Hydraulic power unit

Abstract

The utility model relates to the technical field of hydraulic devices, in particular to a hydraulic power unit which comprises an oil tank internally provided with a two-way gear pump, a valve block arranged at one end of the oil tank and a two-way motor arranged at the end, away from the oil tank, of the valve block. The two ends of the connecting shaft are fixedly connected with the two-way gear pump and the two-way motor correspondingly, first oil ways are symmetrically formed in the valve body, two second oil ways communicating with the two first oil ways correspondingly are symmetrically arranged in the valve body, the valve body is provided with a third oil way at the same ends of the two second oil ways, and a piston is slidably arranged in the third oil way. Throttling valves are installed at the positions, at two ports of the third oil way, of the valve body, the two ends of the piston are arranged in the two throttling valves in a penetrating and matched mode respectively, and the two throttling valves are connected with power output structures. The hydraulic power unit has the effects that the flow and the flow speed of oil in the hydraulic power unit are regulated and controlled, and the stability of power output of the hydraulic power unit is improved.

Description

Technical Field

[0001] This application relates to the field of hydraulic device technology, and particularly to a hydraulic power unit. Background Art

[0002] The hydraulic power unit (HPU) is used as an oil supply device, which is connected to several hydraulic cylinders through an external pipeline system to control the operation of multiple groups of valves. The fuel tank, oil pump, and accumulator form an independent and sealed power oil source system. The oil station can be equipped with a PLC control system, which controls all internal hydraulic functions and generates signals to exchange with the control room (DCS). On a ship, the hydraulic control unit is mainly installed inside the control actuator on the ship. Through the coordinated action with other parts inside the control actuator, the hydraulic control unit jointly realizes operations such as hull steering and valve control.

[0003] In the existing hydraulic control unit, due to the configuration of switching valves at both the left and right ends, it can only control the opening and closing of the oil circuit. During actual use, such a structure often causes the control actuator to act stiffly and unable to achieve smooth operation, resulting in a poor user experience. Summary of the Utility Model

[0004] In order to improve the problem that the hydraulic control unit in the control actuator can only control the opening and closing of the oil circuit and cannot control the flow rate of the oil circuit, resulting in the output power of the control actuator being too stiff to achieve smooth control and a poor actual use experience, this application provides a hydraulic power unit.

[0005] The hydraulic power unit provided by this application adopts the following technical solutions:

[0006] A hydraulic power unit includes a fuel tank with a bidirectional gear pump installed inside, a valve body arranged at one end of the fuel tank, and a bidirectional motor installed at the end of the valve body far from the fuel tank. A coupling is rotatably arranged along the axis inside the valve body, and both ends of the coupling are fixedly connected to the bidirectional gear pump and the bidirectional motor respectively. First oil circuits communicating with the fuel tank are symmetrically arranged inside the valve body. Two second oil circuits respectively communicating with the two first oil circuits are symmetrically arranged inside the valve body. A third oil circuit penetrating the valve body is opened at the same end of the two second oil circuits. A piston is slidably arranged inside the third oil circuit. Throttle valves for changing the oil flow rate and velocity are installed at both port positions of the third oil circuit in the valve body. Both ends of the piston are respectively inserted and fitted into the two throttle valves, and both throttle valves are connected with power output structures.

[0007] By adopting the above technical solution, the bidirectional motor rotates and drives the bidirectional gear pump in the fuel tank to work, sucking the oil into the interior of the fuel tank. Then, the oil enters the interior of the valve body through the first oil passage. The piston in the valve body squeezes the oil flowing into the third oil passage through the second oil passage under the action of two throttle valves, enabling the oil to be smoothly transmitted to the power output structure position, and then delivering the power to the control actuator. Among them, the throttle valve can regulate the flow rate and velocity of the oil flowing through the third oil passage, so as to make the power output more stable while controlling the power output size, so that the hydraulic power unit can adapt to the requirements of various systems and improve the adaptation range of the hydraulic power unit.

[0008] Optionally, the throttle valve includes a one-way valve seat installed on one side of the valve body, a one-way plug arranged in the one-way valve seat, a one-way valve core slidably arranged in the one-way valve seat, and a one-way spring fixedly connected to the one-way plug and the one-way valve core at both ends. The one-way valve core encloses a one-way inner cavity in the one-way valve seat. The end of the one-way valve seat close to the piston is provided with a first one-way valve port communicating with the one-way inner cavity. One end of the piston is slidably fitted in the first one-way valve port. The end of the one-way valve seat is circumferentially provided with a plurality of second one-way valve ports communicating with the one-way inner cavity.

[0009] By adopting the above technical solution, when the throttle valve works, the oil enters the one-way inner cavity through the first one-way valve port, and then the oil is squeezed by the piston and discharged into the position of the power output mechanism from the second one-way valve port. During this process, since the volume of the one-way inner cavity in the throttle valve can be changed by rotating the one-way plug, it can also affect the flow rate and velocity of the oil. The operation is simple, and there will be no situation of instant opening or blocking of the oil passage, making the power output by the hydraulic power unit more stable.

[0010] Optionally, both of the two second oil passages communicate with the outside of the valve body, and overflow valves are installed at the positions of the two second oil passage ports of the valve body. The valve body is provided with an overflow oil passage penetrating and communicating with the fuel tank. The overflow oil passage is communicated with the overflow ports of both overflow valves. A taper plug is installed at the port of the overflow oil passage far from the fuel tank on the valve body.

[0011] By adopting the above technical solution, when the oil entering the interior of the fuel tank from the bidirectional gear pump per unit time is too much, or when the oil entering the second oil passage from the first oil passage per unit time is too much, resulting in exceeding the range that the valve body can bear, the excessive oil in the fuel tank can be discharged through the overflow oil passage opened on the valve body, and the oil in the valve body can be discharged into the overflow oil passage through the overflow valves at the ends of the second oil passages, so as to reduce the amount of oil in the interior of the valve body and avoid the situation of blocking the second oil passage and the third oil passage when there is too much oil in the second oil passage, affecting the normal operation of the hydraulic power unit.

[0012] Optionally, the overflow valve includes an overflow regulating valve installed in the valve body, a conical valve core slidably disposed on the overflow regulating valve, an overflow seat abutted against the end of the conical structure of the conical valve core, and an overflow spring installed between the conical valve core and the overflow seat. A first overflow port communicating with the second oil passage is formed through the end of the overflow seat, and a plurality of second overflow ports communicating with the overflow oil passage are uniformly formed in the circumferential direction.

[0013] By adopting the above technical solution, when the oil in the first oil passage and the second oil passage exceeds the bearing range, due to the increase in pressure inside the oil, the oil will pass through the first overflow port and squeeze the conical valve core abutted against the overflow seat. After the conical valve core is squeezed, the overflow spring drives the conical valve core to separate from the overflow seat, and the oil then enters the overflow valve and is discharged into the overflow oil passage through the second overflow port, thereby realizing the decompression and diversion of the oil, enabling the valve body to work more stably and improving the working stability of the equipment.

[0014] Optionally, the two power output structures are symmetrically arranged. The power output structure includes a fourth oil passage with two ends respectively communicating with the second one-way valve port and the outside of the valve body. The fourth oil passage is communicated with a fifth oil passage, and a reversing valve rod is installed inside the fifth oil passage.

[0015] By adopting the above technical solution, the oil passes through the fourth oil passage and the fifth oil passage, and the power is output to the outside of the hydraulic power unit through the reversing valve rod in the fifth oil passage, avoiding the situation of unstable power transmission caused by direct oil power transmission and making the equipment operation more stable.

[0016] Optionally, a small oil outlet and a large oil outlet are respectively communicated between the reversing valve rod and the second one-way valve port in the fourth oil passage, and cone plugs are installed on the valve body at the positions of the small oil outlet and the large oil outlet.

[0017] By adopting the above technical solution, it is convenient to relieve the pressure of the oil flowing into the fourth oil passage and the fifth oil passage, preventing the problem of damage to the reversing valve rod caused by excessive oil pressure in the fourth oil passage and the fifth oil passage, and improving the operation safety of the equipment.

[0018] Optionally, a set of hydraulic locks for preventing the oil in the valve body from flowing back are embedded in the valve body, and the two hydraulic locks are respectively communicated with the two first oil passages.

[0019] By adopting the above technical solution, it is possible to prevent the oil entering the valve body from flowing back into the fuel tank, resulting in the abnormal operation of the hydraulic power unit. In addition, the oil backflow will also cause the hydraulic power unit to be unable to output power or the output power to suddenly cut off, causing danger.

[0020] Optionally, an oil level gauge for observing the oil quantity inside the fuel tank is provided at the end of the fuel tank away from the valve body.

[0021] By adopting the above technical solution, it is convenient to monitor the oil quantity inside the fuel tank in real time, and avoid the situation that the hydraulic power cannot work due to insufficient oil.

[0022] In summary, the present application includes at least one of the following beneficial technical effects:

[0023] 1. By adopting a throttle valve in the hydraulic power unit, the present application effectively controls the flow rate and flow velocity of the oil inside the valve body. While making the output power of the hydraulic power unit more stable, it also facilitates the hydraulic power unit to adapt to the requirements of various systems;

[0024] 2. The present application designs a plurality of mechanisms inside the valve body for reducing the oil quantity and oil hydraulic pressure inside the valve body, protecting the oil inside the valve body from being blocked, and maintaining the stable operation of the hydraulic power unit. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 is an overall structural view of a hydraulic power unit of the present application.

[0026] Figure 2 is an exploded view of the overall structure of a hydraulic power unit of the present application.

[0027] Figure 3 is an exploded view of the valve body structure of a hydraulic power unit of the present application.

[0028] Figure 4 is a front view of the valve body of a hydraulic power unit of the present application.

[0029] Figure 5 is Figure 4 a sectional view taken along line A-A in

[0030] Figure 6 is a right side view of the valve body of a hydraulic power unit of the present application.

[0031] Figure 7 is Figure 6 a sectional view taken along line B-B in

[0032] Figure 8 is an overall view of the piston of a hydraulic power unit of the present application.

[0033] Figure 9 is an exploded view of the throttle valve structure of a hydraulic power unit of the present application.

[0034] Figure 10It is the left side view of the valve body of a hydraulic power unit of the present application.

[0035] Figure 11 It is Figure 10 the cross-sectional view at C-C in

[0036] Figure 12 It is Figure 10 the cross-sectional view at D-D in

[0037] Figure 13 It is the exploded view of the relief valve structure of a hydraulic power unit of the present application.

[0038] Explanation of reference numerals: 1, fuel tank; 11, oil inlet; 12, plug; 13, oil level gauge; 2, bi-directional gear pump; 3, valve body; 31, first oil passage; 32, second oil passage; 33, third oil passage; 331, retaining ring; 34, fourth oil passage; 35, fifth oil passage; 36, relief oil passage; 4, bi-directional motor; 5, coupling shaft; 6, throttle valve; 61, check valve seat; 611, first check valve port; 612, O-ring; 613, second check valve port; 62, check valve plug; 63, check valve core; 64, check valve spring; 65, check valve cavity; 7, piston; 71, pressing head; 8, power transmission mechanism; 81, reversing valve rod; 82, small oil outlet; 83, large oil outlet; 84, taper plug; 9, relief valve; 91, relief regulating valve; 92, taper valve core; 93, relief valve seat; 931, first relief port; 932, second relief port; 94, relief spring. Detailed implementation manners

[0039] The following will Figures 1-13 further describe the present application in detail with reference to the attached drawings.

[0040] The embodiment of the present application discloses a hydraulic power unit.

[0041] Referring to Figure 1 and Figure 2 , a hydraulic power unit includes a fuel tank 1 in a cylindrical shape with a bi-directional gear pump 2 installed inside, and a valve body 3 provided at one end of the fuel tank 1 and threadedly connected to the fuel tank 1. A bi-directional motor 4 is connected to the end of the valve body 3 away from the fuel tank 1, and a coupling shaft 5 is rotatably provided in the middle of the valve body 3. Both ends of the coupling shaft 5 pass through the valve body 3 and are respectively fixedly connected to the bi-directional motor 4 and the bi-directional gear pump 2. When the bi-directional motor 4 operates, it will drive the bi-directional gear pump 2 through the coupling shaft 5 to suck oil into the valve body 3. A plurality of oil inlets 11 for oil inlet are circumferentially provided on the fuel tank 1, and plugs 12 are threadedly connected to the positions of the oil inlets 11. An oil level gauge 13 is installed at the end of the fuel tank 1 away from the valve body 3 to observe the oil quantity inside the fuel tank 1 in real time and avoid sudden interruption of the power output of the hydraulic power unit.

[0042] In this design, a set of hydraulic locks for preventing the oil fluid from flowing back into the fuel tank 1 after entering the valve body 3 are installed inside the valve body 3. Since the hydraulic locks are commonly embedded inside the valve body 3 and the structure and connection method need to be selected according to the internal structure of the valve body 3, they are not shown in the attached drawings of this design.

[0043] Preferably, the housing of the bidirectional motor 4 is provided with heat sinks made of aluminum alloy to facilitate better heat dissipation. Since the motor with heat sinks belongs to the prior art, it is not separately shown in the attached drawings.

[0044] Refer to Figure 3 、 Figure 4 and Figure 5 and, further, two first oil passages 31 are symmetrically opened on one side of the valve body 3 close to the fuel tank 1 along the axis direction of the fuel tank 1. Two second oil passages 32 are symmetrically opened inside the valve body 3. The two first oil passages 31 are respectively communicated with the two second oil ports, and the two mutually communicated first oil passages 31 and the second oil passages 32 are perpendicular to each other. The valve body 3 is penetrated with a third oil passage 33 perpendicular to the first oil passage 31 and the second oil passage 32. The third oil passage 33 is opened at the same end of the two second oil passages 32 and is communicated with both of the two second oil passages 32.

[0045] Refer to Figure 6 、 Figure 7 and Figure 8 and, even further, two throttle valves 6 are symmetrically installed at the two ports of the third oil passage 33 on the valve body 3. A piston 7 is slidably arranged in the third oil passage 33, and both ends of the piston 7 can extend into the two throttle valves 6. The length of the piston 7 along the axis direction is greater than the distance between the two second oil passages 32 along the axis direction of the third oil passage 33, so that when the piston 7 slides towards one of the throttle valves 6, the oil fluid entering the third oil passage 33 from the second oil passage 32 can be pressed into this throttle valve 6. In addition, both of the two throttle valves 6 are connected with power transmission structures for discharging the oil fluid from the throttle valves 6 to transmit power.

[0046] Preferably, retaining rings 331 are fixedly arranged at both ends of the piston 7 in the third oil passage 33 to prevent the piston 7 from completely abutting against the throttle valve 6, resulting in the situation that the oil fluid cannot smoothly enter the throttle valve 6.

[0047] Refer to Figure 7 and Figure 9, Specifically, the throttle valve 6 includes a cylindrical one-way valve seat 61 threadedly connected to the port position of the third oil passage 33 on the valve body 3, a one-way plug 62 threadedly connected inside the one-way valve seat 61, a one-way valve core 63 slidably disposed inside the one-way valve seat 61 near one end of the piston 7, and a one-way spring 64 fixedly connected to the one-way valve core 63 and the one-way plug 62 at both ends. Among them, the one-way valve seat 61 and the one-way valve core 63 jointly enclose a one-way inner cavity 65 with a variable volume. One end of the one-way valve seat 61 near the piston 7 is penetrated with a first one-way valve port 611, and both ends of the piston 7 are integrally connected with a pressing head 71 slidably fitted in the first one-way valve port 611. When the piston 7 approaches one of the throttle valves 6, the pressing head 71 will squeeze the oil in the third oil passage 33 into the throttle valve 6.

[0048] Preferably, one end of the one-way valve core 63 near the piston 7 is a conical structure, and its diameter along the cross-section is larger than the diameter of the first one-way valve port 611. When the one-way valve core 63 abuts against the one-way valve seat 61 under the action of the one-way spring 64, the first one-way valve port 611 can be completely closed.

[0049] Preferably, an O-ring 612 is sleeved outside the one-way valve seat 61 to facilitate forming a sealing effect, prevent oil from leaking out from the port position of the third oil passage 33, and maintain the pressure stability of the oil in the valve body 3.

[0050] Refer to Figure 7 、 Figure 9 、 Figure 11 and Figure 12 , Further, four second one-way valve ports 613 communicating with the one-way inner cavity 65 are circumferentially provided at one end of the one-way valve seat 61 near the piston 7. The power output mechanism includes two fourth oil passages 34 symmetrically provided on the valve body 3. The fourth oil passage 34 is connected with a fifth oil passage 35, and a reversing valve rod 81 for transmitting power is installed in the fifth oil passage 35.

[0051] Preferably, a plurality of small oil outlets 82 and large oil outlets 83 for draining oil to prevent the pressure of the oil in the fourth oil passage 34 from being too high are provided in the fourth oil passage 34 between the throttle valve 6 and the fifth oil passage 35, and a tapered plug 84 is threadedly connected to the valve body 3 at the positions of the small oil outlets 82 and the large oil outlets 83. During actual use, appropriate oil outlets can be selected according to actual needs to maintain the flow rate and flow stability of the oil in the valve body 3.

[0052] Refer to Figure 6 and Figure 13, at the ends of the two second oil passages 32 far from the third oil passage 33, both pass through the valve body 3, and at the port positions of the two second oil passages 32 on the valve body 3, overflow valves 9 are threadedly connected. The valve body 3 is penetrated with an overflow oil passage 36 communicating with both overflow valves 9, and at the port of the overflow oil passage 36 far from the fuel tank 1 on the valve body 3, a taper plug 84 is threadedly connected. The overflow oil passage 36 communicates with the fuel tank 1. When the oil in the fuel tank 1 is excessive and exceeds the bearing capacity of the valve body 3, the oil can be discharged through the overflow oil passage 36 to reduce the pressure of the oil inside the valve body 3 and play a role in shunting. At the same time, the oil in the two overflow valves 9 can also be discharged through the overflow oil passage 36 to reduce the oil pressure in the first oil passage 31 and the second oil passage 32.

[0053] Refer to Figure 6 and Figure 13 , specifically, the overflow valve 9 includes an overflow regulating valve 91 threadedly connected to the port of the second oil passage 32 on the valve body 3, a taper valve core 92 slidably penetrating through one end of the overflow regulating valve 91 close to the third oil passage 33, and an overflow seat 93 abutted against one end of the taper valve core 92 close to the third oil passage 33. An overflow spring 94 is connected between the taper valve core 92 and the overflow seat 93. The overflow seat 93 is axially penetrated with a first overflow port 931, and the diameter of the cross-section of the side of the taper valve core 92 close to the overflow spring 94 is larger than the diameter of the first overflow port 931.

[0054] The overflow spring 94 is always in a compressed state so that when the oil pressure in the second oil passage 32 is within the bearing range, the taper valve core 92 can abut against the overflow seat 93 to play a sealing role.

[0055] The overflow seat 93 is circumferentially provided with a plurality of second overflow ports 932, and the second overflow ports 932 communicate with the overflow oil passage 36. When the oil in the second oil passage 32 squeezes the taper valve core 92 into the overflow valve 9, it can be discharged from the second overflow ports 932 and the overflow oil passage 36 out of the valve body 3.

[0056] The implementation principle of a hydraulic power unit in an embodiment of the present application is as follows:

[0057] The bidirectional motor 4 rotates, driving the bidirectional gear pump 2 to suck oil from the oil inlet 11 into the fuel tank 1 and making the oil enter the first oil passage 31 and the second oil passage 32 of the valve body 3. The oil in the second oil passage 32 enters the third oil passage 33 and is respectively squeezed into the two throttle valves 6 by the piston 7. Then, the piston 7 continuously squeezes, and the oil enters the first oil passage 31 and the fifth oil passage 35. The reversing valve rod 81 in the fifth oil passage 35 is squeezed by the oil and transmits the power to the control actuator.

[0058] In this process, when the oil quantity exceeds the bearing capacities of the first oil passage 31 and the second oil passage 32, the external oil fluid of the valve body 3 will be discharged to the outside through the overflow oil passage 36; and the oil fluid inside the valve body 3 will press the conical valve core 92 at the position of the first overflow port 931, enter into the overflow valve 9, and finally enter the overflow oil passage 36 from the position of the second overflow port 932 and be discharged.

[0059] The above are all preferred embodiments of the present application, and the protection scope of the present application is not limited thereby. Therefore, all equivalent changes made according to the structure, shape, and principle of the present application shall be covered within the protection scope of the present application.

Claims

1. A hydraulic power unit, comprising an oil tank (1) in which a bidirectional gear pump (2) is installed, a valve body (3) arranged at one end of the oil tank (1), and a bidirectional motor (4) installed at an end of the valve body (3) away from the oil tank (1), a connecting shaft (5) is arranged in the valve body (3) to rotate along an axis, and two ends of the connecting shaft (5) are respectively fixedly connected to the bidirectional gear pump (2) and the bidirectional motor (4), characterized in that: The valve body (3) is symmetrically provided with a first oil circuit (31) in communication with the oil tank (1), and the valve body (3) is symmetrically provided with two second oil circuits (32) in communication with the two first oil circuits (31) respectively. The valve body (3) is provided with a third oil circuit (33) penetrating the valve body (3) at the same end of the two second oil circuits (32), and a piston (7) is slidably provided in the third oil circuit (33). The valve body (3) is provided with throttle valves (6) for changing the flow rate and flow rate of oil at two port positions of the third oil circuit (33), and the two ends of the piston (7) are respectively penetrated and matched in the two throttle valves (6), and the two throttle valves (6) are both connected to a power output structure.

2. A hydraulic power unit according to claim 1, characterized in that: The throttle valve (6) comprises a one-way valve seat (61) installed on one side of the valve body (3), a one-way screw plug (62) arranged in the one-way valve seat (61), a one-way valve core (63) slidably arranged in the one-way valve seat (61), and a one-way spring (64) whose two ends are respectively fixedly connected to the one-way screw plug (62) and the one-way valve core (63); the one-way valve core (63) is surrounded by a one-way inner cavity (65) in the one-way valve seat (61); the end of the one-way valve seat (61) close to the piston (7) is provided with a first one-way valve port (611) connected to the one-way inner cavity (65); one end of the piston (7) is slidably fitted in the first one-way valve port (611); and the end of the one-way valve seat (61) is provided with a plurality of second one-way valve ports (613) connected to the one-way inner cavity (65) along the circumferential direction.

3. A hydraulic power unit according to claim 1, characterized in that: The two second oil passages (32) are both connected to the outside of the valve body (3), and the valve body (3) is provided with overflow valves (9) at the ports of the two second oil passages (32). The valve body (3) is provided with an overflow oil passage (36) connected to the oil tank (1). The overflow oil passage (36) is connected to the overflow ports of the two overflow valves (9), and a cone plug (84) is installed on the valve body (3) at the port of the overflow oil passage (36) away from the oil tank (1).

4. A hydraulic power unit according to claim 3, characterized in that: The overflow valve (9) comprises an overflow regulating valve (91) installed in the valve body (3), a conical valve core (92) slidably arranged on the overflow regulating valve (91), an overflow seat (93) abutting against the conical structural end of the conical valve core (92), and an overflow spring (94) installed between the conical valve core (92) and the overflow seat (93); a first overflow port (931) connected to the second oil circuit (32) is opened through the end of the overflow seat (93), and a plurality of second overflow ports (932) connected to the overflow oil circuit (36) are evenly opened along the circumference.

5. A hydraulic power unit according to claim 2, characterized in that: The two power output structures are symmetrically arranged, and the power output structure comprises a fourth oil circuit (34) whose two ends are respectively connected to the second one-way valve port (613) and the outside of the valve body (3), the fourth oil circuit (34) is connected to a fifth oil circuit (35), and a reversing valve rod (81) is installed inside the fifth oil circuit (35).

6. A hydraulic power unit according to claim 5, characterized in that: A small oil outlet (82) and a large oil outlet (83) are respectively connected between the reversing valve stem (81) and the second one-way valve port (613) in the fourth oil circuit (34), and a cone plug (84) is installed at the position of the small oil outlet (82) and the large oil outlet (83) of the valve body (3).

7. A hydraulic power unit according to claim 1, characterized in that: A group of hydraulic locks for preventing the oil inside the valve body (3) from flowing back are embedded in the valve body (3), and two of the hydraulic locks are respectively connected to the two first oil passages (31).

8. A hydraulic power unit according to claim 1, characterized in that: An oil mark (13) for observing the oil level inside the oil tank (1) is provided at the end of the oil tank (1) away from the valve body (3).

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