A pressure-stabilizing differential valve, a hydraulic system, and a loader

Abstract

This utility model discloses a pressure-stabilizing differential valve, a hydraulic system, and a loader, belonging to the field of engineering machinery technology. It includes a valve body with an oil inlet (P1), an outlet (A1), and an outlet (A2). Inside the valve body are a pressure-reducing valve and a solenoid valve. The P1 inlet is connected to the oil inlet circuit, and the solenoid valve is connected to the A2 outlet, which is connected to the control port of the differential lock. Hydraulic oil sequentially passes through the P1 inlet, pressure-reducing valve, solenoid valve, and A2 outlet before entering the control port of the differential lock to achieve differential speed control. The pressure-reducing valve is also connected to the A1 outlet via an oil circuit. A pressure-reducing valve is installed before the solenoid valve to adjust the hydraulic oil pressure to match the differential lock's opening pressure range. The pressure-reducing valve connects to the A1 and A2 outlets, enabling differential speed control as well as other functions. An accumulator is installed between the pressure-reducing valve and the solenoid valve to release energy promptly when the A1 outlet is opened, preventing a rapid drop in hydraulic oil pressure in the differential chamber.

Description

Technical Field

[0001] This utility model belongs to the field of engineering machinery technology, specifically relating to a pressure-stabilizing differential valve, a hydraulic system, and a loader. Background Technology

[0002] The statements in this section are merely background information related to this utility model and do not necessarily constitute prior art.

[0003] When a loader encounters slippage on one side of its wheels, hydraulic oil is introduced, and the differential lock locks the differential housing and half-shaft together, forcing both wheels to rotate synchronously. This ensures that power is effectively transmitted to the wheel with traction, achieving rigid power distribution to improve the vehicle's ability to get out of trouble.

[0004] Existing loader differential systems, such as Figure 1 As shown, the differential lock connects the front and rear axles via a valve body. A solenoid valve is installed within the valve body. When differential function is needed, the solenoid valve opens the pressure channel, allowing pressurized oil to flow in and locking the differential housing and half-shafts together. When differential function needs to be released, the solenoid valve closes the pressure channel, allowing the pressurized oil to return to the lower-pressure oil tank. This releases the differential housing and half-shafts, allowing the wheels to move freely.

[0005] The above solution has the following problems:

[0006] It is impossible to guarantee that the hydraulic oil pressure and the differential lock opening pressure range of the axle are consistent, which may damage the axle or cause the differential lock to become loose, making it difficult to achieve differential operation normally; and when opening other oil passages ( Figure 1 At the instant of oil port A), the hydraulic oil pressure in the differential chamber drops rapidly, and the pressure replenishment rate is lower than the reduction rate, causing pressure changes in the differential chamber and resulting in poor differential performance. Utility Model Content

[0007] In view of this, the purpose of this utility model is to provide a pressure-stabilizing differential valve, a hydraulic system and a loader. The structural design of the pressure-stabilizing differential valve can solve the problems in the prior art that cannot guarantee the hydraulic oil pressure and the differential lock opening pressure range are inconsistent, and that the hydraulic oil pressure in the differential chamber drops rapidly when other oil passages are opened.

[0008] To achieve the above objectives, the present invention adopts the following technical solution:

[0009] The first aspect provides a pressure-stabilizing differential valve, including a valve body, on which an oil inlet P1, an oil outlet A1, and an oil outlet A2 are provided; the valve body contains a pressure reducing valve and a solenoid valve connected in sequence.

[0010] The P1 inlet is connected to the oil inlet circuit, the solenoid valve is connected to the A2 outlet, and the A2 outlet is connected to the control port of the differential lock. The hydraulic oil passes through the P1 inlet, the pressure reducing valve, the solenoid valve, and the A2 outlet in sequence to enter the control port of the differential lock to achieve differential speed. The pressure reducing valve is also connected to the A1 outlet through an oil circuit.

[0011] Preferably, an accumulator is also connected between the pressure reducing valve and the solenoid valve.

[0012] Preferably, a check valve is installed before the accumulator and the A1 oil outlet and after the pressure reducing valve to prevent hydraulic oil backflow.

[0013] Preferably, the accumulator is a gas-loaded accumulator.

[0014] Preferably, the valve body is also provided with a B2 oil outlet and a T return oil outlet; the T return oil outlet is connected to the oil tank.

[0015] Preferably, the B2 oil outlet is connected between the solenoid valve and the A2 oil outlet via an oil circuit, and a pressure sensor is connected to the B2 oil outlet.

[0016] Preferably, the pressure reducing valve is a pilot-operated pressure reducing valve, with its drain port connected to the T return port; its inlet port connected to the P1 inlet port; and its outlet port connected to a check valve.

[0017] Preferably, the solenoid valve is a two-position three-way solenoid valve, including a first port, a second port, and a third port; a check valve is connected to the first port, and an accumulator is set between the check valve and the first port; the second port is connected to the A2 oil outlet through an oil circuit; and the third port is connected to the T return oil port through an oil circuit.

[0018] The second aspect provides a hydraulic system including the aforementioned pressure-stabilizing differential valve.

[0019] The third aspect provides a loader, including the aforementioned hydraulic system.

[0020] Compared with the prior art, the advantages and positive effects of this utility model are:

[0021] This utility model's pressure-stabilizing differential valve features a pressure-reducing valve installed before the solenoid valve. This valve adjusts the hydraulic oil pressure to match the differential lock's opening pressure range, preventing damage to the axle or a loose differential lock that hinders differential operation. The pressure-reducing valve connects to outlets A1 and A2, enabling other functions alongside differential operation. An accumulator is installed between the pressure-reducing valve and the solenoid valve, releasing energy promptly when outlet A1 is opened. This prevents a rapid drop in hydraulic oil pressure within the differential chamber, where the pressure replenishment rate is lower than the reduction rate, leading to pressure fluctuations within the differential chamber and poor differential performance. Attached Figure Description

[0022] The accompanying drawings, which form part of this specification, are used to provide a further understanding of this utility model. The illustrative embodiments of this utility model and their descriptions are used to explain this utility model and do not constitute an improper limitation of this utility model.

[0023] Figure 1 This is a schematic diagram of the structure of a differential valve in the prior art;

[0024] Figure 2 This is a structural schematic diagram of the pressure-stabilizing differential valve of embodiment 1, 2, or 3 of this utility model;

[0025] In the picture:

[0026] 1. Pressure reducing valve; 2. Accumulator; 3. Solenoid valve; 4. Rear axle; 5. Front axle. Detailed Implementation

[0027] It should be noted that the following detailed description is illustrative and intended to provide further explanation of the present invention. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains.

[0028] The present invention will now be described in detail with reference to the accompanying drawings.

[0029] Example 1

[0030] This embodiment discloses a pressure-stabilizing differential valve, such as... Figure 2 As shown, the valve body includes an oil inlet (P1), an oil outlet (A1), and an oil outlet (A2); the valve body contains a pressure reducing valve 1 and a solenoid valve 3 connected in sequence.

[0031] In this embodiment, as Figure 2 As shown, the P1 oil inlet of the valve body is connected to the oil inlet circuit, the solenoid valve 3 is connected to the A2 oil outlet, and the A2 oil outlet is connected to the control oil port of the differential lock of the front axle 5 and the rear axle 4; the hydraulic oil passes through the P1 oil inlet, the pressure reducing valve 1, the solenoid valve 3, and the A2 oil outlet in sequence, and enters the control oil port of the differential lock to realize differential.

[0032] In this embodiment, hydraulic oil enters the valve body through the P1 inlet and is reduced in pressure by the pressure reducing valve 1. This allows the hydraulic oil pressure to be adjusted to the range required by the differential lock, ensuring that the hydraulic oil pressure and the differential lock opening pressure range are consistent. This prevents damage to the axle or a loose differential lock, which could hinder normal differential operation. This improves the applicability and stability of the pressure-stabilized differential valve.

[0033] In this embodiment, as Figure 2As shown, in addition to being connected to the solenoid valve 3, the pressure reducing valve 1 is also connected to the oil outlet of A1 through an oil circuit. The hydraulic oil after pressure reduction can be sent to the differential lock through the solenoid valve 3, or it can be used as an oil source to supply other oil circuits through the oil outlet of A1. For example, it can be connected to the multi-way valve pilot control oil circuit as the multi-way valve pilot control oil source, or connected to the parking pressure oil circuit as the parking pressure oil source, or connected to the flow amplification valve pilot control oil circuit as the flow amplification valve pilot control oil source.

[0034] In this embodiment, by adding an A1 oil outlet, the stabilized hydraulic oil can be used for other functions, increasing the versatility of the pressure-stabilized differential valve.

[0035] like Figure 2 As shown, an accumulator 2 is also connected between the pressure reducing valve 1 and the solenoid valve 3. The hydraulic oil after pressure reduction valve 1 is stabilized passes through the accumulator 2, and then enters the differential lock through the solenoid valve 3 and the A2 oil outlet, or the hydraulic oil after pressure reduction valve 1 is stabilized passes through the A1 oil outlet to enter other oil circuits.

[0036] In this embodiment, the accumulator 2 can convert the energy in the system into compressed energy or potential energy and store it. When the oil outlet of A1 is opened, the accumulator 2 can replenish the pressure of the hydraulic oil passing through the solenoid valve 3 and the oil outlet of A2, so as to avoid the pressure change in the differential chamber of the differential lock, resulting in poor differential effect.

[0037] Understandably, accumulator 2 can release or absorb energy as needed by the system to ensure normal system pressure, thereby ensuring stable pressure output at oil outlets A1 and A2.

[0038] like Figure 2 As shown, in this embodiment, a check valve is also provided before the accumulator 2 and the oil outlet of A1, and after the pressure reducing valve 1, to prevent hydraulic oil backflow.

[0039] like Figure 2 As shown, in this embodiment, the valve body is also provided with an oil outlet B2 and an oil return port T; wherein, an oil circuit is led out between the solenoid valve 3 and the oil outlet A2 to connect to the oil outlet B2, and a pressure sensor is connected to the oil outlet B2 to detect the oil circuit pressure between the differential lock and the solenoid valve 3, so as to facilitate the pressure reducing valve 1 to adjust the hydraulic oil pressure of the oil inlet circuit.

[0040] like Figure 2 As shown, solenoid valve 3 is also connected to the T return port, which is connected to the oil tank; the hydraulic oil flowing back from the differential lock returns to the oil tank via solenoid valve 3 and the T return port.

[0041] Understandably, by integrating the pressure reducing valve 1, accumulator 2, and solenoid valve 3 into a single valve body, the system volume is optimized, friction losses are reduced, and energy utilization is improved.

[0042] In this embodiment, as Figure 2 As shown, pressure reducing valve 1 is a pilot-operated pressure reducing valve. The drain port of pressure reducing valve 1 is connected to the return port T. The inlet port of pressure reducing valve 1 is connected to the inlet port P1. The outlet port of pressure reducing valve 1 is connected to a check valve. The check valve is connected to the outlet ports A1 and A2 respectively. Accumulator 2 and solenoid valve 3 are located between the check valve and the outlet port A2.

[0043] In this embodiment, as Figure 2 As shown, solenoid valve 3 is a two-position three-way solenoid valve, including a first port, a second port, and a third port. The first port is the pressure port; the outlet of pressure reducing valve 1 is connected to a check valve, and the flow splits into two paths after the check valve. One path connects to the first port of solenoid valve 3 via accumulator 2. The second port is the working port, connected to the A2 outlet via an oil circuit to supply hydraulic oil to the differential lock. The third port is the return port, connected to the T return port of the valve body via an oil circuit.

[0044] When the first port and the second port are connected, the hydraulic oil after pressure reduction by pressure reducing valve 1 enters the differential lock through the check valve, accumulator, first port, second port, and A2 outlet.

[0045] When the third port is connected to the second port, hydraulic oil flows out from the differential lock and flows into the oil tank through the second port, the third port, and the T return port.

[0046] In this embodiment, the accumulator 2 can be a gas-loaded accumulator, which has stable performance.

[0047] Working principle:

[0048] When the loader encounters slippage on one side of the wheel, the first and second ports of the solenoid valve 3 are connected to open the pressure channel. Hydraulic oil enters the valve body through the P1 inlet and is reduced to the range required by the differential lock by the pressure reducing valve 1. This ensures that the hydraulic oil pressure is consistent with the differential lock opening pressure range, thus avoiding damage to the axle or loose differential lock, which would make it difficult to achieve differential operation normally.

[0049] The hydraulic oil, after being depressurized by the pressure reducing valve 1, passes through the accumulator 2 for energy storage, and then enters the differential lock through the first port, the second port, and the A2 oil outlet of the solenoid valve 3. The differential lock will lock the differential housing and the half shaft into a whole, forcing the wheels on both sides to rotate synchronously, ensuring that the power is effectively transmitted to the wheels with traction, and achieving rigid power distribution to improve the vehicle's ability to get out of trouble.

[0050] When the A1 outlet also opens, the depressurized hydraulic oil flows through the A1 outlet into other oil circuits. Accumulator 2 simultaneously replenishes energy to prevent a rapid drop in hydraulic oil pressure in the differential lock's differential chamber after the A1 outlet opens. Since the pressure replenishment rate is lower than the depressurization rate, this would cause pressure changes within the differential chamber, resulting in poor differential performance.

[0051] When it is necessary to release the differential, the pressure channel is closed by connecting the second and third ports of solenoid valve 3. The hydraulic oil flows from the differential lock through the A2 outlet, the second port, the third port, and the T return port back to the oil tank with lower pressure. At this time, the differential housing and the half shaft are released from the locked state, and the two ends of the wheel can move freely.

[0052] Example 2

[0053] This embodiment discloses a hydraulic system including a pressure-stabilizing differential valve as disclosed in Embodiment 1.

[0054] Example 3

[0055] This embodiment discloses a loader, including a hydraulic system disclosed in embodiment 2. When the loader encounters slippage on one side of the wheel, the first port and the second port of the solenoid valve 3 are connected to open the pressure channel, allowing hydraulic oil to enter the valve body through the P1 oil inlet. The pressure is then reduced to the range required by the differential lock by the pressure reducing valve 1, ensuring that the hydraulic oil pressure and the differential lock opening pressure range are consistent, thus avoiding damage to the axle or a loose differential lock that makes it difficult to achieve differential operation normally.

[0056] When the A1 outlet also opens, the depressurized hydraulic oil flows through the A1 outlet into other oil circuits. Accumulator 2 simultaneously replenishes energy to prevent a rapid drop in hydraulic oil pressure in the differential lock's differential chamber after the A1 outlet opens. Since the pressure replenishment rate is lower than the depressurization rate, this would cause pressure changes within the differential chamber, resulting in poor differential performance.

[0057] When it is necessary to release the differential, the pressure channel is closed by connecting the second and third ports of solenoid valve 3. The hydraulic oil flows from the differential lock through the A2 outlet, the second port, the third port, and the T return port back to the oil tank with lower pressure. At this time, the differential housing and the half shaft are released from the locked state, and the two ends of the wheel can move freely.

[0058] Although the specific embodiments of the present utility model have been described above in conjunction with the accompanying drawings, this is not intended to limit the scope of protection of the present utility model. Those skilled in the art should understand that various modifications or variations that can be made by those skilled in the art without creative effort based on the technical solution of the present utility model are still within the scope of protection of the present utility model.

Claims

1. A pressure-stabilized differential valve characterized by comprising: The valve body includes a P1 oil inlet, an A1 oil outlet, and an A2 oil outlet; the valve body also includes a pressure reducing valve and a solenoid valve connected in sequence. The P1 oil inlet is connected to the oil inlet circuit, the solenoid valve is connected to the A2 oil outlet, and the A2 oil outlet is connected to the control oil port of the differential lock. The hydraulic oil passes through the P1 oil inlet, the pressure reducing valve, the solenoid valve, and the A2 oil outlet in sequence to enter the control oil port of the differential lock to achieve differential speed. The pressure reducing valve is also connected to the A1 oil outlet through an oil circuit.

2. A pressure-stable differential valve according to claim 1, characterized in that An accumulator is also connected between the pressure reducing valve and the solenoid valve.

3. A pressure-stable differential valve according to claim 2, characterized in that A check valve is installed before the accumulator and the A1 oil outlet, and after the pressure reducing valve, to prevent hydraulic oil backflow.

4. A pressure-stable differential valve according to claim 3, characterized in that The accumulator is a gas-loaded accumulator.

5. A pressure-stable differential valve according to claim 4, characterized in that The valve body is also provided with a B2 oil outlet and a T oil return port; the T oil return port is connected to the oil tank.

6. A pressure-stable differential valve according to claim 5, characterized in that The B2 oil outlet is connected between the solenoid valve and the A2 oil outlet via an oil circuit, and a pressure sensor is connected to the B2 oil outlet.

7. A pressure-stable differential valve according to claim 6, characterized in that The pressure reducing valve is a pilot-operated pressure reducing valve, the drain port of the pressure reducing valve is connected to the T return port; the inlet port of the pressure reducing valve is connected to the P1 inlet port, and the outlet port of the pressure reducing valve is connected to a check valve.

8. A pressure-stabilizing differential valve as described in claim 7, characterized in that, The solenoid valve is a two-position three-way solenoid valve, including a first port, a second port, and a third port; the check valve is connected to the first port, and the accumulator is located between the check valve and the first port; the second port is connected to the A2 oil outlet through an oil circuit; and the third port is connected to the T return oil port through an oil circuit.

9. A hydraulic system characterized by, Includes a pressure-stabilizing differential valve as described in any one of claims 1-8.

10. A loader characterized by Includes a hydraulic system as described in claim 9.

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