Flow control valve, hydraulic control system and vehicle

Abstract

The utility model relates to a kind of flow control valve, hydraulic control system and vehicle, wherein, flow control valve includes valve body and valve core, the valve core is arranged in the valve body, the valve body is provided with fluid inlet and fluid outlet, the valve core is provided with throttle port, the throttle port is connected with the fluid inlet and the fluid outlet to form throttle passage. The utility model can be in electromagnet when electromagnet circuit failure or proportional solenoid is damaged, so that hydraulic system can be operated for a short time, vehicle can be operated for a short time to repair point to maintain, improve the use convenience of user, and improve the safety performance of vehicle.

Description

Technical Field

[0001] This utility model relates to the field of valves, and in particular to a flow control valve, a hydraulic control system, and a vehicle. Background Technology

[0002] With the development of hydraulic control systems, flow control valves are widely used in automotive transmissions and industrial equipment. Flow control valves are often equipped with electromagnets to regulate the flow of the hydraulic system.

[0003] There are two failure modes in the use of flow control valves: one is the failure of the electromagnet circuit, and the other is the damage of the proportional electromagnet. In both failure modes of flow control valves, the existing hydraulic control system is in a disconnected state, which makes the hydraulic control system unusable and the vehicle unable to move. Utility Model Content

[0004] To solve the above-mentioned technical problems, this utility model provides a flow control valve, a hydraulic control system, and a vehicle, enabling the hydraulic system to be used and the vehicle to move.

[0005] On the one hand, this utility model provides a flow control valve, including a valve body and a valve core. The valve core is disposed in the valve body. The valve body is provided with a fluid inlet and a fluid outlet. The valve core is provided with a throttling orifice. The throttling orifice connects the fluid inlet and the fluid outlet to form a throttling path.

[0006] In one embodiment of this utility model, a flow cavity is formed between the valve core and the valve body, and the fluid inlet, the flow cavity, the throttling port and the fluid outlet are sequentially connected to form the throttling flow path.

[0007] In one embodiment of this utility model, a flow port is formed between the valve core and the valve body, and the fluid inlet, the flow cavity, the flow port and the fluid outlet are sequentially connected to form an adjustment passage.

[0008] In one embodiment of the present invention, the valve body has a cavity, the valve core is located in the cavity, the outer edge of the valve core is recessed radially to form a groove, and the flow cavity is formed between the groove and the side wall of the cavity.

[0009] In one embodiment of this utility model, the flow control valve further includes an electromagnet module, the electromagnet module having an output end, the output end being connected to the valve core, the output end driving the valve core to slide along the axial direction of the cavity within the cavity to adjust the opening and closing of the flow port and to adjust the opening size of the flow port.

[0010] In one embodiment of the present invention, the flow control valve further includes an elastic element located within the cavity. Along the axial direction of the cavity, the output end, the valve core, and the elastic element are connected in sequence, with the elastic element abutting between the valve core and the bottom wall of the cavity.

[0011] In one embodiment of this utility model, the elastic element is a spring, the valve body extends toward the bottom wall of the cavity to form a positioning post, and the spring is sleeved on the positioning post.

[0012] In one embodiment of the present invention, a first sliding portion is formed on one side of the groove along the axial direction of the valve core, and a second sliding portion is formed on the other side of the groove. The first sliding portion and the second sliding portion are slidably disposed within the cavity.

[0013] On the other hand, a hydraulic control system is provided, including a flow control valve.

[0014] On the other hand, a vehicle is provided, including a hydraulic control system.

[0015] The above-mentioned technical solution of this utility model has the following advantages compared with the prior art: The flow control valve described in this utility model, when the electromagnet circuit fails or the proportional electromagnet is damaged, keeps the fluid inlet and outlet in a normally open state due to the throttling of the flow path. This allows the fluid outlet to still provide a small amount of hydraulic oil to the downstream end for use. In other words, when the electromagnet circuit fails or the proportional electromagnet is damaged, the hydraulic control system can operate for a short time, and the vehicle can be driven to a repair shop for maintenance in a short time, improving user convenience and vehicle safety performance. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 This is a first cross-sectional view of the flow control valve of this utility model (flow port closed). Figure 2 This is a second sectional view of the flow control valve of this utility model (flow port open); Figure 3 This is the third sectional view (maximum flow port) of the flow control valve of this utility model. Figure 4This is a schematic diagram of the valve core of the flow control valve of this utility model; Figure 5 This is a three-dimensional structural diagram of the flow control valve of this utility model; Figure 6 This is a schematic diagram of the flow control valve of this utility model, showing the opening amount of the flow port. Figure 7 This is a diagram showing the relationship between the control current and flow rate of the electromagnet module of the flow control valve of this utility model. Figure 8 This is a diagram showing the relationship between the control current and the opening amount of the electromagnet module of the flow control valve of this utility model.

[0018] Explanation of reference numerals in the instruction manual: 1. Valve body; 2. Valve core; 3. Fluid inlet; 4. Fluid outlet; 5. Throttling port; 6. Throttling path; 7. Flow chamber; 8. Flow port; 9. Adjustment path; 10. Cavity; 11. Groove; 12. Electromagnet module; 13. Output end; 14. Elastic element; 15. Positioning pin; 16. First sliding part; 17. Second sliding part; 18. Intermediate connecting part; 19. Sealing groove; 20. Sealing ring; 21. Abutment end; 22. Side wall; 23. Bottom wall. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0020] Example 1 The flow control valve of this utility model includes an electromagnet module 12, a valve body 1, a valve core 2, and an elastic element 14.

[0021] like Figure 1As shown, a cylindrical cavity 10 is provided inside the valve body 1. The outer edge of the valve core 2 is cylindrical, and the valve core 2 is disposed inside the valve body 1. The axis of the valve core 2 coincides with the axis of the cavity 10, and the valve core 2 is slidably disposed within the cavity 10 along the axial direction of the cavity 10. Specifically, the valve core 2 includes a first sliding portion 16, an intermediate connecting portion 18, and a second sliding portion 17 arranged sequentially. Preferably, the first sliding portion 16, the intermediate connecting portion 18, and the second sliding portion 17 are integrally formed. Both the first sliding portion 16 and the second sliding portion 17 are slidably disposed within the cavity 10 to facilitate the sliding of the valve core 2 within the cavity 10. The intermediate connecting portion 18 is recessed radially inward to form a groove 11. Since the valve core 2 is disposed within the cavity 10, the groove 11 and the circumferential sidewall 22 of the cavity 10 together form a flow cavity 7, which is used for the flow of hydraulic oil.

[0022] like Figure 2 and Figure 3 As shown, the valve body 1 is provided with a fluid inlet 3 and a fluid outlet 4. The second sliding part 17 of the valve core 2 forms a flow port 8 between itself and the valve body 1. The fluid inlet 3, the flow chamber 7, the flow port 8, and the fluid outlet 4 are sequentially connected to form a regulating passage 9, as shown. Figure 2 and Figure 3 The solid arrow path is shown.

[0023] like Figure 2 As shown, the electromagnet module 12 has an output end 13, which is cylindrical and can slide along its axial direction. The axis of the output end 13, the axis of the valve body 1, and the axis of the valve core 2 coincide. The output end 13 is connected to the first sliding part 16 of the valve core 2, so as to drive the valve core 2 to slide within the cavity 10 of the valve body 1 via the output end 13. Figure 1 As shown, when the output end 13 of the electromagnet module 12 drives the valve core 2 to slide to the leftmost end within the cavity 10, the flow port 8 between the second sliding part 17 and the valve body 1 closes. At this time, the regulating passage 9 formed by the sequential connection of the fluid inlet 3, the flow cavity 7, the flow port 8, and the fluid outlet 4 is in a closed state, and hydraulic oil cannot flow out through the fluid outlet 4. When the output end 13 of the electromagnet module 12 drives the valve core 2 to slide to the right within the cavity 10, causing the flow port 8 between the second sliding part 17 and the valve body 1 to open, as... Figure 2 As shown, the regulating passage 9, formed by the sequential connection of fluid inlet 3, flow chamber 7, flow port 8, and fluid outlet 4, is in the open state. Hydraulic oil can flow through flow port 8 to fluid outlet 4, and thus allow hydraulic oil to flow out through fluid outlet 4. When the output end 13 continues to drive the valve core 2 to slide to the right within the cavity 10, causing flow port 8 to fully open, the hydraulic oil flow rate through flow port 8 is at its maximum. Figure 3As shown, the hydraulic flow rate at this time is 3.5 L / min - 4 L / min, preferably, the maximum hydraulic flow rate is 3.8 L / min. Therefore, the output terminal 13 of the electromagnet module 12 can drive the valve core 2 to slide, thereby adjusting the opening and closing of the flow port 8 between the second sliding part 17 and the valve body 1 and the opening size of the flow port 8 through the sliding valve core 2, so as to adjust the opening and closing of the hydraulic oil at the fluid outlet 4 and the flow rate, thereby realizing the proportional regulation of the hydraulic oil flow rate, that is, the flow rate at the fluid outlet 4 can be adjusted between 0 L / min and 3.8 L / min. Among them, controlling the opening and closing of the hydraulic oil and the flow rate by the load demand can reduce the overall hydraulic oil flow rate and reduce the power consumption of the oil pump.

[0024] like Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, the valve core 2 is provided with a throttling orifice 5. The fluid inlet 3, the flow chamber 7, the throttling orifice 5, and the fluid outlet 4 sequentially form a throttling flow path 6. That is, the throttling orifice 5 connects the fluid inlet 3 and the fluid outlet 4, so that the hydraulic oil entering the fluid inlet 3 can flow through the throttling orifice 5 into the fluid outlet 4, thus forming the throttling flow path 6. Figure 1 , Figure 2 and Figure 3 The hollow arrow passage is shown. The throttling passage 6 keeps the fluid inlet 3 and fluid outlet 4 in a normally open state. The flow rate of the throttling passage 6 is 0 L / min-0.5 L / min, preferably 0.2 L / min. When the electromagnet experiences circuit failure or damage to the proportional electromagnet, and the position of the valve core 2 within the cavity 10 causes the flow port 8 formed between the second sliding part 17 and the valve body 1 to be closed, the throttling passage 6 keeps the fluid inlet 3 and fluid outlet 4 in a normally open state. This allows the fluid outlet 4 to still provide a small amount of hydraulic oil to the downstream end for use, enabling the downstream end to operate for a short time without damage. In other words, when the electromagnet experiences circuit failure or damage to the proportional electromagnet, the hydraulic system can operate for a short time, allowing the vehicle to be quickly transported to a repair shop for maintenance, improving user convenience and vehicle safety. Figure 1 , Figure 2 and Figure 3As shown, the elastic element 14 is preferably a spring. The output end 13, valve core 2, and spring are arranged sequentially along the axial direction of the cavity 10. The output end 13 abuts against the first sliding part 16 on the valve core 2. One end of the spring abuts against the second sliding part 17, and the other end of the spring abuts against the bottom wall 23 of the cavity 10. The spring is in a pre-compressed state, so that the valve core 2 has a tendency to slide towards the output end 13 within the cavity 10, thereby ensuring that the valve core 2 and the output end 13 are always in contact. The end of the second sliding part 17 away from the intermediate connecting part 18 extends outward along the axial direction of the valve core 2 to form a positioning post 15. That is, the end of the second sliding part 17 away from the intermediate connecting part 18 extends towards the bottom wall 23 of the cavity 10 to form a positioning post 15. The spring is sleeved on the positioning post 15 to prevent the spring from tilting during extension and retraction, thereby improving the stability of extension and retraction. Specifically, the force applied to the first sliding part 16 by the output terminal 13 is controlled by controlling the current of the electromagnet module 12. In other words, the contact force between the output terminal 13 and the first sliding part 16 is controlled by controlling the current of the electromagnet module 12. When the current of the electromagnet module 12 reaches 400mA-600mA, the contact force between the output terminal 13 and the first sliding part 16 is equal to the spring force. Preferably, when the current of the electromagnet module 12 reaches 500mA, the contact force between the output terminal 13 and the first sliding part 16 is equal to the spring force. When the current of the electromagnet module 12 is greater than 500mA, the contact force between the output terminal 13 and the first sliding part 16 is greater than the spring force. The output terminal 13 pushes the valve core 2 to move to the right, causing the flow port 8 between the second sliding part 17 of the valve core 2 and the valve body 1 to open, allowing hydraulic oil to flow through the regulating passage 9 to the fluid outlet 4, and the spring to be further compressed. When the current of the electromagnet module 12 continues to increase, the opening L of the flow port 8 between the second sliding part 17 of the valve core 2 and the valve body 1 increases, the spring continues to compress, and the flow rate to the fluid outlet 4 through the regulating passage 9 increases. When the current of the electromagnet module 12 reaches 1200mA, the opening L of the flow port 8 between the second sliding part 17 of the valve core 2 and the valve body 1 reaches its maximum, and the opening L is as follows: Figure 6 As shown, the maximum opening amount L is 1.5mm-2mm, preferably 1.8mm. A contact end 21 can be provided on the first sliding part 16 at the position where it abuts against the output end 13, and the output end 13 abuts against the contact end 21 on the first sliding part 16. Furthermore, the relationship between the control current of the electromagnet module 12 and the opening amount L of the valve core 2 is as follows... Figure 8 As shown; the relationship between the control current and flow rate of the electromagnet module 12 is as follows: Figure 7 As shown, the flow rate Q is the total flow rate of the throttling path 6 and the regulating path 9.

[0025] like Figure 3As shown, a sealing groove 19 is provided on the outer edge of the valve core 2. The sealing groove 19 is arranged in a circle around the axis of the valve core 2, and several sealing grooves 19 are arranged along the axis of the valve core 2. A sealing ring 20 is provided in the sealing groove 19. Figure 1 , Figure 2 and Figure 3 As shown, the sealing ring 20 achieves a seal between the valve core 2 and the valve body 1, preventing hydraulic oil from overflowing.

[0026] Specific workflow and principles: The output terminal 13 of the electromagnet module 12 is located on the far left, such as... Figure 1 As shown, at this time, the control current of the electromagnet module 12 is 0mA, the contact force between the output terminal 13 and the first sliding part 16 of the valve core 2 is zero, the valve core 2 is located at the leftmost side of the cavity 10 under the action of the spring force, the flow port 8 formed between the second sliding part 17 of the valve core 2 and the valve body 1 is in a closed state, the hydraulic oil in the fluid inlet 3 cannot flow to the fluid outlet 4 through the regulating passage 9, and the hydraulic oil in the fluid inlet 3 flows to the fluid outlet 4 through the throttling passage 6 formed by the throttling port 5 to ensure a minimum flow rate of 0.2 L / min.

[0027] Increasing the control current of the electromagnet module 12, when the current of the electromagnet module 12 is greater than 500mA, the contact force between the output terminal 13 and the first sliding part 16 of the valve core 2 is greater than the spring force. The output terminal 13 pushes the valve core 2 to move to the right within the cavity 10, thereby opening the flow port 8 between the second sliding part 17 and the valve body 1. Figure 2 As shown, the hydraulic oil in the fluid inlet 3 flows to the fluid outlet 4 through the regulating passage 9. At the same time, the hydraulic oil in the fluid inlet 3 flows to the fluid outlet 4 through the throttling passage 6 formed by the throttling port 5.

[0028] Continue increasing the control current of the electromagnet module 12. When the current of the electromagnet module 12 reaches 1200mA, the contact force between the output terminal 13 and the first sliding part 16 of the valve core 2 is greater than the spring force and reaches its maximum. Figure 3 As shown, the output end 13 pushes the valve core 2 to the rightmost end of the cavity 10, so that the opening size of the flow port 8 between the second sliding part 17 and the valve body 1 reaches the maximum. The hydraulic oil in the fluid inlet 3 flows to the fluid outlet 4 through the regulating passage 9. At the same time, the hydraulic oil in the fluid inlet 3 flows to the fluid outlet 4 through the throttling passage 6 formed by the throttling port 5. At this time, the flow rate of the fluid outlet 4 reaches the maximum of 3.8 L / min.

[0029] The flow rate of fluid outlet 4 is adjusted according to actual needs. That is, the control current of electromagnet module 12 is adjusted according to the load of fluid outlet 4 to control the sliding amount of valve core 2 in cavity 10, thereby controlling the opening and closing of regulating passage 9 and the flow rate through fluid outlet 4.

[0030] Example 2 A hydraulic control system includes the flow control valve described in Example 1.

[0031] In one specific embodiment, the hydraulic control system is a motor cooling system. The motor cooling system includes the flow control valve in Embodiment 1. The flow control valve includes a valve body 1 and a valve core 2. The valve core 2 is disposed inside the valve body 1. The valve body 1 is provided with a fluid inlet 3 and a fluid outlet 4. The valve core 2 is provided with a throttling orifice 5, which connects the fluid inlet 3 and the fluid outlet 4 to form a throttling flow path 6.

[0032] When the electromagnetic control valve experiences electromagnetic circuit failure or proportional electromagnet damage during operation, the cooling oil in the existing motor cooling system cannot flow to the motor, resulting in insufficient cooling of the motor and ultimately rendering the hydraulic control system inoperable. Therefore, the flow control valve of this invention features a throttling orifice 5 on the valve body 1 to establish a throttling flow path 6. This path keeps the fluid inlet 3 and fluid outlet 4 normally open, allowing a small amount of cooling oil to flow into the motor from the outlet 4. This small amount of cooling oil cools the motor, allowing it to operate at low speeds. The small amount of coolant is sufficient to meet the motor's low-speed cooling needs, allowing users to quickly drive the vehicle to a repair shop for maintenance, improving user convenience and vehicle safety.

[0033] In one specific embodiment, the hydraulic control system is a clutch system. The clutch system includes the flow control valve in embodiment 1. The flow control valve includes a valve body 1 and a valve core 2. The valve core 2 is disposed inside the valve body 1. The valve body 1 is provided with a fluid inlet 3 and a fluid outlet 4. The valve core 2 is provided with a throttling orifice 5, which connects the fluid inlet 3 and the fluid outlet 4 to form a throttling passage 6.

[0034] When the electromagnetic control valve experiences electromagnetic circuit failure or proportional electromagnet damage during use, the hydraulic oil in the existing clutch system cannot flow, causing the clutch system to malfunction. Therefore, the flow control valve of this invention features a throttling orifice 5 on the valve body 1 to establish a throttling flow path 6. This path keeps the fluid inlet 3 and fluid outlet 4 in a normally open state, allowing a small amount of hydraulic oil to flow through the clutch system for vehicle operation. With this small flow of hydraulic oil, the clutch engagement speed is slower, and the torque after engagement is lower, allowing the vehicle to start slowly and operate at low speeds. This allows users to quickly drive the vehicle to a repair shop for maintenance, improving user convenience and vehicle safety.

[0035] Example 3 A vehicle includes a hydraulic control system according to embodiment 2. The hydraulic control system includes a flow control valve according to embodiment 1. The flow control valve includes a valve body 1 and a valve core 2. The valve core 2 is disposed inside the valve body 1. The valve body 1 is provided with a fluid inlet 3 and a fluid outlet 4. The valve core 2 is provided with a throttling orifice 5. The throttling orifice 5 connects the fluid inlet 3 and the fluid outlet 4 to form a throttling flow path 6.

[0036] When the electromagnetic control valve experiences a malfunction in its electromagnet circuitry or damage to the proportional electromagnet during operation, the hydraulic oil in the existing hydraulic control system cannot flow, causing the hydraulic control system to malfunction. Therefore, the flow control valve of this invention features a throttling orifice 5 on the valve body 1 to establish a throttling flow path 6. This throttling flow path 6 keeps the fluid inlet 3 and fluid outlet 4 in a normally open state, allowing a small amount of hydraulic oil to flow through the hydraulic control system for operation. This enables the vehicle to run at low speeds, allowing the user to quickly drive the vehicle to a repair shop for maintenance, improving user convenience and vehicle safety.

[0037] It should be noted that the above description is merely a preferred embodiment of the present utility model and the technical principles employed. Those skilled in the art will understand that the present utility model is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the protection scope of the present utility model. Therefore, although the present utility model has been described in detail through the above embodiments, the present utility model is not limited to the above embodiments. Under the circumstances of the inventive concept and the disclosed technical solutions, other equivalent embodiments or equivalent technical means may also be included, all of which fall within the protection scope of the claims of the present utility model.

Claims

1. A flow control valve, characterized in that: It includes a valve body (1) and a valve core (2). The valve core (2) is disposed inside the valve body (1). The valve body (1) is provided with a fluid inlet (3) and a fluid outlet (4). The valve core (2) is provided with a throttling port (5). The throttling port (5) connects the fluid inlet (3) and the fluid outlet (4) to form a throttling passage (6).

2. The flow control valve according to claim 1, characterized in that: A flow cavity (7) is formed between the valve core (2) and the valve body (1), and the fluid inlet (3), the flow cavity (7), the throttling port (5) and the fluid outlet (4) are sequentially connected to form the throttling flow path (6).

3. The flow control valve according to claim 2, characterized in that: A flow port (8) is formed between the valve core (2) and the valve body (1), and the fluid inlet (3), the flow cavity (7), the flow port (8) and the fluid outlet (4) are connected in sequence to form a regulating passage (9).

4. The flow control valve according to claim 3, characterized in that: The valve body (1) has a cavity (10) inside, the valve core (2) is located inside the cavity (10), the outer edge of the valve core (2) is recessed along its radial direction to form a groove (11), and the flow cavity (7) is formed between the groove (11) and the side wall (22) of the cavity (10).

5. The flow control valve according to claim 4, characterized in that: The flow control valve also includes an electromagnet module (12), which has an output end (13). The output end (13) is connected to the valve core (2). The output end (13) drives the valve core (2) to slide along the axial direction of the cavity (10) within the cavity (10) to adjust the opening and closing of the flow port (8) and the opening size of the flow port (8).

6. The flow control valve according to claim 5, characterized in that: The flow control valve also includes an elastic element (14), which is located in the cavity (10). Along the axial direction of the cavity (10), the output end (13), the valve core (2) and the elastic element (14) are connected in sequence, and the elastic element (14) abuts against the valve core (2) and the bottom wall (23) of the cavity (10).

7. The flow control valve according to claim 6, characterized in that: The elastic element (14) is a spring, and the valve body (1) extends toward the bottom wall (23) of the cavity (10) to form a positioning post (15), and the spring is sleeved on the positioning post (15).

8. The flow control valve according to any one of claims 4-7, characterized in that: Along the axial direction of the valve core (2), a first sliding portion (16) is formed on one side of the groove (11), and a second sliding portion (17) is formed on the other side of the groove (11). The first sliding portion (16) and the second sliding portion (17) are slidably disposed in the cavity (10).

9. A hydraulic control system, characterized in that: Includes the flow control valve as described in any one of claims 1-8.

10. A vehicle, characterized in that: Includes the hydraulic control system as described in claim 9.

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