. After the electromagnetic directional valve 41 is energized, the solenoid valve of the servo valve 3 is energized and is in the proportional left position working state. After the servo valve 3 is energized, the variable control valve 2 is energized, and the solenoid of the variable control valve 2 is in the left position state. At this time, the drain port of the electromagnetic directional valve 41 is connected to the working port, and the hydraulic oil in the spring chamber of the two-way cartridge valve 43 enters the low-pressure oil port output by the hydraulic oil source through the drain port of the electromagnetic directional valve 41, causing the two-way cartridge valve 43 to open. At this time, the high-pressure oil output by the hydraulic oil source enters the piston motor 1 through the oil outlet of the two-way cartridge valve 43. At the same time, the high-pressure oil output by the hydraulic oil source enters the left chamber of the variable cylinder 14 through the variable control valve 2 and the servo valve 3, causing the piston motor 1 to be in the positive displacement state. By controlling the amplitude of the left position of the servo valve 3, the magnitude of the positive displacement of the piston motor 1 is realized, and the control of the hoisting speed of the winch is realized.

[0048] The winch lowering working condition is as follows:

[0049] The high-pressure oil output by the hydraulic oil source enters the oil inlet of the electromagnetic directional valve 41 and the spring chamber of the two-way cartridge valve 43. When the electromagnetic directional valve 41 is energized, the spool of the electromagnetic directional valve 41 is in the left position. After the electromagnetic directional valve 41 is energized, the variable control valve 2 is energized, and the solenoid of the variable control valve 2 is in the proportional right position state. After the variable control valve 2 is energized, the solenoid valve of the servo valve 3 is energized and is in the right position working state. At this time, the drain port of the electromagnetic directional valve 41 is connected to the working port, and the hydraulic oil in the spring chamber of the two-way cartridge valve 43 enters the low-pressure oil port output by the hydraulic oil source through the drain port of the electromagnetic directional valve 41, causing the two-way cartridge valve 43 to open. At this time, the high-pressure oil output by the hydraulic oil source enters the piston motor 1 through the oil outlet of the two-way cartridge valve 43. At the same time, the high-pressure oil output by the hydraulic oil source enters the right chamber of the variable cylinder 14 through the variable control valve 2 and the servo valve 3, causing the piston motor 1 to gradually change from the positive displacement state to the negative displacement conversion state. By controlling the amplitude of the right position of the servo valve 3, the positive displacement of the piston motor 1 is reduced. When the positive displacement of the piston motor 1 is less than zero, the piston motor 1 accelerates in the reverse direction and the winch descends. Embodiment

[0050] A hydraulic motor, the hydraulic motor comprising: a piston motor 1, a variable control valve 2, a servo valve 3, a shut-off valve 4 and a safety valve 5; a low-pressure oil port of the piston motor 1 is communicated with a low-pressure oil port of a hydraulic oil source, a high-pressure oil port of the piston motor 1 is communicated with a working port of the shut-off valve 4, a first working port of the variable control valve 2 is communicated with a first working port A of the piston motor 1, a second working port of the variable control valve 2 is communicated with a second working port B of the piston motor 1, a third working port of the variable control valve 2 is communicated with a first working port of the servo valve 3, a fourth working port of the variable control valve 2 is communicated with a second working port of the servo valve 3, a fifth working port of the variable control valve 2 is communicated with an oil outlet of the shut-off valve 4, a sixth working port of the variable control valve 2 is communicated with the low-pressure oil port of the hydraulic oil source, an oil inlet of the servo valve 3 is communicated with a high-pressure oil port of the hydraulic oil source, an oil outlet of the servo valve 3 is communicated with the low-pressure oil port of the hydraulic oil source, an oil inlet of the shut-off valve 4 is communicated with the high-pressure oil port of the hydraulic oil source, an oil outlet of the shut-off valve 4 is communicated with the fifth working port of the variable control valve 2, a load control oil port of the shut-off valve 4 is communicated with the low-pressure oil port of the hydraulic oil source, an oil inlet of the safety valve 5 is communicated with the high-pressure oil port of the piston motor 1, and an oil discharge port of the safety valve 5 is communicated with the low-pressure oil port of the hydraulic oil source; the shut-off valve 4 comprises an electromagnetic directional valve 41, a shuttle valve 42, a two-way cartridge valve 43 and a proximity switch 44, the electromagnetic directional valve 41 is a two-position three-way electromagnetic directional valve, an oil inlet of the shuttle valve 42 is communicated with the high-pressure oil port of the hydraulic oil source, an oil outlet of the shuttle valve 42 is communicated with an A3 port of the variable control valve 2, an oil inlet of the electromagnetic directional valve 41 is communicated with the oil outlet of the shuttle valve 42, a working port of the electromagnetic directional valve 41 is communicated with a spring chamber of the two-way cartridge valve 43, a drain port of the electromagnetic directional valve 41 is communicated with the low-pressure oil port of the hydraulic oil source, the spring chamber of the two-way cartridge valve 43 is communicated with the low-pressure oil port of the hydraulic oil source, a springless chamber of the two-way cartridge valve 43 is communicated with the high-pressure oil port of the hydraulic oil source, the springless chamber of the two-way cartridge valve 43 is communicated with an oil inlet of the piston motor 1, a detection end of the proximity switch 44 is in transmission cooperation with a valve core of the two-way cartridge valve 43, and the proximity switch 44 is signal-connected to an external electric control system.

[0051] During the use of this design:

[0052] The high-pressure oil output by the hydraulic oil source enters the oil inlet of the piston motor 1 after passing through the shut-off valve 4, driving the piston motor 1 to work. At the same time, the high-pressure oil output by the hydraulic oil source enters the first working port A and the second working port B of the piston motor 1 after passing through the variable control valve 2 and the servo valve 3. The variable size and variable direction of the piston motor 1 are controlled by the proportional positions of the variable control valve 2 and the servo valve 3.

[0053] It enters the oil inlet of the electromagnetic directional valve 41 and the spring chamber of the two-way cartridge valve 43. When the electromagnetic directional valve 41 is energized, the spool of the electromagnetic directional valve 41 is in the left position. After the electromagnetic directional valve 41 is energized, the servo valve 3 electromagnet is energized and is in the proportional left position working state. After the servo valve 3 is energized, the variable control valve 2 is energized, and the control valve 2 electromagnet is in the left position state. At this time, the drain port of the electromagnetic directional valve 41 is communicated with the working port, and the hydraulic oil in the spring chamber of the two-way cartridge valve 43 enters the low-pressure oil port output by the hydraulic oil source through the drain port of the electromagnetic directional valve 41, so that the two-way cartridge valve 43 is opened. At this time, the high-pressure oil output by the hydraulic oil source enters the plunger motor 1 through the oil outlet of the two-way cartridge valve 43. At the same time, the high-pressure oil output by the hydraulic oil source enters the left chamber of the variable cylinder 14 through the variable control valve 2 and the servo valve 3, so that the plunger motor 1 is in the positive displacement state. By controlling the left position amplitude of the servo valve 3, the magnitude of the positive displacement of the plunger motor 1 is realized, and the control of the winch rising speed is realized. Embodiment

[0054] Embodiment 2 is basically the same as Embodiment 1, and the difference lies in:

[0055] The plunger motor 1 includes a motor cylinder 11, a power output shaft 12, a swash plate 13 and a variable cylinder 14. The oil inlet of the motor cylinder 11 is communicated with the non-spring chamber of the two-way cartridge valve 43. The oil outlet of the motor cylinder 11 is communicated with the low-pressure oil port of the hydraulic oil source. The power output shaft 12 of the motor cylinder 11 is fixedly connected to the rotation center of the swash plate 13. The swash plate 13 is in transmission cooperation with the piston rod of the variable cylinder 14. The first working port A of the variable cylinder 14 is communicated with the first working port of the variable control valve 2, and the second working port B is communicated with the second working port of the variable control valve 2. Embodiment

[0056] Embodiment 3 is basically the same as Embodiment 2, and the difference lies in:

[0057] The variable control valve 2 is a two-position six-way electromagnetic directional control valve. The variable control valve 2 is signal-connected to an external electronic control system. The first working port of the variable control valve 2 is communicated with the first working port A of the variable oil cylinder 14. The second working port of the variable control valve 2 is communicated with the second working port B of the variable oil cylinder 14. The third working port of the variable control valve 2 is communicated with the first working port of the servo valve 3. The fourth working port of the variable control valve 2 is communicated with the second working port of the servo valve 3. The fifth working port of the variable control valve 2 is communicated with the oil outlet of the stop valve 4. The sixth working port of the variable control valve 2 is communicated with the low-pressure oil port of the hydraulic oil source. The servo valve 3 is a four-position four-way directional control valve with a displacement sensor. The safety valve 5 includes a first safety valve group 51 and a second safety valve group 52, and the structures of the first safety valve group 51 and the second safety valve group 52 are the same. The first safety valve group 51 includes an electromagnetic directional control valve 53, a first overflow valve 54, a second overflow valve 55 and a two-way cartridge valve 56. The oil inlet of the two-way cartridge valve 56 is communicated with the high-pressure oil port of the plunger motor 1. The oil outlet of the two-way cartridge valve 56 is communicated with the oil inlet of the second overflow valve 55. The oil drain port of the two-way cartridge valve 56 is communicated with the low-pressure oil port of the hydraulic oil source. The oil outlet of the second overflow valve 55 is communicated with the low-pressure oil port of the hydraulic oil source. The oil inlet of the electromagnetic directional control valve 53 is communicated with the oil outlet of the two-way cartridge valve 56. The oil outlet of the electromagnetic directional control valve 53 is communicated with the low-pressure oil port of the hydraulic oil source. The working port of the electromagnetic directional control valve 53 is communicated with the oil inlet of the first overflow valve 54. The oil outlet of the first overflow valve 54 is communicated with the low-pressure oil port of the hydraulic oil source. The hydraulic motor further includes a make-up check valve 6. The oil inlet of the make-up check valve 6 is communicated with the low-pressure oil port of the hydraulic oil source. The oil outlet of the make-up check valve 6 is communicated with the high-pressure oil port of the plunger motor 1. The plunger motor 1 further includes a swing angle sensor 15. The detection end of the swing angle sensor 15 is arranged perpendicular to the telescopic rod of the plunger motor 1. The contact rod of the swing angle sensor 15 is in transmission cooperation with the piston rod of the variable oil cylinder 14. The swing angle sensor 15 is signal-connected to an external electronic control system. The plunger motor 1 further includes a rotational speed sensor 16. The power output shaft 12 of the plunger motor 1 is in transmission cooperation with the detection end of the rotational speed sensor 16. The rotational speed sensor 16 is signal-connected to an external electronic control system. The plunger motor 1 further includes two pressure measuring oil ports, and the two pressure measuring oil ports are respectively used for measuring the working pressures of the left and right chambers of the variable oil cylinder 14.

[0058] The above is only the preferred embodiment of the present design. The protection scope of the present design is not limited to the above embodiment. Any equivalent modification or change made by those of ordinary skill in the art according to the disclosure of the present invention shall be included in the protection scope recorded in the claims.

Claims

1. A hydraulic motor, characterized in that: The hydraulic motor includes: a piston motor (1), a variable control valve (2), a servo valve (3), a shut-off valve (4) and a safety valve (5); the low-pressure oil port of the piston motor (1) is communicated with the low-pressure oil port of the hydraulic oil source, the high-pressure oil port of the piston motor (1) is communicated with the working port of the shut-off valve (4), the first working port of the variable control valve (2) is communicated with the first working port A of the piston motor (1), the second working port of the variable control valve (2) is communicated with the second working port B of the piston motor (1), the third working port of the variable control valve (2) is communicated with the first working port of the servo valve (3), the fourth working port of the variable control valve (2) is communicated with the second working port of the servo valve (3), the fifth working port of the variable control valve (2) is communicated with the oil outlet of the shut-off valve (4), the sixth working port of the variable control valve (2) is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the servo valve (3) is communicated with the high-pressure oil port of the hydraulic oil source, the oil outlet of the servo valve (3) is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the shut-off valve (4) is communicated with the high-pressure oil port of the hydraulic oil source, the oil outlet of the shut-off valve (4) is communicated with the fifth working port of the variable control valve (2), the unloading control oil port of the shut-off valve (4) is communicated with the low-pressure oil port of the hydraulic oil source, the oil inlet of the safety valve (5) is communicated with the high-pressure oil port of the piston motor (1), and the oil discharge port of the safety valve (5) is communicated with the low-pressure oil port of the hydraulic oil source; The shut-off valve (4) includes an electromagnetic directional valve (41), a shuttle valve (42), a two-way cartridge valve (43) and a proximity switch (44), the electromagnetic directional valve (41) is a two-position three-way electromagnetic directional valve, the oil inlet of the shuttle valve (42) is communicated with the high-pressure oil port of the hydraulic oil source, the oil outlet of the shuttle valve (42) is communicated with the A3 port of the variable control valve (2), the oil inlet of the electromagnetic directional valve (41) is communicated with the oil outlet of the shuttle valve (42), the working port of the electromagnetic directional valve (41) is communicated with the spring chamber of the two-way cartridge valve (43), the oil drain port of the electromagnetic directional valve (41) is communicated with the low-pressure oil port of the hydraulic oil source, the spring chamber of the two-way cartridge valve (43) is communicated with the low-pressure oil port of the hydraulic oil source, the non-spring chamber of the two-way cartridge valve (43) is communicated with the high-pressure oil port of the hydraulic oil source, the non-spring chamber of the two-way cartridge valve (43) is communicated with the oil inlet of the piston motor (1), the detection end of the proximity switch (44) is in driving cooperation with the valve core of the two-way cartridge valve (43), and the proximity switch (44) is signal-connected to an external electric control system.

2. The hydraulic motor according to claim 1, characterized in that: The plunger motor (1) includes a motor cylinder (11), a power output shaft (12), a swash plate (13), and a variable cylinder (14). The oil inlet of the motor cylinder (11) is communicated with the springless cavity of the two-way cartridge valve (43). The oil outlet of the motor cylinder (11) is communicated with the low-pressure oil port of the hydraulic oil source. The power output shaft (12) of the motor cylinder (11) is fixedly connected to the rotation center of the swash plate (13). The swash plate (13) is in transmission cooperation with the piston rod of the variable cylinder (14). The first working port A of the variable cylinder (14) is communicated with the first working port of the variable control valve (2), and the second working port B is communicated with the second working port of the variable control valve (2).

3. The hydraulic motor according to claim 1 or 2, characterized in that: The variable control valve (2) is a two-position six-way electromagnetic reversing valve. The variable control valve (2) is signal-connected to an external electric control system. The first working port of the variable control valve (2) is communicated with the first working port A of the variable cylinder (14). The second working port of the variable control valve (2) is communicated with the second working port B of the variable cylinder (14). The third working port of the variable control valve (2) is communicated with the first working port of the servo valve (3). The fourth working port of the variable control valve (2) is communicated with the second working port of the servo valve (3). The fifth working port of the variable control valve (2) is communicated with the oil outlet of the stop valve (4). The sixth working port of the variable control valve (2) is communicated with the low-pressure oil port of the hydraulic oil source. The servo valve (3) is a four-position four-way reversing valve with a displacement sensor.

4. The hydraulic motor according to claim 3, characterized in that: The safety valve (5) includes a first safety valve group (51) and a second safety valve group (52), and the structures of the first safety valve group (51) and the second safety valve group (52) are the same.

5. The hydraulic motor according to claim 4, characterized in that: The first safety valve group (51) includes an electromagnetic reversing valve, a first overflow valve (54), a second overflow valve (55), and a two-way cartridge valve. The oil inlet of the two-way cartridge valve is communicated with the high-pressure oil port of the plunger motor (1). The oil outlet of the two-way cartridge valve is communicated with the oil inlet of the second overflow valve (55). The drain port of the two-way cartridge valve is communicated with the low-pressure oil port of the hydraulic oil source. The oil outlet of the second overflow valve (55) is communicated with the low-pressure oil port of the hydraulic oil source. The oil inlet of the electromagnetic reversing valve is communicated with the oil outlet of the two-way cartridge valve. The oil outlet of the electromagnetic reversing valve is communicated with the low-pressure oil port of the hydraulic oil source. The working port of the electromagnetic reversing valve is communicated with the oil inlet of the first overflow valve (54). The oil outlet of the first overflow valve (54) is communicated with the low-pressure oil port of the hydraulic oil source.

6. The hydraulic motor according to claim 5, characterized in that: The hydraulic motor further includes a make-up check valve (6). The inlet of the make-up check valve (6) is communicated with the low-pressure oil port of the hydraulic oil source, and the outlet of the make-up check valve (6) is communicated with the high-pressure oil port of the piston motor (1).

7. A hydraulic motor according to claim 6, wherein: The piston motor (1) further includes a swing angle sensor (15). The detection end of the swing angle sensor (15) is arranged perpendicular to the telescopic rod of the piston motor (1). The contact rod of the swing angle sensor (15) is in transmission cooperation with the piston rod of the variable oil cylinder (14), and the swing angle sensor (15) is signal-connected to an external electric control system.

8. A hydraulic motor according to claim 7, wherein: The piston motor (1) further includes a rotational speed sensor (16). The power output shaft (12) of the piston motor (1) is in transmission cooperation with the detection end of the rotational speed sensor (16), and the rotational speed sensor (16) is signal-connected to an external electric control system.

9. A hydraulic motor according to claim 8, wherein: The piston motor (1) further includes two pressure measurement oil ports, and the two pressure measurement oil ports are respectively used for measuring the working pressures of the left and right chambers of the variable oil cylinder (14).

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