A large flow spool valve for a hydraulic assist system

Abstract

The utility model provides a large flow structure valve core for hydraulic pressure booster system, including push rod, push rod and high pressure valve seat are connected, one end of push rod and steel ball are top -connected, push rod and steel ball are adjacent one end of bushing and have pilot valve seat, pilot valve seat and pilot valve seat spring support seat are riveted pressure, pilot valve seat spring support seat is connected with pilot cover through pilot valve return spring, can make pilot valve seat return spring avoid high pressure liquid's flow field area, thereby make pilot valve return spring no longer be side impact of high pressure oil, in addition, through the mounting structure of push rod spring seat, spring pad and snap spring, make push rod return spring avoid high pressure liquid's flow field area, make valve core structure more stable, satisfy different liquid quantity demand.

Description

Technical Field

[0001] This utility model relates to hydraulic power assist systems, and more particularly to a high-flow-rate structural valve core for hydraulic power assist systems. Background Technology

[0002] Currently, there are many types of hydraulic power steering systems. The principle of power steering is hydraulic drive. Some are purely mechanical hydraulic transmission systems that use changes in the size of the piston chamber to generate different power steering ratios and achieve the power steering function. However, the amount of fluid in the piston chamber is limited by the piston stroke and thrust, and cannot continuously provide an unlimited amount of fluid.

[0003] For hydraulic power steering systems in light commercial vehicles requiring more than 25 ml of brake fluid, existing valve cores pose certain risks. The main issue is that the pilot valve seat return spring and push rod return spring are located within the flow channel of the high-pressure brake fluid. When the primary and secondary cone seals open, the high-pressure fluid impacts the springs within the flow channel, causing them to break or deform abnormally. This leads to valve core system sealing failure, thereby affecting the vehicle's braking safety.

[0004] For applications requiring high flow rates, space constraints prevent the spring wire diameter from being increased to withstand the impact of liquid. Therefore, it is necessary to improve the valve core structure to meet the demands of high flow rates. Summary of the Invention

[0005] The purpose of this invention is to address the shortcomings of the prior art by providing a high-flow-rate valve core for hydraulic power assist systems, which is suitable for applications with high load flow rates.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] This utility model provides a high-flow structural valve core for a hydraulic power assist system, including a push rod, which is sleeved with a high-pressure valve seat. One end of the push rod is in contact with a steel ball, and a pilot valve seat is sleeved at the end of the push rod adjacent to the steel ball. The pilot valve seat is riveted to a pilot valve seat spring support, and the pilot valve seat spring support is connected to a pilot cover through a pilot valve return spring.

[0008] Furthermore, the pilot cover contains a steel ball seat, one end of which is in contact with the pilot cover via a steel ball return spring, and the other end of which is press-fitted to the steel ball.

[0009] Furthermore, a push rod spring seat is sleeved at the end of the push rod that is separate from the steel ball, and the push rod spring seat abuts against the high-pressure valve seat.

[0010] Furthermore, the push rod is provided with a retaining spring, which contacts the push rod spring pad.

[0011] Furthermore, the push rod spring pad is installed with the push rod spring seat via a push rod return spring.

[0012] Furthermore, the high-pressure valve seat is riveted to the pilot cover, and the pilot cover is provided with a first oil inlet.

[0013] Furthermore, the pilot valve spring support seat is provided with a second oil inlet.

[0014] Furthermore, the high-pressure valve seat is fitted with an outer sleeve.

[0015] Furthermore, a first sealing ring is fitted onto the high-pressure valve seat, and a second sealing ring is fitted onto the outer sleeve.

[0016] The beneficial effects of this utility model are as follows: it enables the pilot valve seat return spring to avoid the flow field area of ​​high-pressure liquid, thereby preventing the pilot valve return spring from being impacted by the side of high-pressure oil. In addition, through the installation structure of the push rod spring seat, spring washer and snap ring, the push rod return spring avoids the flow field area of ​​high-pressure liquid, making the valve core structure more stable and able to resist long-term liquid impact (continuous increase in liquid volume) without being affected by the structure. Attached Figure Description

[0017] Figure 1 A schematic diagram of a high-flow-rate structural valve core for a hydraulic power assist system;

[0018] Figure 2 This is a schematic diagram of the pilot valve seat spring support.

[0019] Figure 3 This is a schematic diagram of the pilot valve seat. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the present utility model and are not intended to limit the scope of the present utility model.

[0021] Please see Figure 1 A high-flow-rate structural valve core for a hydraulic power assist system includes a push rod 1, which is sleeved with a high-pressure valve seat 2. One end of the push rod 1 is abutted against a steel ball 3. A pilot valve seat 4 is sleeved at the end of the push rod 1 adjacent to the steel ball 3. The pilot valve seat 4 is riveted to a pilot valve seat spring support 5. The pilot valve seat spring support 5 is connected to a pilot cover 7 through a pilot valve return spring 6.

[0022] Please see Figure 2 and Figure 3In one specific embodiment, the pilot valve seat 4 is sleeved on the surface of one end of the push rod 1, and the outer surface of the pilot valve seat 4 is provided with a protruding ring. The protruding ring of the pilot valve seat 4 abuts against the high pressure valve seat 2. That is, a part of the outer surface of the pilot valve seat 4 is sleeved with the high pressure valve seat 2, and the other part of the pilot valve seat 4 extends out of the high pressure valve seat 2 and abuts against the steel ball 3.

[0023] In addition, one end of the push rod 1 passes through the pilot valve seat 4, and the protruding end of the push rod 1 abuts against the steel ball 3. In the initial state, there is a certain gap between the protruding end of the push rod 1 and the steel ball 3 to ensure the normal sealing of the steel ball 3. During the movement, the protruding end of the push rod will push the steel ball 3 open, forming a high-pressure flow channel area.

[0024] In one specific embodiment, the steel ball 3 is separated from the conical opening of the pilot valve seat 4 to form a primary sealing conical opening, through which high-pressure oil flows into the inner cavity of the high-pressure valve seat 2.

[0025] As push rod 1 continues to push steel ball 3 to move along the Y-axis, high-pressure brake fluid enters the inner cavity of the high-pressure valve seat and together with push rod 1, pushes pilot valve seat 4 to move along the Y-axis, causing the arc surface of pilot valve seat 4 to separate from the sealing cone of high-pressure valve seat 2 to form a secondary sealing cone. At the same time, high-pressure oil flows into the inner cavity of the high-pressure valve seat from the secondary sealing cone.

[0026] The pilot cover 7 contains a ball bearing seat 8. One end of the ball bearing seat 8 is abutted against the pilot cover 7 via a ball bearing return spring 9, and the other end of the ball bearing seat 8 is press-fitted to the ball bearing 3. In a specific embodiment, the ball bearing return spring 9 is installed along the Y-axis; the pilot valve return spring 6 is in the X-axis direction, forming a certain angle with the X-axis.

[0027] That is, the pilot valve return spring 6 is a conical spring (tower spring) with a large opening at the top and a small opening at the bottom, so that the pilot valve seat 4 is more stable under the spring return force during its back-and-forth movement.

[0028] The push rod 7 is sleeved with a push rod spring seat 10 at the end that is separate from the steel ball 3, and the push rod spring seat 10 abuts against the high pressure valve seat 2.

[0029] The push rod 7 is provided with a retaining spring 11, which is in contact with the push rod spring pad 12.

[0030] The push rod spring pad 12 is installed with the push rod spring seat 10 via the push rod return spring 13.

[0031] The high-pressure valve seat 2 is riveted to the pilot cover 7, and the pilot cover 7 is provided with a first oil inlet 1301.

[0032] The pilot valve spring support 5 is provided with a second oil inlet 1302.

[0033] In one specific embodiment, the second oil inlet 1302 is provided on the pilot valve spring support seat 5, and the outer wall of the pilot valve spring support seat 5 is provided with a protrusion. The protrusion on the pilot valve spring support seat 5 is used to install the pilot valve return spring 6, and the second oil inlet 1302 is installed directly below the protrusion of the pilot valve spring support seat 5, and the first oil inlet 1301 is installed obliquely below the second oil inlet 1302, that is, the first oil inlet 1301 is provided below the protrusion of the pilot valve spring support seat 5. Since both the first oil inlet 1301 and the second oil inlet 1302 avoid the pilot valve seat return spring 6, the impact and damage to the pilot valve seat return spring 6 when a large flow of hydraulic fluid enters the valve core are avoided.

[0034] The high-pressure valve seat 2 is fitted with an outer sleeve 14.

[0035] In one specific embodiment, the high-pressure valve seat 2 is installed inside the outer sleeve 14, and the installation of the high-pressure valve seat 2 is supported by the steps inside the outer sleeve 14.

[0036] In one specific embodiment, the outer casing 14 is provided with a high-pressure liquid outlet 1401 on its wall.

[0037] A first sealing ring 15 is fitted onto the high-pressure valve seat 2, and a second sealing ring 16 is fitted onto the outer sleeve 14; the first sealing ring 15 and the second sealing ring 16 seal the high-pressure liquid storage area.

[0038] To facilitate understanding of the above-mentioned technical solution of this utility model, the following is a detailed description of the operation method of this utility model in actual process:

[0039] Push rod 1 applies a thrust F. The top of push rod 1 first contacts the steel ball 3 and pushes the steel ball 3 to separate the steel ball 3 from the pilot valve seat 4, that is, it opens the first-stage conical seal. High-pressure oil flows into the pilot cover cavity from the first oil inlet 1301 and then into the high-pressure valve seat 2 cavity from the second oil inlet 1302.

[0040] As the force F of push rod 1 continues to increase, the displacement of push rod 1 continues to move forward, and the snap ring 11 abuts against the push rod spring pad 12, thereby compressing the push rod return spring 13. As push rod 1 continues to be subjected to force, it pushes the pilot valve seat 4, causing the arc surface of the pilot valve seat 4 to separate from the high-pressure valve 2, that is, the secondary cone seal is opened, and the high-pressure oil flows along the inner cavity of the high-pressure valve seat 2 to the high-pressure liquid outlet on the outer sleeve 14, thereby causing the high-pressure oil to flow to the load or to the drive device.

[0041] During this process, the pilot valve seat return spring and push rod return spring in the high-pressure flow channel are both protected from the impact of the liquid, thus improving the reliability of the product.

[0042] The embodiments described above merely illustrate the implementation of this utility model, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of this utility model patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this utility model, and these all fall within the protection scope of this utility model. Therefore, the protection scope of this utility model patent should be defined by the appended claims.

Claims

1. A high-flow-rate structural valve core for a hydraulic power assist system, characterized in that: Includes a push rod (1), which is sleeved with a high-pressure valve seat (2). One end of the push rod (1) is abutted against a steel ball (3). A pilot valve seat (4) is sleeved on the end of the push rod (1) adjacent to the steel ball (3). The pilot valve seat (4) is riveted to a pilot valve seat spring support (5). The pilot valve seat spring support (5) is connected to a pilot cover (7) through a pilot valve reset spring (6).

2. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 1, characterized in that: The pilot cover (7) contains a steel ball seat (8). One end of the steel ball seat (8) is in contact with the pilot cover (7) through a steel ball return spring (9), and the other end of the steel ball seat (8) is press-fitted to the steel ball (3).

3. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 2, characterized in that: The push rod (1) is connected to a push rod spring seat (10) at the end that is separate from the steel ball (3), and the push rod spring seat (10) abuts against the high pressure valve seat (2).

4. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 3, characterized in that: The push rod (1) is provided with a retaining ring (11), which is in contact with the push rod spring pad (12).

5. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 4, characterized in that: The push rod spring pad (12) is installed with the push rod spring seat (10) via the push rod return spring (13).

6. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 2, characterized in that: The high-pressure valve seat (2) is riveted to the pilot cover (7), and the pilot cover (7) is provided with a first oil inlet (1301).

7. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 1, characterized in that: The pilot valve seat spring support (5) is provided with a second oil inlet (1302).

8. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 1, characterized in that: The high-pressure valve seat (2) is fitted with an outer sleeve (14).

9. A high-flow-rate structural valve core for a hydraulic power assist system according to claim 8, characterized in that: The high-pressure valve seat (2) is fitted with a first sealing ring (15), and the outer sleeve (14) is fitted with a second sealing ring (16).

Images