Energy-saving and noise-reducing type hydraulic control one-way valve

Abstract

The utility model relates to an energy -conserving and noise reduction type liquid control check valve, including valve body, central cavity, the central cavity is along the axial and is equipped with central cavity in the valve body, and the central cavity is multiple cylindrical passages of unequal diameter and is respectively spring cavity, valve element cavity from top to bottom of the central cavity, communication cavity and piston cavity, and the main oil way export P2 is opened along the valve element cavity radial, and the main oil way import P1 is opened along the communication cavity radial, and the control oil way K is opened along the piston cavity radial, and the spring cavity is linked with the main oil way export P2, the buffer spring is installed in the spring cavity, and the buffer spring lower extreme is unshakable with the unloading valve element, and the unloading valve element can be up and down and is inserted in the inner hole of main valve element, and the main valve element sets up in the valve element cavity and the main valve element lower end jams the valve element cavity lower end through -hole, and the piston cavity is movably arranged control piston, and the control piston upside is unshakable unloading piston. The utility model reaches the beneficial effect is: effectively avoids the oil liquid impact under pressure and noise, reduces the pressure loss.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic control device technology, and in particular to an energy-saving and noise-reducing hydraulic control check valve. Background Technology

[0002] Currently, check valves are commonly used in hydraulic machinery, petrochemicals, metallurgy, mining, and construction. A check valve is a type of valve that allows fluid flowing through it to flow only from the inlet to the outlet, and prevents the outlet fluid from flowing back. Due to its anti-backflow characteristic, check valves are used in various hydraulic tools and hydraulic equipment.

[0003] Traditional check valves suffer from problems such as high energy loss, significant noise pollution, and limited functionality. There are many factors contributing to these problems. First, ordinary main valve cores typically use conical seals to meet sealing requirements, and poor design of flow-through components leads to high pressure loss. Second, there are no unloading valve cores. When the valve port opens in the reverse direction, the pressurized oil in the high-pressure chamber is suddenly released, resulting in hydraulic shock and valve core vibration. This further leads to noise generated by the interaction between the oil and the flow-through components.

[0004] Therefore, based on the shortcomings of the existing device, the inventors made further improvements to overcome the aforementioned problems. Utility Model Content

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide an energy-saving and noise-reducing hydraulic check valve with forward and reverse opening functions, low control pressure when opening in reverse, low noise during the opening process, and low energy loss after opening.

[0006] The purpose of this utility model is achieved through the following technical solution: an energy-saving and noise-reducing hydraulic control check valve, including a valve body, a central cavity, a main valve core, and an unloading valve core; The valve body has a central cavity along the axial direction. The central cavity is a plurality of cylindrical channels with different diameters. From top to bottom, the central cavity consists of a spring cavity, a valve core cavity, a connecting cavity, and a piston cavity. A main oil passage outlet P2 is opened radially along the valve core cavity, a main oil passage inlet P1 is opened radially along the connecting cavity, and a control oil passage K is opened radially along the piston cavity. The spring cavity is connected to the main oil passage outlet P2. The central cavity is equipped with a buffer spring, an unloading valve core, a main valve core, an unloading piston, and a control piston, arranged from top to bottom. The buffer spring is installed in the spring cavity, and its lower end is fixedly connected to the unloading valve core. The unloading valve core is movably inserted into the inner hole of the main valve core. The main valve core is located in the valve core cavity, and its lower end blocks the lower end of the valve core cavity. The control piston is movably installed in the piston cavity. The upper side of the control piston is vertically fixed to the unloading piston, and the upper end of the unloading piston is directly opposite the lower end of the unloading valve core. During forward flow, high-pressure oil enters the connecting chamber through the main oil passage inlet P1, thereby opening the main valve core. The high-pressure oil then enters the valve core chamber and finally flows out through the main oil passage outlet P2. During reverse flow, control oil enters the piston chamber through the control oil passage K and pushes the control piston and unloading piston upward. The unloading piston pushes the unloading valve core upward, and after the high-pressure oil flows and releases pressure, the unloading piston continues to push upward and then lifts the main valve core, realizing slow communication between the connecting chamber and the valve core chamber, avoiding pressure shock and noise.

[0007] As a preferred technical solution of this application, the upper and lower surfaces of the valve body are respectively secured to the valve body by a valve cover with bolts and sealed.

[0008] As a preferred technical solution of this application, the valve cover is an upper valve cover and a lower valve cover; the upper and lower valve covers are fitted and sealed with the upper and lower surfaces of the valve body, and an O-ring is provided on the inner side to prevent the hydraulic oil inside the valve body from leaking to the outside.

[0009] As a preferred technical solution of this application, the main oil passage inlet P1 and the main oil passage outlet P2 in the valve body are basically equal in size, and an external oil passage L is also provided along the radial direction of the piston cavity. The external oil passage L is basically equal in size to the control oil passage K, and the main oil passage size is much larger than the external oil passage L and the control oil passage K.

[0010] As a preferred technical solution of this application, the upper end of the main valve core is a cylindrical tube, the lower end of which is smaller than the upper end and the bottom end is rounded. The main valve core has stepped channels from top to bottom. The unloading valve core is adapted to be inserted into the stepped channels. The diameter of the valve core cavity is larger than that of the connecting cavity, that is, there is a stepped platform between the valve core cavity and the connecting cavity. The rounded corner of the lower end of the main valve core abuts against the stepped platform.

[0011] As a preferred technical solution of this application, the upper end of the unloading valve core is conical, and its lower end is a cylindrical small end that is adapted to be vertically inserted into the cylindrical inner hole of the main valve core. The upper end dimensions of the unloading valve core and the unloading piston are similar, and the unloading valve core moves axially under the action of the unloading piston.

[0012] As a preferred technical solution of this application, the piston chamber at the large end of the unloading piston is connected to the external leakage oil passage L, which can timely discharge the internal leakage oil to the hydraulic oil tank through the external leakage oil passage L.

[0013] As a preferred technical solution of this application, the control piston is cylindrical and is installed axially in the piston cavity. The lower cavity of the control piston is connected to the control oil passage K. The upper end of the control piston is fixedly connected to the large end of the unloading piston. When high-pressure oil is introduced into the control oil passage K, the control piston moves upward. When the control oil passage is depressurized, the control piston returns to its initial position under its own weight.

[0014] This utility model has the following advantages: (1) First, the main valve core in this scheme adopts an inverted round valve core, which optimizes the fluid dynamics performance. When the check valve is working, the pressure loss of the flow through the flow component is low, which reduces the eddy current and throttling loss when the oil passes through the valve port. This reduces energy loss and increases the life of the check valve, achieving energy saving and high efficiency. In addition, this scheme is designed with an external leakage oil passage L and a control oil passage K. The control oil passage K controls the action of the piston, and the independent external leakage oil passage design ensures the reliability of the control piston action, avoids control failure caused by internal leakage, and enables the valve to work stably under harsh working conditions. (2) The unloading valve core is used in this scheme. The unloading valve core reduces the control pressure of opening the main valve core, which reduces the conversion rate of hydraulic energy into heat energy in the hydraulic system. At the same time, the unloading valve core can effectively reduce the pressure shock and noise caused by the sudden release of pressurized oil in the high-pressure closed chamber during the reverse opening process. This not only increases the life of the check valve, but also plays a role in protecting the environment. (3) In summary, the one-way valve in this scheme has the function of bidirectional fluid control and can realize bidirectional flow control of the fluid according to the specific working conditions. This not only improves the adaptability of the device under different working conditions, but also saves the additional cost required for reverse control. Attached Figure Description

[0015] Figure 1 This is a first-view structural schematic diagram of the present invention; Figure 2 This is a first-view structural schematic diagram of the main valve core of this utility model; In the diagram: 1-nut, 2-bolt, 3-lower valve cover, 4-O-ring seal, 5-control piston, 6-unloading piston, 7-valve body, 8-main valve core, 9-unloading valve core, 10-buffer spring, 11-spring chamber, 12-valve core chamber, 13-connecting chamber, 14-piston chamber. Detailed Implementation

[0016] The present invention will be further described below with reference to the accompanying drawings, but the scope of protection of the present invention is not limited to the following description.

[0017] It should be noted that the orientation or positional relationship indicated by terms such as "left" and "right" is based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship that the product of this invention is usually placed in during use, or the orientation or positional relationship that is commonly understood by those skilled in the art. Such terms are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0018] It should be noted that, unless otherwise specified, the embodiments and features and technical solutions in the present invention can be combined with each other.

[0019] Therefore, based on the above issues, please refer to Figure 1 This utility model proposes an energy-saving and noise-reducing hydraulic control check valve to solve the problem.

[0020] See Figures 1-2 The present implementation scheme proposes an energy-saving and noise-reducing hydraulic control check valve, which includes a valve body 7, a central cavity opened inside the valve body 7, a main valve core 8, an unloading valve core 9, an unloading piston 6, and a control piston 5. Among them, see Figure 1 The valve body 7 has a central cavity running from top to bottom along the central axis. The central cavity is formed by multiple cylindrical channels of different diameters running vertically. The central cavity is further divided into a spring cavity 11, a valve core cavity 12, a connecting cavity 13, and a piston cavity 14. The four cavities are connected vertically. A main oil passage outlet P2 is opened radially along the side of the valve core cavity 12, a main oil passage inlet P1 is opened radially along the side of the connecting cavity 13, and a control oil passage K is opened radially along the side of the piston cavity 14. The spring cavity 11 is also connected to the main oil passage outlet P2. Among them, see Figure 1 The central cavity is equipped with a buffer spring 10, an unloading valve core 9, a main valve core 8, an unloading piston 6, and a control piston 5, arranged sequentially from top to bottom. The buffer spring 10 is located in the spring cavity 11. The upper end of the buffer spring 10 is connected to the inner wall of the central cavity, and the lower end of the buffer spring 10 is connected to the unloading valve core 9. The unloading valve core 9 is movably inserted into the inner hole of the main valve core 8. The main valve core 8 is located in the valve core cavity 12, and the lower end of the main valve core 8 blocks the lower end opening of the valve core cavity 12. Among them, see Figure 1 A control piston 5 is movably disposed in the piston chamber 14, and an unloading piston 6 is vertically fixed to the upper side of the control piston 5; the uppermost end of the unloading piston 6 faces the unloading valve core 9 (that is, this end is opposite to the lower end of the unloading valve core 9), and is used to push the unloading valve core 9 upward. When in use, when the main oil circuit flows in the forward direction, high-pressure oil enters the main oil passage inlet P1 and acts on the outer surface of the main valve core 8, thereby overcoming the spring force, hydraulic force, and the gravity of the main valve core 8 to open the main valve core 8. The high-pressure oil rushes in and flows out through the main oil passage outlet P2. When the main oil circuit needs to flow in the reverse direction, when high-pressure oil is introduced into the control oil passage K, the control piston 5 moves upward, and the unloading piston 6 moves upward and pushes open the unloading valve core 9. At this time, the high-pressure oil in the main oil circuit is released after flowing, avoiding high-pressure impact. Then the unloading piston 6 continues to push upward and then pushes up the main valve core 8, realizing the slow communication between the front and rear chambers of the main valve core 8, while avoiding the pressure impact and noise problems caused by the sudden release of pressurized oil.

[0021] In existing check valves, traditional check valves suffer from high energy loss, significant noise pollution, and limited functionality. Without an unloading valve core 9, when the valve opens in the reverse direction, the pressurized oil in the high-pressure chamber is suddenly released, causing hydraulic shock and valve core vibration. This further leads to noise generated by the interaction between the oil and the flow components, which propagates in the pipeline, causing hydraulic shock and vibration of the pipeline and components. The oil then generates strong noise, significantly interfering with the entire operation. Therefore, this solution designs an energy-saving and noise-reducing hydraulic control check valve to address these issues. This solution introduces an unloading valve core 9, reducing the control pressure for opening the main valve core 8. Furthermore, during the reverse opening process, the cooperation between the control piston 5 and the unloading piston 6 with the unloading valve core 9 effectively reduces the pressure shock and noise caused by the sudden release of pressurized oil in the high-pressure closed chamber.

[0022] In this embodiment, see Figure 1 For valve body 7, the uppermost and lowermost ends of valve body 7 are connected by a valve cover, which is connected to the upper and lower surfaces of valve body 7 via an upper valve cover and a lower valve cover 3. The upper and lower valve covers 3 are connected to the corresponding surfaces of valve body 7 by multiple bolts 2 and nuts 1. O-rings 4 are provided on the inner side of the upper valve cover and the upper surface of valve body 7, and on the lower valve cover 3 and the lower surface of valve body 7, respectively. The O-rings 4 seal the valve body 7 and prevent leakage of hydraulic oil inside valve body 7. Valve body 7 has three basic oil circuits: main oil circuit, control oil circuit, and external leakage oil circuit. The main oil circuit includes a main oil passage inlet P1 and a main oil passage outlet P2, and the main oil circuit can achieve bidirectional movement. The center of valve body 7 The cavity has multiple cylindrical channels of varying diameters along its axial direction. From top to bottom, a buffer spring 10, an unloading valve core 9, a main valve core 8, an unloading piston 6, and a control piston 5 are installed sequentially. The four radial branch oil passages are, from top to bottom, the main oil passage outlet P2, the main oil passage inlet P1, the external leakage oil passage L, and the control oil passage K. In the radial cylindrical oil passages in the valve body 7, the two main oil passages are approximately equal in size, and the external leakage oil passage L and the control oil passage K are approximately equal in size. Furthermore, the two main oil passages are much larger than the external leakage oil passage L and the control oil passage K. The radial main oil passage at the top of the valve body 7 (i.e., the main oil passage outlet P2) is connected to the buffer spring 10 cavity in the valve body 7, allowing the oil to flow freely between the two cavities.

[0023] In this embodiment, see Figure 1For the control piston 5 and the unloading piston 6; the control piston 5 and the unloading piston 6 are located in the lower part of the central cavity, i.e., in the piston cavity 14. The entire control piston 5 is located in the piston cavity 14, and the upper end face of the control piston 5 is connected to the unloading piston 6. The upper end (i.e., the small end) of the unloading piston 6 passes through the through hole between the piston cavity 14 and the connecting cavity 13, so that the small end of the unloading piston 6 is inserted into the connecting cavity 13. The lower end of the control piston 5 communicates with the control oil passage K. The upper end of the unloading piston 6 is the small end, and the size of the small end of the unloading piston 6 is equivalent to the size of the small end of the unloading valve core 9. The small end of the unloading piston 6 is directly opposite the unloading valve core 9. The unloading piston 6 is configured such that the cavity at its large end (i.e., piston cavity 14) is connected to the external leakage oil circuit, thereby timely discharging the internal leakage oil to the hydraulic oil tank and further preventing the control piston 5 from failing to work due to internal leakage. The power for the unloading piston 6 to move up and down comes from the hydraulic pressure transmitted by the control oil passage K. When high-pressure oil is introduced into the control oil passage K, the oil acts on the control piston 5, thereby controlling the piston 5 to move upward, together with the unloading piston 6 fixed to it, thus pushing the unloading valve core 9 open. After the unloading valve core 9 is pushed open by the unloading piston 6, the high-pressure oil in the main oil circuit flows and releases pressure.

[0024] It should be noted that the internal leakage of oil can cause the pressure to rise continuously. When the internal leakage is severe or the pressure in the closed cavity accumulates to a sufficiently high level, the control oil pressure may not be able to push the control piston 5 upward, causing the hydraulic check valve to fail to open and become completely ineffective. Therefore, an external leakage oil passage is set up to allow the oil to flow back to the oil tank without resistance, thus avoiding the failure problem in this solution.

[0025] It should also be noted that the lower end of the control piston 5 is connected to the control oil circuit, and the upper end is fixedly connected to the unloading piston 6. When high-pressure oil is introduced into the control oil circuit, the control piston 5 moves upward; when the control oil circuit is depressurized, the control piston 5 returns to its initial position under its own weight. In this embodiment, see Figures 1-2For the main valve core 8, the upper end of the main valve core 8 is a cylindrical tube, and its lower end is smaller than the upper end and has a rounded corner. Generally, the flow-through components of the main valve core 88 have three structures: spherical, chamfered, and rounded. However, in this design, the lower end of the main valve core 88 has a rounded corner, which can minimize energy loss when subjected to oil impact at this point. Moreover, this smooth streamlined design avoids dead zones and rapid pressure changes. The main valve core 8 is adapted to be installed in the valve core cavity 12. The diameter of the valve core cavity 12 is larger than that of the connecting cavity 13, and there is a stepped platform between the valve core cavity 12 and the connecting cavity 13. The bottom of the main valve core 8 is rounded and abuts against the stepped platform. Inside the main valve core 8, there are stepped channels from top to bottom. The stepped channels have three channels of different diameters from top to bottom. Between every two channels, there is a stepped platform. The unloading valve core 9 is fitted into the stepped channel. The upper end of the unloading valve core 9 is conical, and its lower end is cylindrical and is fitted vertically into the bottommost channel of the main valve core 8 (i.e., in the cylindrical inner hole). The conical end face of the unloading valve core 9 abuts against the stepped surface of the stepped channel in the main valve core 8. The unloading valve core 9 can move axially under the action of the unloading piston 6.

[0026] Traditional check valves suffer from high energy loss, significant noise pollution, and limited functionality. The sudden release of pressurized oil in the high-pressure chamber generates hydraulic shock and valve core vibration, further leading to noise generation due to the interaction between the oil and flow components. Therefore, this solution utilizes a buffer spring 10 in the central chamber, which works in conjunction with the unloading valve core 9 and the main valve core 8. The main valve core 8 employs an inverted circular design, optimizing fluid dynamics, reducing energy loss, increasing the lifespan of the check valve, and achieving energy efficiency. Furthermore, the main valve core 8 in this solution exhibits both active and passive axial movement. When the main oil flows in the forward direction, the high-pressure oil acts on the outer surface of the main valve core 8, overcoming the spring force and hydraulic shock. The main valve core 8 is opened by force and gravity. When the main oil circuit flows in reverse, the unloading piston 6 moves upward and pushes open the unloading valve core 9. At this time, the high-pressure oil in the main oil circuit is released after flowing, and the unloading piston 6 continues to move, further pushing up the main valve core 8. This achieves slow communication between the front and rear chambers of the main valve core 8, while avoiding pressure shock and noise problems caused by the sudden release of pressurized oil, and further reducing the oil pressure in the control oil circuit. In addition, this scheme also sets up an external leakage oil circuit, which directly connects the large end cavity of the unloading piston 6 to the oil tank, ensuring that the internal leakage oil can be discharged from the external leakage oil passage L in a timely manner, completely eliminating the risk of control oil circuit failure due to pressure accumulation, and greatly improving the reliability and stability of control.

[0027] Finally, it should be noted that the above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Although the utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. An energy-saving and noise-reducing hydraulic control check valve, characterized in that: Includes valve body (7), central cavity, main valve core (8), and unloading valve core (9); The valve body (7) has a central cavity along the axial direction. The central cavity is a plurality of cylindrical channels with different diameters. From top to bottom, the central cavity consists of a spring cavity (11), a valve core cavity (12), a connecting cavity (13), and a piston cavity (14). A main oil passage outlet P2 is opened radially along the valve core cavity (12), a main oil passage inlet P1 is opened radially along the connecting cavity (13), and a control oil passage K is opened radially along the piston cavity (14). The spring cavity (11) is connected to the main oil passage outlet P2. The central cavity is installed from top to bottom as follows: buffer spring (10), unloading valve core (9), main valve core (8), unloading piston (6) and control piston (5); buffer spring (10) is installed in spring cavity (11), the lower end of buffer spring (10) is fixedly connected to unloading valve core (9), unloading valve core (9) is movably inserted into the inner hole of main valve core (8), main valve core (8) is set in valve core cavity (12) and the lower end of main valve core (8) blocks the lower end of valve core cavity (12), control piston (5) is movably set in piston cavity (14), unloading piston (6) is vertically fixedly connected to the upper side of control piston (5), and the upper end of unloading piston (6) is directly opposite to the lower end of unloading valve core (9); When flowing in the forward direction, high-pressure oil enters the connecting chamber (13) through the main oil passage inlet P1, thereby opening the main valve core (8), and the high-pressure oil enters the valve core chamber (12), and finally flows out through the main oil passage outlet P2; when flowing in the reverse direction, control oil enters the piston chamber (14) through the control oil passage K and pushes the control piston (5) and the unloading piston (6) upward. The unloading piston (6) pushes the unloading valve core (9) upward. After the high-pressure oil flows and is depressurized, the unloading piston (6) continues to push upward and then pushes up the main valve core (8), realizing the slow communication between the connecting chamber (13) and the valve core chamber (12) to avoid pressure shock and noise.

2. The energy-saving and noise-reducing hydraulic control check valve according to claim 1, characterized in that: The main oil passage inlet P1 and the main oil passage outlet P2 in the valve body (7) are basically equal in size, and an external oil passage L is also provided radially along the piston cavity (14). The external oil passage L is basically equal in size to the control oil passage K, and the main oil passage size is much larger than the external oil passage L and the control oil passage K.

3. The energy-saving and noise-reducing hydraulic control check valve according to claim 1, characterized in that: The upper end of the main valve core (8) is a cylindrical tube, the lower end of which is smaller than the upper end and the bottom end is rounded. The main valve core (8) has a stepped channel from top to bottom inside. The unloading valve core (9) is fitted into the stepped channel. The diameter of the valve core cavity (12) is larger than that of the connecting cavity (13), that is, there is a stepped platform between the valve core cavity (12) and the connecting cavity (13). The rounded corner of the lower end of the main valve core (8) abuts against the stepped platform.

4. The energy-saving and noise-reducing hydraulic control check valve according to claim 1, characterized in that: The upper end of the unloading valve core (9) is conical, and the lower end is cylindrical and is vertically inserted into the cylindrical inner hole of the main valve core (8). The conical end face of the unloading valve core (9) abuts against the stepped surface of the stepped channel in the main valve core (8). The upper dimensions of the unloading valve core (9) and the unloading piston (6) are similar. The unloading valve core (9) moves axially under the action of the unloading piston (6).

5. The energy-saving and noise-reducing hydraulic control check valve according to claim 4, characterized in that: The piston chamber (14) at the large end of the unloading piston (6) is connected to the external drain oil passage L, which can discharge the internal drain oil to the hydraulic oil tank in a timely manner through the external drain oil passage L.

6. The energy-saving and noise-reducing hydraulic control check valve according to claim 1, characterized in that: The control piston (5) is cylindrical and is installed axially in the piston chamber (14). The lower cavity of the control piston (5) is connected to the control oil passage K. The upper end of the control piston (5) is fixedly connected to the large end of the unloading piston (6). When high-pressure oil is introduced into the control oil passage K, the control piston (5) moves upward. When the control oil passage is depressurized, the control piston (5) returns to its initial position under its own weight.

7. The energy-saving and noise-reducing hydraulic control check valve according to claim 2, characterized in that: The upper and lower surfaces of the valve body (7) are respectively secured by a valve cover with bolts (2) to seal the valve body (7).

8. The energy-saving and noise-reducing hydraulic control check valve according to claim 7, characterized in that: The valve covers are an upper valve cover and a lower valve cover (3); the upper and lower valve covers (3) are fitted and sealed to the upper and lower surfaces of the valve body (7), and an O-ring seal (4) is provided on the inner side of the valve cover to prevent the hydraulic oil inside the valve body (7) from leaking to the outside.

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