Modular integrated hydraulic system device

Abstract

This application relates to the field of hydraulic system technology, specifically a modular integrated hydraulic system device, comprising: a motor, which is driven to a piston pump with a differential pressure valve via a bell housing and coupling assembly; a shock absorber strip disposed at the bottom of the motor; a valve block, which is connected to the pressure port of the piston pump with the differential pressure valve, and the outlet end of the valve block is provided with a tubular check valve; the valve block integrates a stacked high-pressure filter, a proportional relief valve, and a stacked relief valve; and a control oil pipe, which is connected between the valve block and the piston pump with the differential pressure valve via a connector to form a pressure feedback channel. The valve block of this application integrates stacked high-pressure filter, proportional relief valve, and stacked relief valve elements, with a compact structure, reduced pipeline connections, reduced system space occupation, and facilitates installation, commissioning, and maintenance, while reducing leakage risk and pressure loss.

Description

Technical Field

[0001] This application relates to the field of hydraulic system technology, and in particular to a modular integrated hydraulic system device. Background Technology

[0002] Hydraulic systems, as widely used power transmission and control devices in modern industrial equipment, are extensively applied in fields such as engineering machinery, automated production lines, and aerospace. Traditional hydraulic systems typically include major components such as motor-driven piston pumps, pressure regulating valve assemblies, filters, and check valves.

[0003] However, in practical applications, existing hydraulic systems still have the following shortcomings: the hydraulic components are scattered, the pipeline connections are complex, resulting in a large system structure, a large space occupation, and increased difficulty and cost in installation, commissioning, and maintenance. This project aims to develop a modular integrated hydraulic system device to solve these problems. Utility Model Content

[0004] In view of at least one of the above technical problems, this application provides a modular integrated hydraulic system device, which adopts the following technical solution to solve the above problems.

[0005] According to one aspect of this application, a modular integrated hydraulic system device is provided, comprising:

[0006] The motor is connected to a plunger pump with a differential pressure valve via a bell housing and coupling assembly.

[0007] Shock-absorbing strips are installed at the bottom of the motor;

[0008] A valve block is connected to the pressure port of the plunger pump with a differential pressure valve, and a tubular check valve is provided at the outlet end of the valve block; the valve block integrates a stacked high-pressure filter, a proportional relief valve, and a stacked relief valve.

[0009] The control oil pipe is connected to the valve block and the plunger pump with differential pressure valve through a connector, forming a pressure feedback channel.

[0010] Preferably, the stacked high-pressure filter is connected to the oil inlet end of the valve block to achieve preliminary purification of the hydraulic oil.

[0011] Preferably, the superimposed relief valve is fixed to the valve block via a threaded interface. It is located after the proportional relief valve and is used to set the maximum protection pressure of the system. When the system pressure exceeds the preset safety threshold, overload protection is performed.

[0012] Preferably, the proportional relief valve is fixed to the valve block via a threaded interface and connected to the pressure output end of the plunger pump with a differential pressure valve.

[0013] Preferably, the plunger pump with differential pressure valve is linked to the proportional relief valve to dynamically balance the system pressure by adjusting the valve core opening.

[0014] Preferably, two shock-absorbing strips are arranged parallel to each other along the length of the motor base to reduce mechanical vibration during power transmission.

[0015] Preferably, the valve core of the tubular check valve faces the hydraulic actuator to prevent hydraulic oil backflow.

[0016] Preferably, the motor, the plunger pump with differential pressure valve, the valve block, the proportional relief valve, and the superimposed relief valve are arranged in a straight line in sequence.

[0017] This application has the following technical effects:

[0018] The valve block of this application integrates stacked high-pressure filter, proportional relief valve and stacked relief valve elements. It has a compact structure, reduces pipeline connections, reduces system space occupation, facilitates installation, commissioning and maintenance, and reduces leakage risk and pressure loss. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a perspective view of this application;

[0021] Figure 2 This is another perspective view in this application;

[0022] Figure 3 This is a top view of this application;

[0023] Figure 4 This is the front view in this application.

[0024] Figure label:

[0025] 1. Motor; 2. Bell housing and coupling assembly; 3. Vibration damping strip; 4. Piston pump with differential pressure valve; 5. Control oil pipe; 6. Stacked high-pressure filter; 7. Proportional relief valve; 8. Stacked relief valve; 9. Connector; 10. Valve block; 11. Pipe-type check valve. Detailed Implementation

[0026] Please see Figures 1-4It should be understood that the structures, proportions, sizes, etc., illustrated in the accompanying drawings are merely for illustrative purposes to aid those skilled in the art and to facilitate understanding. They are not intended to limit the scope of the invention and therefore have no substantial technical significance. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effectiveness and objectives of the invention, should still fall within the scope of the technical content disclosed herein. Furthermore, the technical terms used in this specification are merely for clarity and not intended to limit the scope of the invention. Changes or adjustments to their relative relationships, without substantially altering the technical content, should also be considered within the scope of the invention's implementation.

[0027] The specific embodiments of this application will now be described in detail with reference to the accompanying drawings. Numerous specific details are set forth in the following description to provide a thorough understanding of this application.

[0028] In this embodiment of the application, as Figures 1-4 As shown, a modular integrated hydraulic system device is provided, comprising:

[0029] Motor 1, which is connected to a plunger pump with differential pressure valve 4 via a bell housing and coupling assembly 2;

[0030] Shock-absorbing strip 3 is located at the bottom of motor 1;

[0031] Valve block 10 is connected to the pressure port of the plunger pump with differential pressure valve 4, and valve block 10 outlet end is provided with tubular check valve 11; valve block 10 integrates stacked high pressure filter 6, proportional relief valve 7 and stacked relief valve 8.

[0032] The control oil pipe 5 is connected to the valve block 10 and the plunger pump with differential pressure valve 4 via the connector 9, forming a pressure feedback channel.

[0033] It should be noted that this application achieves multi-stage pressure regulation and modular integration, offering advantages such as high efficiency, stability, and ease of maintenance. Through the coordinated operation of various components, hydraulic oil of different pressure levels can be provided to the hydraulic actuator to meet diverse operational needs.

[0034] Specifically, motor 1 serves as the power source, and it is connected to the plunger pump with differential pressure valve 4 via a bell housing and coupling assembly 2. The bell housing and coupling assembly 2 connects the output shaft of motor 1 to the input shaft of the plunger pump, ensuring smooth power transmission. A common NL coupling can be used, offering connection stability and ensuring synchronous rotation of the two shafts during power transmission, reducing vibration and noise. In practical applications, the appropriate model of the bell housing and coupling assembly 2 can be selected based on the power of motor 1 and the specifications of the plunger pump. For example, a 0.75-1.5kW motor 1 can be paired with a specific specification of bell housing and coupling, while a 2.2-4kW motor 1 can be paired with another specification, and so on.

[0035] Vibration damping strips 3 are installed at the bottom of motor 1, with two strips arranged parallel to each other along the length of the motor 1 base. Taking the common DSM-type rubber vibration damping strip specifically designed for motor 1 as an example, its excellent elasticity effectively absorbs the vibration energy generated during motor 1 operation, reducing mechanical vibration during power transmission. Simultaneously, it is wear-resistant, ensuring that it maintains good vibration damping performance even after prolonged use. Its temperature and oil resistance allow it to operate normally in various environments, and its performance will not be affected by environmental changes or corrosion from the motor 1's lubricating oil.

[0036] Valve block 10 is connected to the pressure port of the plunger pump with differential pressure valve 4, playing a key role in modular integration. It integrates a stacked high-pressure filter 6, a proportional relief valve 7, and a stacked relief valve 8. The stacked high-pressure filter 6 is connected to the oil inlet of valve block 10, performing preliminary purification of the hydraulic oil output from the plunger pump with differential pressure valve 4, removing impurities and ensuring the cleanliness of the hydraulic oil in the system, thus extending the service life of other hydraulic components. The proportional relief valve 7 is fixed to valve block 10 via a threaded interface and connected to the pressure output of the plunger pump with differential pressure valve 4. It can adjust the valve core opening according to the input electrical signal, thereby precisely controlling the pressure of the hydraulic system. The stacked relief valve 8, located after the proportional relief valve 7, is also fixed to valve block 10 via a threaded interface. It is used to set the maximum protection pressure of the system. When the system pressure exceeds the preset safety threshold, it provides overload protection to prevent damage to the system due to excessive pressure. The outlet end of the valve block 10 is equipped with a tubular check valve 11, whose valve core faces the hydraulic actuator. This effectively prevents hydraulic oil backflow and ensures that the hydraulic oil flows in the specified direction, providing stable oil supply to the hydraulic actuator.

[0037] The control oil pipe 5 is connected to the valve block 10 and the plunger pump with differential pressure valve 4 via the connector 9, forming a pressure feedback channel. The plunger pump with differential pressure valve 4 can adjust its own working state according to the pressure signal fed back by the control oil pipe 5. For example, when the system pressure changes, the plunger pump with differential pressure valve 4 can be linked with the proportional relief valve 7 through this feedback channel to dynamically balance the system pressure.

[0038] In one embodiment of this application, the superimposed high-pressure filter 6 is connected to the oil inlet end of the valve block 10 to achieve preliminary purification of the hydraulic oil.

[0039] It should be noted that the stacked high-pressure filter 6 achieves preliminary purification of hydraulic oil, improves the cleanliness of hydraulic oil, thereby protecting other precision hydraulic components in the system, extending the service life of the entire hydraulic system, and reducing the probability of component wear and failure caused by impurities.

[0040] Specifically, the stacked high-pressure filter 6 has an internal filter element that can intercept impurities such as metal particles and dust in the hydraulic oil. For example, the filter element uses high-precision metal mesh or fiber material, which can filter out impurities at the micron level. It is connected to the oil inlet of the valve block 10 through a standard interface to ensure a tight connection and smooth oil flow. Before the hydraulic oil output from the plunger pump with differential pressure valve 4 enters the valve block 10, it first flows through the stacked high-pressure filter 6. Through the filtering action of the filter element, impurities are intercepted on the surface of the filter element. The cleaned hydraulic oil then enters the valve block 10 to participate in the subsequent pressure regulation and delivery process.

[0041] In one embodiment of this application, the superimposed relief valve 8 is fixed to the valve block 10 via a threaded interface. It is located after the proportional relief valve 7 and is used to set the maximum protection pressure of the system. When the system pressure exceeds the preset safety threshold, overload protection is performed.

[0042] It should be noted that the stacked relief valve 8 provides the hydraulic system with the highest pressure protection function, effectively preventing damage to components caused by abnormal pressure rise, and ensuring the operational safety and stability of the entire hydraulic system.

[0043] Specifically, the stacked relief valve 8 is tightly fixed to the valve block 10 via a threaded interface, located after the proportional relief valve 7. Its working principle is based on the balance between hydraulic oil pressure and spring force. When the system pressure is normal, the force of the hydraulic oil acting on the relief valve spool is less than the spring's preload, the spool is closed, and the hydraulic oil flows normally through the valve block 10 to supply oil to the actuator. When the system pressure exceeds the preset safety threshold of the stacked relief valve 8 due to abnormal conditions such as a sudden increase in load or a malfunction of the proportional relief valve 7, the force of the hydraulic oil acting on the spool exceeds the spring preload, the spool opens, and some hydraulic oil overflows back to the oil tank through the relief valve, thereby reducing the system pressure and achieving overload protection. For example, if the preset maximum system protection pressure is 20 MPa, when the system pressure rises to 20.5 MPa, the stacked relief valve 8 opens to overflow until the system pressure drops to near the set value.

[0044] In one embodiment of this application, the proportional relief valve 7 is fixed to the valve block 10 via a threaded interface and connected to the pressure output end of the plunger pump with differential pressure valve 4.

[0045] It should be noted that the proportional relief valve 7 can achieve precise regulation of hydraulic system pressure. Through electrical signal control, the system pressure can be flexibly adjusted according to actual working needs, which improves the control accuracy and response speed of the hydraulic system and meets the diverse pressure requirements under different working conditions.

[0046] Specifically, the proportional relief valve 7 is securely fixed to the valve block 10 via a threaded interface and connected to the pressure output end of the plunger pump with differential pressure valve 4. It integrates an electromagnetic control unit and a valve core adjustment mechanism. When the control system sends an electrical signal, the electromagnetic coil generates a magnetic field, attracting the valve core to move. By changing the magnitude of the electrical signal, the valve core opening can be precisely controlled. For example, when a higher system pressure is required, increasing the electrical signal decreases the valve core opening, reducing the overflow of hydraulic oil and increasing the system pressure; conversely, decreasing the electrical signal increases the valve core opening, increasing the overflow of hydraulic oil and decreasing the system pressure. This precise pressure regulation method allows the hydraulic system to quickly and accurately adapt to the pressure requirements of different working scenarios.

[0047] In one embodiment of this application, the plunger pump is linked with the differential pressure valve 4 and the proportional relief valve 7 to dynamically balance the system pressure by adjusting the valve core opening.

[0048] It should be noted that the linkage between the piston pump with differential pressure valve 4 and proportional relief valve 7 achieves dynamic balance of system pressure, enabling the hydraulic system to maintain stable pressure output under different loads and operating conditions, improving the stability and reliability of the system, and ensuring the smooth operation of the hydraulic actuator.

[0049] Specifically, when the system pressure changes, the control oil pipe 5 feeds back the pressure signal at valve block 10 to the piston pump with differential pressure valve 4. For example, when the system pressure decreases, the piston pump with differential pressure valve 4 detects the pressure change and adjusts the piston pump's displacement through its internal control mechanism, increasing the output hydraulic oil flow and thus raising the system pressure. Simultaneously, the proportional relief valve 7 also receives the pressure change signal and, according to a preset control strategy, adjusts the overflow hydraulic oil flow by changing the valve core opening, further assisting in stabilizing the system pressure. Conversely, when the system pressure increases, both work together to reduce the piston pump's displacement, increase the relief valve's overflow flow, and lower the system pressure, thereby achieving dynamic balance regulation of the system pressure.

[0050] In one embodiment of this application, two shock-absorbing strips 3 are arranged parallel to each other along the length of the motor 1 base to reduce mechanical vibration during power transmission.

[0051] It should be noted that the two shock-absorbing strips 3, which are parallel to each other along the length of the base of the motor 1, effectively reduce the transmission of mechanical vibration generated by the motor 1 during operation to the surrounding structure, reduce the noise during operation, improve the overall stability of the equipment, and also help extend the service life of the motor 1 and other related components.

[0052] Specifically, when motor 1 operates at high speed, it generates significant vibration. The damping strip 3 absorbs most of the vibration energy through its elastic deformation, thereby greatly reducing the vibration transmitted to the frame and other structures on which motor 1 is mounted. This reduces structural fatigue and component wear caused by vibration.

[0053] In one embodiment of this application, the valve core of the tubular check valve 11 faces the hydraulic actuator to prevent hydraulic oil backflow.

[0054] It should be noted that the pipe-type check valve 11 prevents hydraulic oil backflow, ensures the uniqueness of the oil flow direction in the hydraulic system, guarantees that the hydraulic actuator can work normally according to the design requirements, and avoids malfunction of the actuator or system failure caused by oil backflow.

[0055] Specifically, the tubular check valve 11 is installed at the outlet end of the valve block 10, with its valve core facing the hydraulic actuator. The tubular check valve 11 employs a specific valve core and seat structure. When hydraulic oil flows normally from the valve block 10 to the hydraulic actuator, the pressure of the hydraulic oil pushes the valve core, causing it to overcome spring force or other resistance, opening the passage and allowing the oil to flow smoothly. However, when abnormal conditions occur in the hydraulic system, such as system pressure fluctuations at the moment the pump stops working, or the inertia of the actuator causing the oil to flow back, the force of the backflowing hydraulic oil acting on the valve core causes it to tightly adhere to the valve seat, closing the passage and preventing oil backflow. For example, when the hydraulic system stops working, without the tubular check valve 11, the oil in the hydraulic actuator might flow back to the valve block 10 due to gravity or residual pressure in the pipeline, affecting the normal operation of the system upon restart. The presence of the tubular check valve 11 effectively prevents this from happening.

[0056] In one embodiment of this application, the motor 1, the plunger pump with differential pressure valve 4, the valve block 10, the proportional relief valve 7, and the superimposed relief valve 8 are distributed in a straight line in sequence.

[0057] It should be noted that the motor 1, the plunger pump with differential pressure valve 4, the valve block 10, the proportional relief valve 7, and the stacked relief valve 8 are arranged in a straight line. This layout makes the entire hydraulic system compact and neat, which is convenient for installation, commissioning and maintenance. At the same time, it reduces the length of pipeline connections and reduces pressure loss and leakage risk.

[0058] Specifically, during equipment installation, following a linear layout, components such as motor 1, plunger pump with differential pressure valve 4, and valve block 10 are installed and fixed sequentially. For example, motor 1 is first installed on a pre-designed frame foundation, and then the plunger pump with differential pressure valve 4 is connected via a bell housing and coupling assembly 2, ensuring it is concentric with the output shaft of motor 1. Next, valve block 10 is installed near the pressure port of plunger pump with differential pressure valve 4, and a secure connection is ensured using standard connection methods such as bolts. Proportional relief valve 7 and stacked relief valve 8 are integrated and installed on the corresponding interface positions on valve block 10 according to design requirements. This linear layout allows for a more direct flow path of hydraulic oil in the system, reducing pressure loss caused by pipe bends and excessive length. Simultaneously, during equipment maintenance, it facilitates the inspection, repair, and replacement of various components by operators, improving maintenance efficiency.

[0059] The above are merely preferred embodiments of this application and do not constitute any limitation on this application. Any person skilled in the art can make many possible variations and modifications to the technical solution of this application, or modify it into equivalent embodiments, without departing from the scope of the technical solution of this application. Therefore, all equivalent changes made based on the shape, structure, and principle of this application without departing from the content of the technical solution of this application should be covered within the protection scope of this application.

Claims

1. A modular integrated hydraulic system apparatus, characterized by, include: The motor (1) is connected to the plunger pump with differential pressure valve (4) via a bell housing and coupling assembly (2). Shock-absorbing strip (3), which is disposed at the bottom of the motor (1); The valve block (10) is connected to the pressure port of the plunger pump with differential pressure valve (4), and the outlet end of the valve block (10) is provided with a tubular check valve (11); the valve block (10) is integrated with a stacked high pressure filter (6), a proportional relief valve (7) and a stacked relief valve (8). The control oil pipe (5) is connected to the valve block (10) and the plunger pump with differential pressure valve (4) through the connector (9) to form a pressure feedback channel.

2. A modular integrated hydraulic system apparatus as claimed in claim 1, wherein: The superimposed high-pressure filter (6) is connected to the oil inlet end of the valve block (10) to achieve preliminary purification of hydraulic oil.

3. The modular integrated hydraulic system apparatus of claim 1, wherein: The superimposed relief valve (8) is fixed to the valve block (10) through a threaded interface. It is located after the proportional relief valve (7) and is used to set the maximum protection pressure of the system. When the system pressure exceeds the preset safety threshold, it performs overload protection.

4. The modular integrated hydraulic system apparatus of claim 1, wherein: The proportional relief valve (7) is fixed to the valve block (10) through a threaded interface and connected to the pressure output end of the plunger pump with differential pressure valve (4).

5. The modular integrated hydraulic system apparatus of claim 1, wherein: The plunger pump with differential pressure valve (4) is linked with the proportional relief valve (7) to dynamically balance the system pressure by adjusting the valve core opening.

6. The modular integrated hydraulic system apparatus of claim 1, wherein: Two shock-absorbing strips (3) are arranged parallel to each other along the length of the motor (1) base to reduce mechanical vibration during power transmission.

7. The modular integrated hydraulic system apparatus of claim 1, wherein: The valve core of the tubular check valve (11) faces the hydraulic actuator to prevent hydraulic oil backflow.

8. The modular integrated hydraulic system apparatus of claim 1, wherein: The motor (1), the plunger pump with differential pressure valve (4), the valve block (10), the proportional relief valve (7), and the superimposed relief valve (8) are distributed in a straight line in sequence.

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