A hydraulic motor balancing valve group with energy recovery and safety release functions

Abstract

The present invention discloses a hydraulic motor balancing valve assembly with energy recovery and safety release functions. The balancing valve assembly includes a balancing valve, a hydraulically controlled reversing valve, and a shuttle valve. Ports A and B of the balancing valve assembly are respectively connected to an external oil supply circuit. Port A of the balancing valve assembly is connected to port A1 of the hydraulic motor via the balancing valve and a first oil circuit. Port B of the balancing valve assembly is connected to port B1 of the hydraulic motor via a third shut-off valve and a second oil circuit. The balancing valve assembly further includes a first electromagnetic reversing valve and an eighth shut-off valve. Port A of the first electromagnetic reversing valve is connected to the first oil circuit, and port B of the first electromagnetic reversing valve is connected to port B of the eighth shut-off valve via a third oil circuit. Port A of the eighth shut-off valve is connected to port XQ of the balancing valve assembly, and port XQ of the balancing valve assembly is connected to an external accumulator. The present invention has the beneficial effects of solving the problems of being unable to safely release at low tension values, being unable to recover and reuse released potential energy, and rapidly overheating the motor due to too low a release speed.

Description

Technical Field

[0001] The present invention relates to a winch drive mechanism, and in particular to a hydraulic motor balancing valve group with energy recovery and safety release functions. Background Art

[0002] When lifting, cranes often experience a power failure, leaving the load suspended in mid-air. For safety reasons, the load must be lowered. However, for particularly valuable loads, lowering the load at a low tension setting is essential. If the load remains outside the safe lowering range when power is lost, the crane must be hoisted, and the boom and slew angle adjusted, requiring additional power.

[0003] To safely lower heavy objects, a manual release function is typically employed. This is achieved by opening the winch brake and connecting the winch motor's A and B ports. Conventional motor balancing valves lack a low-tension control function between motor ports A and B. This makes it impossible to achieve low-tension control between motor ports A and B in emergency situations, hindering the effective and safe release of valuable loads. In the event of a complete power loss, conventional motor balancing valves are unable to capture the potential energy of the lowered load, making it impossible to lower the load safely in the event of a complete power loss. Therefore, there is an urgent need to develop a motor balancing valve that can address these issues. Summary of the Invention

[0004] The purpose of the present invention is to address the shortcomings of the existing technology and provide a hydraulic motor balancing valve group with energy recovery and safety release functions to solve the problems that the existing conventional motor balancing valve group cannot automatically store energy when heavy objects are lowered in an emergency and cannot achieve low tension value communication between the motor A and B chambers in an emergency.

[0005] The present invention adopts a novel technical solution: a hydraulic motor balancing valve group with energy recovery and safety release functions, the balancing valve group comprising a balancing valve, a hydraulically controlled reversing valve, and a shuttle valve. Port A of the balancing valve group is connected to port A1 of the hydraulic motor via the balancing valve and a first oil circuit; port B of the balancing valve group is connected to port B1 of the hydraulic motor via a third shut-off valve and a second oil circuit; port A of the balancing valve group is connected to the second oil circuit via a shuttle valve; port X of the balancing valve is connected to the second oil circuit; port L0 of the balancing valve is connected to port T of the hydraulically controlled reversing valve; the shuttle valve is connected to port P of the hydraulically controlled reversing valve and port X of the pilot control; port A of the hydraulically controlled reversing valve is connected to ports SC and SB of the balancing valve group, respectively; the balancing valve group further comprises a first solenoid reversing valve and an eighth shut-off valve. Port A of the first solenoid reversing valve is connected to the first oil circuit, port B of the first solenoid reversing valve is connected to port B of the eighth shut-off valve via a third oil circuit, port A of the eighth shut-off valve is connected to port XQ of the balancing valve group, and port XQ of the balancing valve group is connected to an external accumulator.

[0006] According to the above scheme, a second electromagnetic reversing valve and a first overflow valve are further provided in the balancing valve group. Port a of the second electromagnetic reversing valve is connected to the first oil circuit and port a of the first electromagnetic reversing valve, and port b of the second electromagnetic reversing valve is connected to the second oil circuit through the first overflow valve; the first overflow valve is a low-pressure overflow valve.

[0007] According to the above scheme, the balancing valve group is additionally provided with an L port connected to the external oil circuit system. The l0 port of the balancing valve and the t port of the hydraulically controlled reversing valve are respectively connected to the L port of the balancing valve group, and the oil leakage of both is discharged to the external oil circuit system through the L port of the balancing valve group.

[0008] According to the above scheme, the third oil circuit is connected to the HY port of the balancing valve group through the third overflow valve, and enters the external oil tank through it; the third oil circuit is connected to the GY port of the balancing valve group through the sixth stop valve; the third oil circuit is connected to the QJ port of the balancing valve group through the seventh stop valve; the third overflow valve is a high-pressure overflow valve.

[0009] According to the above solution, a first stop valve and a first throttle hole are further provided in the balancing valve group. Port a of the first stop valve is connected to the first oil circuit, and port b of the first stop valve is connected to the second oil circuit through the first throttle hole.

[0010] According to the above scheme, a second overflow valve and a one-way valve are further provided in the balancing valve group. The p port of the second overflow valve is connected to the first oil circuit, the t port of the second overflow valve is connected to the second oil circuit, and the t port of the second overflow valve is connected to the BY port of the balancing valve group through the one-way valve.

[0011] According to the above solution, a pressure sensor is additionally provided in the balancing valve group, and a detection end of the pressure sensor is located in the third oil circuit.

[0012] The beneficial effects of the present invention are:

[0013] 1. The motor balancing valve group of the present invention solves the problems of inability to release safely at low tension values, inability to recover and reuse released potential energy, and rapid overheating of the motor due to too low a release speed through the designed first solenoid reversing valve, second solenoid reversing valve, relief valve, stop valve, etc. and the connection of related pipelines. At the same time, it solves the problems of oil replenishment at the motor B port when the motor A and B chambers are connected, external pressure oil activating the brake, and the possibility of affecting the normal closing of the balancing valve due to excessive pressure of external oil replenishment or control of brake pressure oil. It improves the normal use of lifting equipment and the reliability of safe release of heavy objects, has a high safety factor, and is highly adaptable.

[0014] 2. The motor balancing valve group of the present invention has a high degree of integration, flexible control, easy disassembly and inspection, and a higher degree of safety. It has the functions of normally lowering the load, safely releasing the load, recovering the energy released by the load and serving as a power source to drive other mechanisms, etc., which fully guarantees the safe lifting of the lifting machinery. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a structural diagram of a specific embodiment of the present invention.

[0016] Among them: 1. Hydraulic motor; 2. Balancing valve; 3. Filter; 4. Check valve; 5. Shuttle valve; 6. Pressure reducing valve; 7. Hydraulically controlled reversing valve; 8. Pressure sensor; JZ1, first stop valve; JZ2, second stop valve; JZ3, third stop valve; JZ4, fourth stop valve; JZ5, fifth stop valve; JZ6, sixth stop valve; JZ7, seventh stop valve; JZ8, eighth stop valve; JL1, first throttle valve; JL2, pilot throttle valve; YL1, first overflow valve; YL2, second overflow valve; YL3, third overflow valve; DC1, first solenoid reversing valve; DC2, second solenoid reversing valve. DETAILED DESCRIPTION

[0017] In order to better understand the present invention, the present invention is further described below with reference to the accompanying drawings and specific embodiments.

[0018] like Figure 1 The figure shows a hydraulic motor balancing valve group with energy recovery and safety release functions, wherein the balancing valve group is provided with a balancing valve 2, a hydraulically controlled reversing valve 7 and a shuttle valve 5. The A port of the balancing valve group is connected to the A1 port of the hydraulic motor 1 through the balancing valve 2 and the first oil circuit; the B port of the balancing valve group is connected to the B1 port of the hydraulic motor 1 through the third stop valve JZ3 and the second oil circuit; the A port and the B port of the balancing valve group are respectively connected to the external oil supply circuit to realize the inflow and outflow of oil. When the hydraulic motor 1 rotates forward (winch), oil enters the A port of the balancing valve 2 group and oil exits the B port; when the hydraulic motor 1 reverses (lowers), oil enters the B port of the balancing valve 2 group and oil exits the A port. The A port of the balancing valve group is connected to the second oil circuit through the shuttle valve 5; the x port of the balancing valve 2 is connected to the second oil circuit; the l0 port of the balancing valve 2 is connected to the t port of the hydraulically controlled reversing valve 7; the shuttle valve 5 is connected to the p port and the pilot control x port of the hydraulically controlled reversing valve 7, and the a port of the hydraulically controlled reversing valve 7 is respectively connected to the SC port and the SB port of the balancing valve group.

[0019] In the present invention, the balancing valve group is further provided with a first electromagnetic reversing valve DC1 and an eighth stop valve JZ8. The a port of the first electromagnetic reversing valve DC1 is connected to the first oil circuit, the b port of the first electromagnetic reversing valve DC1 is connected to the b port of the eighth stop valve JZ8 through the third oil circuit, the a port of the eighth stop valve JZ8 is connected to the XQ port of the balancing valve group, and the XQ port of the balancing valve group is connected to the external accumulator.

[0020] Specifically, in this embodiment, port A of the balancing valve group communicates with port a of balancing valve 2, and port b of balancing valve 2 communicates with port A1 of hydraulic motor 1 via the first oil circuit. Port B of the balancing valve group communicates with port a of the third shut-off valve JZ3, and port b of the third shut-off valve JZ3 communicates with port B1 of hydraulic motor 1 via the second oil circuit. Port x of balancing valve 2 communicates with the second oil circuit via the second throttle orifice JL2 and the second shut-off valve JZ2. Specifically, port x of balancing valve 2 communicates with port b of the second throttle orifice JL2, and port a of the second throttle orifice JL2 communicates with port b of the second shut-off valve JZ2 via the filter 3. Port a of the second shut-off valve JZ2 communicates with port b of the third shut-off valve JZ3 via the second oil circuit. Port l0 of balancing valve 2 communicates with port t of hydraulically controlled reversing valve 7. Port a of hydraulically controlled reversing valve 7 communicates with port SC of the balancing valve assembly via fourth shut-off valve JZ4. Port SC of the balancing valve assembly communicates with the external power source. Port a of hydraulically controlled reversing valve 7 communicates with port SB of the balancing valve assembly via fourth shut-off valve JZ4 and fifth shut-off valve JZ5. Port SB of the balancing valve assembly is connected to the winch brake. Port a of shuttle valve 5 communicates with port A of the balancing valve assembly. Port b of shuttle valve 5 communicates with the second oil circuit. Port c of shuttle valve 5 communicates with port p and pilot control port x of hydraulically controlled reversing valve 7 via pressure reducing valve 6 (port a of pressure reducing valve 6 connects with port c of shuttle valve 5, and port b of pressure reducing valve 6 connects with port p and pilot control port x of hydraulically controlled reversing valve 7, respectively).

[0021] Preferably, the balancing valve group is additionally provided with an L port connected to the external oil circuit system, and the l0 port of the balancing valve 2 and the t port of the hydraulically controlled reversing valve 7 are respectively connected to the L port of the balancing valve group, and the oil leakage of both is discharged to the external oil circuit system through the L port of the balancing valve group.

[0022] Preferably, the third oil circuit is connected to the HY port of the balancing valve group through the third relief valve YL3, and then enters the external oil tank; the third oil circuit is connected to the GY port of the balancing valve group through the sixth stop valve JZ6; and the third oil circuit is connected to the QJ port of the balancing valve group through the seventh stop valve JZ7. Preferably, the third relief valve YL3 is a high-pressure relief valve.

[0023] In the present invention, the third oil circuit is connected to the p port of the third overflow valve YL3, and the t port of the third overflow valve YL3 is connected to the HY port of the balancing valve group; the third oil circuit is connected to the a port of the sixth stop valve JZ6, and the b port of the sixth stop valve JZ6 is connected to the GY port of the balancing valve group; the third oil circuit is connected to the a port of the seventh stop valve JZ7, and the b port of the seventh stop valve JZ7 is connected to the QJ port of the balancing valve group.

[0024] Preferably, the balancing valve assembly further includes a second solenoid reversing valve DC2 and a first relief valve YL1. Port a of the second solenoid reversing valve DC2 communicates with the first oil circuit and port a of the first solenoid reversing valve DC1. Port b of the second solenoid reversing valve DC2 communicates with the second oil circuit via the first relief valve YL1. The first relief valve YL1 is a low-pressure relief valve. In this embodiment, port b of the second solenoid reversing valve DC2 communicates with port p of the first relief valve YL1, while port t of the first relief valve YL1 communicates with the second oil circuit.

[0025] Preferably, a first stop valve JZ1 and a first throttle hole JL1 are further provided in the balancing valve group. The port a of the first stop valve JZ1 is connected to the first oil circuit, and the port b of the first stop valve JZ1 is connected to the second oil circuit through the first throttle hole JL1. Specifically, the port b of the first stop valve JZ1 is connected to the port a of the first throttle hole JL1, and the port b of the first throttle hole JL1 is connected to the second oil circuit.

[0026] Preferably, a second overflow valve YL2 and a one-way valve 4 are further provided in the balancing valve group, the p port of the second overflow valve YL2 is connected to the first oil circuit, the t port of the second overflow valve YL2 is connected to the second oil circuit, and the t port of the second overflow valve YL2 is connected to the BY port of the balancing valve group through the one-way valve 4.

[0027] Preferably, a pressure sensor 8 is added to the balancing valve assembly, with the detection end of the pressure sensor 8 located in the third oil circuit. When the winch lowers a heavy object, its potential energy is converted into hydraulic energy to store in the accumulator. If the lowering is prolonged, the accumulator will be full. At this time, a signal can be sent via the pressure sensor 8 to the first electromagnetic reversing valve DC1 to cut off the flow of oil, and the oil can be released at high pressure via the second relief valve YL2. 2. If the winch is not used for an extended period of time, the accumulator pressure may decrease due to internal leakage in the balancing valve assembly. This can be monitored by the pressure sensor 8, and the accumulator can be appropriately replenished for short-distance lifting of heavy objects in emergency situations.

[0028] In the present invention, the balancing valve 2 is a flow type balancing valve 2; the stop valves JZ1 to JZ8 are all throttling stop valves; the second relief valve YL2 and the third relief valve YL3 are both high-pressure relief valves, and the first relief valve YL1 is a low-pressure relief valve.

[0029] like Figure 1As shown, the balancing valve group described in this embodiment is connected to the A1 and B1 ports of the hydraulic motor 1 respectively. The GY port of the balancing valve group is an external oil replenishment port, used to replenish high-pressure oil from other external systems into the accumulator; the HY port is the overflow port after the accumulator reaches the maximum pressure, which is directly connected to the external oil tank of the hydraulic system; the QJ port is the accumulator oil release port, used to drain the oil in the accumulator when the accumulator is damaged, replaced, cleaned, or in non-operating operations; the XQ port is the connecting oil port between the accumulator and the balancing valve block, through which the accumulator communicates oil with the balancing valve block; the L port is the main oil drain port of the balancing valve block, which is connected to the external oil tank of the hydraulic system. The other oil ports and related configurations of the balancing valve group are commonly used in the prior art and will not be repeated here. A pressure measuring point MA is added to the connecting pipe of the A1 port of the hydraulic motor 1, and a pressure measuring point MB is added to the connecting pipe of the B1 port of the hydraulic motor 1. The other configurations of the hydraulic motor 1 are all in the prior art. The following is a detailed description of this embodiment.

[0030] The working principle of this embodiment is:

[0031] 1. Safe release action

[0032] The oil in the pressure chamber of the hydraulic motor 1 enters the balancing valve group through the A1 port, flows out from the a port of the second electromagnetic reversing valve DC2 through its b port, enters through the p port of the first relief valve YL1 and flows out from its t port, flows out through the B1 port of the balancing valve group and enters the oil suction chamber of the hydraulic motor 1, realizing the high-speed and stable operation of the hydraulic motor 1 at a low tension value, so as to increase the release speed.

[0033] The leaked oil generated by the operation of hydraulic motor 1 flows out through its L1 port and into the external oil tank.

[0034] The forced oil replenishment oil enters the balancing valve group through the BY port, flows in through the a port of the one-way valve 4, flows out through its b port, and enters the oil suction chamber of the hydraulic motor 1 through the B1 port to realize the replenishment of oil.

[0035] The variable control oil flows in from the PA port of the variable control cylinder of hydraulic motor 1, enters one side of the variable control cylinder through the ya port, pushes the variable control cylinder to the right to increase the displacement of hydraulic motor 1, and the oil on the other side of the variable control cylinder flows out through the yb port, flows out from the PB port of the variable control cylinder of hydraulic motor 1, and returns to the variable balancing valve group (external) of hydraulic motor 1.

[0036] During safe release, if release is difficult (i.e., the hydraulic motor 1 does not run or runs very slowly), it means that the displacement of the hydraulic motor 1 is set too large. By reducing the displacement of the hydraulic motor 1, the pressure value of its pressure chamber can be increased, and the pressure of the pressure oil from the first relief valve YL1 can be increased, thereby increasing the operating speed of the hydraulic motor 1. Since the operation of the hydraulic motor 1 is blocked by the pressure of the first relief valve YL1, it can achieve a smooth release of heavy objects within a certain speed range.

[0037] 2. Energy recovery action during release

[0038] When releasing, first close the second stop valve JZ2, the third stop valve JZ3 and the fourth stop valve JZ4, open the fifth stop valve JZ5, and the external power source (usually a manual pump) provides pressure oil to enter through the SB port of the balance valve group, flow through the fifth stop valve JZ5, and then flow out from the SC port of the balance valve group to the hoisting brake, opening the hoisting brake; the variable control oil flows from its PB port to the yb port and enters its variable control cylinder, driving its displacement to decrease, and the oil on the other side of the variable control cylinder is discharged from the ya port to the PA port, and then flows through its external The variable control valve returns the oil to the oil tank; when the pressure value displayed at pressure measuring point MA meets the energy recovery pressure range, the first solenoid reversing valve DC1 is energized (or manually controlled if power is lost). The oil in the pressure chamber of hydraulic motor 1 (the space enclosed by port b of balancing valve 2 and the detection position of pressure measuring point MA of hydraulic motor 1) enters through port a of the first solenoid reversing valve DC1, flows out through port b, passes through the eighth shut-off valve JZ8, flows to port XQ of the balancing valve group, and then enters the (external) accumulator, achieving energy storage and recovery. After energy recovery is completed, the oil discharged from the pressure chamber of hydraulic motor 1 enters through port p of YL3 (relief valve), is discharged through port t, flows to port HY of the balancing valve group, and then flows out into the external oil tank.

[0039] When hydraulic motor 1 is operating, the oil discharged from its pressure chamber and leaked through its L1 port (drain port) during operation needs to be replenished in its suction chamber (the space enclosed by the third shut-off valve JZ3 and the pressure measuring point MB of hydraulic motor 1). External forced oil replenishment enters through the BY port of the balancing valve block, flows to the a port of DX (check valve 4), and flows out through its b port to the B1 port of the balancing valve block. After passing through B1, it flows into the suction chamber of hydraulic motor 1, completing the oil replenishment.

[0040] During energy recovery, the displacement of hydraulic motor 1 is adjusted in real time based on the pressure in the hydraulic motor 1 pressure chamber measured at port MA. The variable control oil in hydraulic motor 1 flows through port PB to port yb, ultimately entering the variable control cylinder, reducing its displacement. The oil on the other side of the variable control cylinder is discharged through port ya to port PA, then returns to the tank via the external variable control valve. During operation, the pressure in the hydraulic motor 1 pressure chamber must be higher than the set value of the third relief valve YL3 to facilitate energy recovery and smooth lowering.

[0041] 3. Recovery energy drive mechanism action

[0042] The recovered energy stored in the accumulator (external) passes through the eighth stop valve JZ8 and then the bottom air stop valve to the QJ port of the balancing valve group, and then flows out through the QJ port to the main balancing valve group (external) of other external mechanisms. Other mechanisms (rotation and amplitude adjustment, etc.) can change the rotation angle of the whole machine and the lifting amplitude, thereby realizing the spatial position movement of the lifting, so that it can be lowered within a safe range; the recovered energy stored in the (external) accumulator can also pass through the eighth stop valve JZ8 and then enter through the first electromagnetic reversing valve DC1b port, flow out through its a port, and enter the pressure chamber of the hydraulic motor 1 through the A1 port, thereby driving the hydraulic motor 1 to operate in the forward hoisting direction.

[0043] In this embodiment, the return oil flow direction is as follows:

[0044] 1. When the load is lifted, the oil enters through port A of the balancing valve group, passes through balancing valve 2, enters port A1 of the balancing valve group, and then flows to the pressure chamber of hydraulic motor 1. After the hydraulic motor 1 is running, the oil flows out through port B1 and enters the balancing valve group, passes through the third stop valve JZ3, flows to port B of the balancing valve group, and then flows out and enters the external main balancing valve group;

[0045] 2. During safety release, the oil in the pressure chamber of hydraulic motor 1 enters the balancing valve group through port A1, enters through port a of the second solenoid reversing valve DC2, flows out through port b and enters port p of the first relief valve YL1, flows out through port t, and enters the oil suction chamber of hydraulic motor 1 through port B1 of the balancing valve group;

[0046] 3. During energy recovery, the oil in the pressure chamber of hydraulic motor 1 enters the balancing valve group through port A1, enters through port a of the first solenoid reversing valve DC1, and flows out through port b. A portion of the oil flows through the eighth stop valve JZ8 and then enters the external accumulator through port XQ of the balancing valve group. A portion of the oil flows through port p of YL3 (relief valve), flows out through port t, and flows out through port HY of the balancing valve group back to the external oil tank.

[0047] 4. When recovering energy to drive the hoisting mechanism, the oil enters from the first solenoid reversing valve DC1b port after passing through the eighth stop valve JZ8, flows out through port a, and enters the pressure chamber of hydraulic motor 1 from port A1 of the balancing valve group, driving the hydraulic motor 1 to operate in the forward hoisting direction. The oil discharged from hydraulic motor 1 flows in from port B1 of the balancing valve group, passes through the third stop valve JZ3, flows out from port B of the balancing valve group, enters the external main reversing valve group, and then returns to the oil tank.

[0048] In this embodiment, the oil drain flow direction of the hydraulic system is as follows:

[0049] 1. Hydraulic system oil leakage occurs regardless of winch lifting, lowering and releasing conditions;

[0050] 2. The oil drain of hydraulic motor 1 is discharged through port L1 of the hydraulic motor 1 housing;

[0051] 3. The oil leakage of the external brake is discharged through the L port of the balance valve group;

[0052] 4. All leaked oil is collected by pipelines outside the balancing valve group and then enters the external main pump station tank.

[0053] In the present invention, external oil enters the balancing valve assembly through port A. Port A connects to shuttle valve 5, which in turn connects to hydraulically controlled reversing valve 7, which in turn connects to fourth shut-off valve JZ4. Fourth shut-off valve JZ4 connects to fifth shut-off valve JZ5, which in turn connects to port SB of the balancing valve assembly, enabling emergency release of the hydraulic brake. Fourth shut-off valve JZ4 connects to balancing valve assembly SC, enabling normal hydraulic brake operation. Oil enters the balancing valve assembly through port A and connects to balancing valve 2, achieving dynamic braking of hydraulic motor 1 from dynamic to static and maintaining static pressure. Balancing valve 2 is connected to the second relief valve YL2 to achieve impact filtering and maximum pressure limitation. Balancing valve 2 is connected to the second solenoid reversing valve DC2, which is connected to the first relief valve YL1, to achieve impact filtering and maximum pressure limitation for hydraulic motor 1 under low load. Balancing valve 2 is connected to the first solenoid reversing valve DC1, which is connected to the third relief valve YL3, to achieve maximum pressure limitation during energy recovery. Balancing valve 2 is connected to the first stop valve JZ1, which is connected to the first throttle orifice JL1, to achieve safe and adjustable speed communication between hydraulic motor 1's A1 and B1 ports in emergency situations, achieving adjustable speed freewheel operation of hydraulic motor 1 and enabling manual release. Balancing valve 2 is connected to hydraulic motor 1's A1 port to achieve forward rotation (winch) operation of hydraulic motor 1.

[0054] The oil of the external accumulator enters the balancing valve group from the XQ port of the balancing valve group. On the one hand, the XQ port is connected to the eighth stop valve JZ8, and the eighth stop valve JZ8 is connected to the seventh stop valve JZ7 to release the accumulator oil; the eighth stop valve JZ8 is connected to the pressure sensor 8 (PT) to realize the pressure monitoring of the accumulator and the hydraulic motor 1A1 port; the eighth stop valve JZ8 is connected to the third overflow valve YL3 to realize the maximum pressure limit of the accumulator; the eighth stop valve JZ8 is connected to the first electromagnetic reversing valve DC1 to realize the filling and release of the hydraulic oil between the external accumulator and the hydraulic motor 1; the eighth stop valve JZ8 is connected to the sixth stop valve JZ6 to realize the filling of the accumulator.

[0055] The oil enters the interior of the balancing valve group through the B port of the balancing valve group, and the B port is connected to the third stop valve JZ3, the third stop valve JZ3 is connected to the shuttle valve 5, the shuttle valve 5 is connected to the hydraulically controlled reversing valve 7, the hydraulically controlled reversing valve 7 is connected to the fourth stop valve JZ4, and the fourth stop valve JZ4 is connected to the fifth stop valve JZ5 on one hand, and the fifth stop valve JZ5 is connected to the SB port of the balancing valve group to realize emergency release and open the hydraulic brake; the fourth stop valve JZ4 is connected to the balancing valve group SC on the other hand to realize the normal opening of the hydraulic brake. The third shut-off valve JZ3 is connected to the second shut-off valve JZ2, which is connected to the pilot filter 3 of the balancing valve 2. The pilot filter 3 is connected to the second throttle orifice JL2 of the balancing valve 2, ensuring smooth opening of the balancing valve 2. The third shut-off valve JZ3 is connected to the first throttle orifice JL1, which is in turn connected to the first shut-off valve JZ1. This allows for safe, adjustable speed communication between the A1 and B1 ports of the hydraulic motor 1 in an emergency, enabling an adjustable speed freewheeling state for the hydraulic motor 1 and manual release. The third shut-off valve JZ3 is connected to the B1 port of the hydraulic motor 1, enabling reverse (lowering) operation of the hydraulic motor 1.

[0056] The external oil replenishment fluid enters the balancing valve group through the BY port of the balancing valve group, the BY port is connected to the one-way valve 4, and the one-way valve 4 is connected to the B1 port of the hydraulic motor 1 to realize the oil replenishment of the hydraulic motor 1 during normal lowering and parking and emergency lowering.

[0057] Finally, it should be noted that the above are only preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the embodiments, those skilled in the art can still modify the technical solutions described in the aforementioned embodiments or make equivalent replacements for some of the technical features therein. However, any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A hydraulic motor balancing valve group with energy recovery and safety release functions, characterized in that: The balancing valve group is provided with a balancing valve (2), a hydraulically controlled reversing valve (7) and a shuttle valve (5); the A port and the B port of the balancing valve group are respectively connected to the external oil supply circuit; the A port of the balancing valve group is connected to the A1 port of the hydraulic motor (1) via the balancing valve (2) and the first oil circuit; the B port of the balancing valve group is connected to the B1 port of the hydraulic motor (1) via the third stop valve (JZ3) and the second oil circuit; the A port of the balancing valve group is connected to the second oil circuit via the shuttle valve (5); the X port of the balancing valve (2) is connected to the second oil circuit; the L0 port of the balancing valve (2) is connected to the T port of the hydraulically controlled reversing valve (7); the shuttle valve (5) is connected to the p port and the pilot control x port of the hydraulically controlled reversing valve (7), and the a port of the hydraulically controlled reversing valve (7) is respectively connected to the SC port and the SB port of the balancing valve group; the balancing valve group is further provided with a first electromagnetic reversing valve (DC1) and an eighth stop valve (JZ8), the a port of the first electromagnetic reversing valve (DC1) is connected to the first oil circuit, the b port of the first electromagnetic reversing valve (DC1) is connected to the b port of the eighth stop valve (JZ8) through the third oil circuit, the a port of the eighth stop valve (JZ8) is connected to the XQ port of the balancing valve group, and the XQ port of the balancing valve group is connected to an external accumulator; A second electromagnetic reversing valve (DC2) and a first relief valve (YL1) are further provided in the balancing valve group. Port a of the second electromagnetic reversing valve (DC2) is connected to the first oil circuit and port a of the first electromagnetic reversing valve (DC1). Port b of the second electromagnetic reversing valve (DC2) is connected to the second oil circuit via the first relief valve (YL1). The first relief valve (YL1) is a low-pressure relief valve. The third oil circuit is connected to the HY port of the balancing valve group through the third relief valve (YL3) and enters the external oil tank through the HY port; the third oil circuit is connected to the GY port of the balancing valve group through the sixth stop valve (JZ6); the third oil circuit is connected to the QJ port of the balancing valve group through the seventh stop valve (JZ7); the third relief valve (YL3) is a high-pressure relief valve; A first stop valve (JZ1) and a first throttle hole (JL1) are further provided in the balancing valve group; port a of the first stop valve (JZ1) is connected to the first oil circuit; and port b of the first stop valve (JZ1) is connected to the second oil circuit through the first throttle hole (JL1); A second overflow valve (YL2) and a one-way valve (4) are further provided in the balancing valve group. The p port of the second overflow valve (YL2) is connected to the first oil circuit, the t port of the second overflow valve (YL2) is connected to the second oil circuit, and the t port of the second overflow valve (YL2) is connected to the BY port of the balancing valve group through the one-way valve (4).

2. The hydraulic motor balancing valve assembly with energy recovery and safety release functions according to claim 1, characterized in that: The balancing valve group is additionally provided with an L port connected to an external oil circuit system. The L0 port of the balancing valve (2) and the t port of the hydraulically controlled reversing valve (7) are both connected to the L port of the balancing valve group, and the oil leakage of both is discharged to the external oil circuit system through the L port of the balancing valve group.

3. The hydraulic motor balancing valve assembly with energy recovery and safety release functions according to claim 1, characterized in that: A pressure sensor (8) is additionally provided in the balancing valve group, and a detection end of the pressure sensor (8) is located in the third oil circuit.

Images