A hydraulic power cylinder assembly, a steering system and a vehicle

Abstract

The application relates to the technical field of hydraulic power, and provides a hydraulic power cylinder assembly, a steering system and a vehicle; the hydraulic power cylinder assembly comprises a parallelly arranged hydraulic power supply mechanism and an external output power mechanism; the hydraulic power supply mechanism comprises a movable first output shaft; the external output power mechanism comprises a movable second output shaft; the end of the first output shaft is rigidly connected with the end of the second output shaft; the hydraulic power supply mechanism further comprises a first lateral force resisting shell; the external output power mechanism further comprises a second lateral force resisting shell; the side wall of the first lateral force resisting shell is connected with the side wall of the second lateral force resisting shell. The application overcomes the technical problems of poor lateral force resistance of an existing power cylinder, leading to sealing failure and mechanical wear of the hydraulic power cylinder assembly.

Description

Technical Field

[0001] The present application relates to the field of hydraulic power technology, and in particular to a hydraulic power cylinder assembly, a steering system and a vehicle. Background Art

[0002] At present, hydraulic power cylinders have been widely used in the vehicle field. As the power source of many systems, they ensure the reliable operation of various systems. However, the power cylinders currently used, whether single-acting or double-acting, have an inherent defect, which is weak resistance to lateral force. Especially in the application of high-load off-road vehicles, the power cylinders are subjected to complex force conditions and are more likely to generate large lateral impact forces, resulting in risks such as poor stiffness, seal failure, and mechanical wear. If the traditional approach is used to increase the lateral resistance or add a transition transmission structure, the hydraulic cylinder will become too heavy, the system structure will be complex, and the spatial layout will be difficult. There are currently some patent descriptions of power cylinder structures, but they are basically related to some technologies for expanding functions and integrating structures. There are no patent descriptions related to improving lateral resistance.

[0003] Patent document 1 (CN201420853362.0) discloses a new linear power steering gear for a power steering system. The device has a hydraulic power cylinder and a rack and pinion steering gear. The rack and pinion steering gear is provided with a rotary valve assembly. The rotary valve assembly is connected to the power cylinder through an oil circuit. At the same time, the steering gear and the two ends of the power cylinder are rigidly connected together through a mechanical connecting arm. During operation, when the steering gear input shaft rotates, the rotary valve assembly generates corresponding hydraulic power in the power cylinder through the pipeline. At the same time, the rack and pinion structure determines the displacement of the power cylinder. The power cylinder can provide hydraulic power for the external load according to the predetermined displacement movement, that is, to achieve steering assistance. This device avoids the defect that the rack and pinion steering gear cannot be used on large vehicles due to its fragile structure. However, due to the structural limitations of the rack and pinion steering gear, the improvement of the lateral stiffness of the power cylinder is limited, and the problem of the device's weak ability to resist lateral forces still exists.

[0004] Patent document 2 (CN201621486599.5) discloses a combined hydraulic centering cylinder, which has a centering cylinder body, a piston rod, left and right floating pistons, a locking cylinder and other parts. When the device is working, high-pressure oil is filled into the oil chambers on both sides of the centering cylinder body to push the two floating pistons to move toward the middle. The floating pistons press against the piston rod to ensure that it returns to the middle position; then the locking cylinder is filled with high-pressure oil, and the locking piston inside it overcomes the spring tension and moves downward until the lower end of the locking piston is inserted into the annular wedge groove on the piston rod. The piston rod is stuck by the locking piston and cannot move left or right. This device realizes the function of mechanical locking of hydraulic centering, but it has no effect on improving the ability to resist lateral forces. Summary of the Invention

[0005] The purpose of this application is to provide a hydraulic power cylinder assembly, a steering system, and a vehicle, which solve the technical problem of poor lateral force resistance of existing power cylinders. The specific solution is as follows:

[0006] A hydraulic power cylinder assembly comprises: a hydraulic power supply mechanism and an external output power mechanism arranged in parallel; the hydraulic power supply mechanism comprises a movable first output shaft; the external output power mechanism comprises a movable second output shaft;

[0007] The end of the first output shaft is rigidly connected to the end of the second output shaft; the hydraulic power supply mechanism also includes a first lateral force resistance housing;

[0008] The external output power mechanism further includes a second lateral force resisting housing;

[0009] In which, the side wall of the first lateral force anti-resisting shell is connected to the side wall of the second lateral force anti-resisting shell; the hydraulic power supply mechanism drives the first output shaft located inside the first lateral force anti-resisting shell to move, and synchronously drives the second output shaft located inside the second lateral force anti-resisting shell to move in the same direction.

[0010] Optionally, the first lateral force resisting shell and the second lateral force resisting shell are arranged up and down to form a lateral force resisting support shell with an integral structure; wherein the front cross-sectional shape of the lateral force resisting support shell is an 8-shape; the first channel for sliding of the first output shaft arranged inside the first lateral force resisting shell and the second channel for sliding of the second output shaft arranged inside the second lateral force resisting shell are arranged parallel to each other; wherein the first output shaft sliding inside the first channel is designed as a piston rod, and the second output shaft sliding inside the second channel is designed as a lateral force resisting shaft; wherein the internal chamber of the first channel is constituted as a hydraulic oil chamber for relative sliding of the piston rod.

[0011] Optionally, the end of the piston rod is connected to the corresponding end of the lateral force resisting shaft through a connecting arm; through the setting of the connecting arm, the piston rod synchronously drives the lateral force resisting shaft to reciprocate under the drive of the hydraulic power supply mechanism; the end of the piston rod extending out of the hydraulic oil chamber is fixedly connected to the lower part of the connecting arm; the upper part of the connecting arm is fixedly connected to the lateral force resisting shaft.

[0012] Optionally, the cross-sectional shape formed by the lateral force resistance support shell, the lateral force resistance shaft, the connecting arm and the piston rod is a rectangular shape.

[0013] Optionally, the lateral force resisting shaft is connected to the end of the connecting arm and is fixedly provided with a first ball head seat, and the other end away from the connecting arm is fixedly provided with a second ball head seat; the connecting arm is close to the upper side of the lateral force resisting shaft and is protruding with a first ring sleeve that covers the outer peripheral part of the lateral force resisting shaft, and the corresponding side of the second lateral force resisting shell is provided with a second ring sleeve; a retractable first flexible protective cover is provided between the first ring sleeve and the second ring sleeve; wherein, the first flexible protective cover can wrap the left side part of the lateral force resisting shaft extending out of the second lateral force resisting shell; the second lateral force resisting shell is protruding with a third ring sleeve on the side away from the second ring sleeve, and accordingly, the lateral force resisting shaft is provided with a fixed sleeve at the end away from the connecting arm; wherein, a retractable second flexible protective cover is provided between the third ring sleeve and the fixed sleeve; the second flexible protective cover can wrap the right side part of the lateral force resisting shaft extending out of the third ring sleeve.

[0014] Optionally, a first protective bushing and a second protective bushing are respectively provided at both ends of the second channel inside the second lateral force resisting shell near the outlet; wherein, the first protective bushing and the second protective bushing, together with the outer surface of the lateral force resisting shaft and the inner surface of the second channel, constitute a lubrication gap inside which can be filled with grease.

[0015] Optionally, the hydraulic power supply mechanism also includes: an end cover enclosing the opening at the right end of the hydraulic oil chamber, a guide sleeve enclosing the opening at the left end of the hydraulic oil chamber, and a piston slidably arranged inside the hydraulic oil chamber and connected to one end of the piston rod; wherein the piston rod is fixedly connected to the connecting arm through the guide sleeve; the piston divides the hydraulic oil chamber into left and right chambers; at least two sets of sealing rings are provided on the outer surface of the side wall of the piston; and hydraulic oil delivery ports are provided on the side walls of the left chamber and the right chamber.

[0016] Optionally, a guide bushing that cooperates with the sliding of the piston rod is provided in the center hole of the guide sleeve; a first ring portion is protruding from the side opposite to the guide sleeve and the connecting arm, and correspondingly, a second ring portion is protruding from the surface of the lower side of the connecting arm; wherein, the outer diameter of the first ring portion is greater than the outer diameter of the second ring portion; a third flexible protective cover is provided between the first ring portion and the second ring portion, which can wrap the part of the piston rod extending out of the hydraulic oil chamber; the two ends of the third flexible protective cover are respectively sleeved on the outer surfaces of the first ring portion and the second ring portion.

[0017] A steering system includes the hydraulic power cylinder assembly.

[0018] A vehicle comprises the steering system.

[0019] Compared with the prior art, the present invention has the following beneficial effects:

[0020] The present invention provides a hydraulic power cylinder assembly, a steering system, and a vehicle; the hydraulic power cylinder assembly includes: a hydraulic power supply mechanism and an external output power mechanism arranged in parallel; the hydraulic power supply mechanism includes a movable first output shaft; the external output power mechanism includes a movable second output shaft; the end of the first output shaft is rigidly connected to the end of the second output shaft; the hydraulic power supply mechanism also includes a first lateral force resistance shell; the external output power mechanism also includes a second lateral force resistance shell; wherein the side wall of the first lateral force resistance shell is connected to the side wall of the second lateral force resistance shell. This design can effectively solve the problem of weak lateral force of existing power cylinder assemblies, and the overall structure is relatively simple, the layout space occupied is limited, and the risks of poor rigidity, sealing failure, and mechanical wear are avoided. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a schematic diagram of the cross-sectional structure of the hydraulic power cylinder assembly;

[0022] Figure 2 It is a schematic diagram of the cross-sectional structure of the front side of the lateral force resistance support shell;

[0023] Figure 3 It is a schematic diagram of the connection between the hydraulic power cylinder assembly and the external actuator;

[0024] Figure 4 Schematic diagram of the structure of the connecting arm.

[0025] In the picture:

[0026] 1. Hydraulic power supply mechanism; 11. First lateral force resisting housing; 12. First channel; 13. Piston rod; 130. Positioning block; 131. Tightening bolt; 14. End cover; 15. Guide sleeve; 16. Piston; 17. Guide bushing; 18. First ring portion; 19. Second ring portion; 19A. Third flexible protective cover;

[0027] 2. External output power mechanism; 20. Second channel; 21. Second lateral force resisting housing; 22. Lateral force resisting shaft; 23. Second flexible protective cover; 24. First ball seat; 25. Second ball seat; 26. First ring sleeve; 27. Second ring sleeve; 28. First flexible protective cover; 29. ​​Third ring sleeve; 200. Fixed sleeve;

[0028] 100. Lateral force resistance support shell;

[0029] 3. Connecting arm;

[0030] 4. First protective bushing;

[0031] 5. Second protective bushing;

[0032] 6. Lubrication gap;

[0033] 7. Structural stable cavity;

[0034] 8. First pull rod;

[0035] 9. Second pull rod;

[0036] 10. Adjust the nut. DETAILED DESCRIPTION

[0037] In order to make the purpose, technical solutions and advantages of this application clearer, the following Figure 1-4 This application is further described in detail. Obviously, the embodiments described are only a part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0038] The terms used in the examples of this application are for the purpose of describing specific embodiments only and are not intended to limit this application. The singular forms "a," "the," and "the" used in the examples of this application and the appended claims are also intended to include plural forms, and unless the context clearly indicates otherwise, "a plurality" generally includes at least two.

[0039] It should be understood that the term "and / or" as used herein is merely a description of the relationship between associated objects, indicating that three possible relationships exist. For example, "A and / or B" can represent: A exists alone, A and B exist simultaneously, or B exists alone. Furthermore, the character " / " in this document generally indicates that the associated objects are in an "or" relationship.

[0040] It should be understood that although the terms first, second, third, etc. may be used to describe in the embodiments of the present application, these descriptions should not be limited to these terms. These terms are only used to distinguish the descriptions. For example, without departing from the scope of the embodiments of the present application, the first may also be referred to as the second, and similarly, the second may also be referred to as the first.

[0041] As used herein, the words "if" and "if" may be interpreted as "at the time of" or "when" or "in response to determining" or "in response to detecting," depending on the context. Similarly, the phrases "if it is determined" or "if (stated condition or event) is detected" may be interpreted as "when it is determined" or "in response to the determination" or "when detecting (stated condition or event)" or "in response to detecting (stated condition or event)," depending on the context.

[0042] It should be noted in particular that any symbols and / or numbers in the specification that are not marked in the accompanying drawings are not drawing marks.

[0043] The following combination Figure 1 Example 1 of the present application is described in detail.

[0044] Example 1

[0045] A hydraulic power cylinder assembly includes: a hydraulic power supply mechanism 1 and an external output power mechanism 2 arranged in parallel; the hydraulic power supply mechanism 1 includes a movable first output shaft; the external output power mechanism 2 includes a movable second output shaft;

[0046] The end of the first output shaft is rigidly connected to the end of the second output shaft; the side wall of the first lateral force anti-resistance shell 11 composed of a non-extensible part included in the hydraulic power supply mechanism 1 is connected to the side wall of the second lateral force anti-resistance shell 21 composed of a non-extensible part included in the external output power mechanism 2; wherein, the hydraulic power supply mechanism 1 drives the first output shaft located inside the first lateral force anti-resistance shell 11 to move back and forth in a straight line, and synchronously drives the second output shaft located inside the second lateral force anti-resistance shell 21 to move in the same direction.

[0047] Specifically, the hydraulic power supply mechanism 1 includes a first output shaft and the external output power mechanism 2 includes a second output shaft, both of which have the same side end portions rigidly connected to each other up and down; wherein, a structurally stable cavity 7 is formed between the portion of the first output shaft extending from the first lateral force resistance housing 11 and the portion of the second output shaft extending from the second lateral force resistance housing 21. The structurally stable cavity 7 is configured to cooperate with the first lateral force resistance housing 11 and the second lateral force resistance housing 21 so that the piston rod in the hydraulic power cylinder assembly can withstand the impact of the lateral impact force when subjected to a large lateral impact force, and the piston rod will not be bent and deformed by the force, resulting in failure of the device. The hydraulic power cylinder assembly of the present application has a significant improvement in its resistance stability to lateral impact forces, ensuring that the friction fit between its internal components will not be abnormal.

[0048] Specifically, the external output power mechanism 2 serves as a power output mechanism for driving an external actuator to work; the hydraulic power supply mechanism 1 is used to provide driving force to the external output power mechanism 2 to drive the external output power mechanism 2 to operate.

[0049] Furthermore, when the input ends on both sides of the external output power mechanism 2 are subjected to a large lateral impact force, under the limiting protection of the first lateral force anti-resistance shell 11 and the second lateral force anti-resistance shell 21, the external force is transmitted to the first output shaft inside the first lateral force anti-resistance shell 11 through the second output shaft inside the second lateral force anti-resistance shell 21.

[0050] Compared to traditional power cylinder assemblies, these systems often lack the necessary response measures when subjected to significant lateral impacts. Because power cylinder assemblies are precision-manufactured components, their dimensional accuracy directly impacts engine performance, efficiency, and lifespan. The piston rod outer diameter of traditional power cylinder assemblies is also precisely calculated. Therefore, simply increasing the piston rod's outer diameter solely to improve its ability to withstand lateral forces is infeasible. Improperly increasing the piston's outer diameter can lead to slower system response, impacting operational accuracy and sensitivity, while also increasing frictional resistance and reducing system efficiency.

[0051] In contrast, the present application provides a specially designed hydraulic power cylinder assembly that can drive external actuators to operate, such as steering operations, when the cylinder body is subjected to a large lateral impact force under complex working conditions. When suddenly subjected to a large external lateral impact force, the second output shaft inside the second lateral force-resisting housing 21 is used to resist the first wave of lateral impact force. Then, the overall structure of the hydraulic power supply mechanism 1 and the external output power mechanism 2 is used as a support backing to block the second wave of lateral impact force. Finally, when the lateral impact force weakened by the two waves is transmitted to the first output shaft (i.e., the piston rod) inside the first lateral force-resisting housing 11, the impact amplitude of the lateral impact force has been weakened to more than 90%. This avoids the risks of seal failure and mechanical wear of the hydraulic power cylinder assembly.

[0052] A further optimized design scheme is specifically as follows: the first lateral force resisting shell 11 and the second lateral force resisting shell 21 are arranged together up and down to form an integrated lateral force resistance support shell 100; wherein, the front cross-sectional shape of the lateral force resistance support shell 100 is an 8-shape; the first channel 12 for sliding of the first output shaft arranged inside the first lateral force resisting shell 11 and the second channel 2 for sliding of the output shaft arranged inside the second lateral force resisting shell 21 are arranged parallel to each other; wherein, the first output shaft sliding inside the first channel 12 is designed as a piston rod 13, and the second output shaft sliding inside the second channel 2 is designed as a lateral force resisting shaft 22; wherein, the internal chamber of the first channel 12 is constituted as a hydraulic oil chamber for relative sliding of the piston rod 13.

[0053] Specifically, in order to improve the overall resistance strength of the hydraulic power cylinder assembly and to reduce the space occupancy, the first lateral force resistance shell 11 and the second lateral force resistance shell 21 involved in this application are arranged up and down as an integrated lateral force resistance support shell 100; wherein, the front cross-sectional shape of the lateral force resistance support shell 100 is an 8-shape, and the structure of the lateral force resistance support shell 100 is designed to be narrow at the top and wide at the bottom, that is, the outer diameter and inner diameter of the hole of the first lateral force resistance shell 11 are correspondingly larger than the outer diameter and inner diameter of the hole of the second lateral force resistance shell 21. The layout advantage of this design is that, through the shape design of the lateral force resistance support shell 100, when subjected to a large external lateral impact force, the lateral impact force can be evenly dispersed to various parts of the lateral force resistance support shell 100, avoiding stress concentration at a certain point or a certain side, thereby improving the ability to resist lateral forces while reducing the risk of local deformation and damage; secondly, the structural design of the 8-shaped lateral force resistance support shell 100 has high stability and high integration, reduces the space occupancy rate, and also facilitates the installation, arrangement and connection of various components (such as the lateral force resistance shaft 22, piston rod, etc.).

[0054] Furthermore, the end of the piston rod 13 is connected to the corresponding end of the lateral force resisting shaft 22 through the connecting arm 3; through the setting of the connecting arm 3, the piston rod 13 synchronously drives the lateral force resisting shaft 22 to reciprocate under the drive of the hydraulic power supply mechanism 1; the end of the piston rod 13 extending out of the hydraulic oil chamber is fixedly connected or fixedly sleeved with the lower part of the connecting arm 3; the upper part of the connecting arm 3 is fixedly connected or fixedly sleeved with the lateral force resisting shaft 22.

[0055] See also Figure 1 As shown, the lateral force resistance support housing 100, the lateral force resistance shaft 22, the connecting arm 3 and the piston rod 13 form a rectangular lateral cross-sectional shape.

[0056] Among them, when the input end of the external output power mechanism 2 is subjected to a large lateral impact force, the second output shaft inside the second lateral force resisting shell 21 is configured to be connected to the piston rod 13 located inside the first lateral force resisting shell 11 included in the hydraulic power supply mechanism 1 through the connecting arm 3, so that the lateral force resistance support shell 100 constitutes an impedance to the lateral force.

[0057] Specifically, the piston rod 13 and the lateral force resisting shaft 22 are arranged in parallel, and their ends on the same side are connected by a connecting arm 3, thereby achieving synchronous movement of the piston rod 13 and the lateral force resisting shaft 22. When the piston rod 13 and the lateral force resisting shaft 22 extend outward synchronously, the portion where the piston rod 13 extends out of the first lateral force resisting housing 11, the portion where the lateral force resisting shaft 22 extends out of the second lateral force resisting housing 21, and the left side portion of the lateral force resisting support housing 100 form a non-enclosed structurally stable cavity 7, thereby ensuring the stability of the operation of the piston rod 13 and the lateral force resisting shaft 22.

[0058] At the same time, according to the overall structural layout of the present application, the overall lateral cross-section of the lateral force resistance support housing 100, the lateral force resistance shaft 22, the connecting arm 3 and the piston rod 13 is a rectangular structure, see Figure 1 Compared with the traditional piston rod 13, the overall rigidity of the assembly is greatly improved, and the overall resistance of the hydraulic power cylinder assembly is improved.

[0059] It should be further explained that, with respect to the diameter of the piston rod 13 of the hydraulic power cylinder assembly used in the prior art, the outer diameter of the piston rod 13 used in the present application is at least halved under the same conditions (e.g., an external load of 2 tons). At the same time, the deformation of the piston rod 13 of the present application is increased by nearly 80%. For example, compared with the existing hydraulic power cylinder assembly, when subjected to a larger lateral force, the radial elastic offset of the piston rod is reduced from the original 0.2 mm to 0.05 mm, and the deviation is reduced by 75%.

[0060] Furthermore, the lateral force resisting shaft 22 is connected to the end of the connecting arm 3 and is fixedly provided with a first ball head seat 24, and the other end away from the connecting arm 3 is fixedly provided with a second ball head seat 25; the connecting arm 3 is close to the side of the lateral force resisting shaft 22 and is protruded with a first ring sleeve 26 covering the outer peripheral part of the lateral force resisting shaft 22, and the corresponding side of the second lateral force resisting shell 21 is protruded with a second ring sleeve 27; a retractable first flexible protective cover 28 is elastically connected between the first ring sleeve 26 and the second ring sleeve 27; wherein, the first flexible protective cover 28 can be The left side portion of the lateral force resisting shaft 22 extending out of the second lateral force resisting shell 21 is sealed and wrapped; a third ring sleeve 29 is protruding from the side of the second lateral force resisting shell 21 away from the second ring sleeve 27, and accordingly, a fixed sleeve 200 is provided on the end of the lateral force resisting shaft 22 away from the connecting arm 3; wherein, a retractable second flexible protective cover 23 is elastically connected between the third ring sleeve 29 and the fixed sleeve 200; the second flexible protective cover 23 can wrap the right side portion of the lateral force resisting shaft 22 extending out of the third ring sleeve 29.

[0061] Furthermore, the overall structure of the connecting arm 3 is an 8-shaped structure; wherein, at least two reinforcing ribs are provided in the recessed areas in the middle parts of both sides of the connecting arm 3; and the overall connection strength of the connecting arm 3 is increased by the design of the reinforcing ribs.

[0062] During installation, the connecting arm 3 is integrally sleeved on the end of the lateral force resisting shaft 22 and the piston rod 13; wherein, the end of the lateral force resisting shaft 22 is threadedly connected to the first ball head seat 24 to press and fix the upper part of the connecting arm 3; the end of the piston rod 13 is threadedly connected to the external fixing bolt to press and fix the lower part of the connecting arm 3.

[0063] Specifically, the outer diameter of the first ring sleeve 26 is smaller than the outer diameter of the second ring sleeve 27; the outer diameter of the third ring sleeve 29 is larger than the outer diameter of the fixed sleeve 200; the advantage of this design is that when the lateral force resisting shaft 22 moves back and forth, sufficient gaps can be left between the first flexible protective cover 28 and the second flexible protective cover 23 and the lateral force resisting shaft 22, thereby avoiding frictional contact between the first flexible protective cover 28 and the second flexible protective cover 23 and the lateral force resisting shaft 22.

[0064] Specifically, the first ball head seat 24 and the second ball head seat 25 are used to connect external actuators; wherein, the external actuators are inclined to the axis of the lateral force resistance shaft 22 in the direction of the lateral impact force of the actual vehicle; for example, the external actuator (such as a pull rod) is connected to the first ball head seat 24 or the second ball head seat 25 at a 35-degree direction.

[0065] In this embodiment, a detailed description is given by taking the external actuator as an example of a tie rod. The first ball head seat 24 is hinged to the ball end of the first tie rod 8; the second ball head seat 25 is hinged to the ball end of the second tie rod 9; and the other ends of the first tie rod 8 and the second tie rod 9 are both provided with ball head components. The ball head components include a ball head seat connected to one end of the first tie rod 8 or the second tie rod 9, a ball end hinged to the ball head seat, a ball pin integrally connected to the ball end, a connecting nut threadedly connected to the ball pin, and a stop pin passing through the rod of the ball pin to prevent the connecting nut from falling off.

[0066] The first pull rod 8 and the second pull rod 9 have the same structure; the bodies of the first pull rod 8 and the second pull rod 9 are both provided with an adjusting nut 10 for adjusting the length of the pull rod.

[0067] It can be understood that the lateral force resisting shaft 22 provided in the present application slides in the second channel inside the second lateral force resisting housing 21 in a sliding friction manner, thereby avoiding the situation where the hydraulic oil leaks due to seal failure.

[0068] Furthermore, through the joint support and limiting action of the first ring sleeve 26, the second ring sleeve 27, the third ring sleeve 29, the connecting arm 3 and the lateral force resistance support shell 100, the movement process of the lateral force resistance shaft 22 is limited, and the radial offset of the lateral force resistance shaft 22 is reduced as much as possible; and based on this, by utilizing the first flexible protective cover 28 and the second flexible protective cover 23, the parts of the lateral force resistance shaft 22 extending out of both sides of the second lateral force resistance shell 21 are wrapped, thereby preventing external dust or particles from entering the second channel 20 inside the second lateral force resistance shell 21, causing friction loss.

[0069] Furthermore, a first protective bushing 4 and a second protective bushing 5 are respectively provided at both ends of the second channel 20 within the second lateral force resistance housing 21, near the outlet. The left side wall of the first protective bushing 4 and the right side wall of the second protective bushing 5, together with the outer side surface of the lateral force resistance shaft 22 and the inner surface of the second channel 20, form a lubrication gap 6 that can be filled with grease. It can be understood that the present application utilizes the first protective bushing 4 and the second protective bushing 5, and utilizes the inner space of the second channel 20, thereby constructing a lubrication gap 6 with an annular structure that can be filled with grease. At the same time, the first protective bushing 4 and the second protective bushing 5 of the present application are non-embedded installations within the second channel 20. The advantage of this design is that, on the basis of achieving the movement limit of the lateral force resisting shaft 22, it not only reduces the sliding friction contact area between the lateral force resisting shaft 22 and the second lateral force resisting shell 21, but also provides lubrication effect to the outer surface of the lateral force resisting shaft 22 located inside the second channel 20 through the grease filled in the lubrication gap 6, thereby achieving the expected effect of reducing friction and increasing slip (i.e. reducing friction and increasing smoothness).

[0070] Furthermore, the hydraulic power supply mechanism 1 also includes: an end cover 14 that closes the opening at the right end of the hydraulic oil chamber, a guide sleeve 15 that closes the opening at the left end of the hydraulic oil chamber, and a piston 16 that is slidably arranged inside the hydraulic oil chamber and connected to the right end of the piston rod 13; wherein, the left end of the piston rod 13 passes through the guide sleeve 15 and is fixedly connected to the connecting arm 3; the piston 16 divides the hydraulic oil chamber into left and right chambers; at least two groups of sealing rings (such as lip sealing rings) are provided on the outer surface of the side wall of the piston 16; and hydraulic oil delivery ports are provided on the lower side walls of the left chamber and the right chamber.

[0071] Specifically, the right end of the piston rod 13 extends into the interior of the piston and is fixed to the piston 16 by tightening the bolt 131; wherein, the right end face of the tightening bolt 131 is further provided with at least two pre-assembled threaded holes; the outer surface of the right end of the piston rod 13 close to the left end face of the piston is surrounded by a positioning block 130.

[0072] It will be understood that the hydraulic power supply mechanism 1 involved in this application uses piston 16 to drive the lateral force resistance shaft 22 to telescopic movement; wherein, the power source of the hydraulic power supply mechanism 1 adopts a hydraulic drive method; during use, an external hydraulic oil pump controls the flow direction of the hydraulic oil and the movement direction of the piston 16 within the hydraulic oil chamber to achieve reciprocating movement of the piston rod 13. This application integrates the hydraulic power supply mechanism 1 and the external output power mechanism 2 to ensure the effectiveness of product operation while minimizing space occupation, overcoming the design defects of traditional complex structures. The service life of the product is significantly improved.

[0073] Furthermore, a guide bushing 17 is provided in the center hole of the guide sleeve 15 to cooperate with the sliding of the piston rod 13; a first ring portion 18 is protruding from the side opposite to the guide sleeve 15 and correspondingly, a second ring portion 19 is protruding from the surface of the lower side of the connecting arm 3; wherein, the outer diameter of the first ring portion 18 is greater than the outer diameter of the second ring portion 19; a third flexible protective cover 19A is provided between the first ring portion 18 and the second ring portion 19 to wrap the portion of the piston rod 13 extending out of the hydraulic oil chamber; the two ends of the third flexible protective cover 19A are respectively sleeved on the outer surfaces of the first ring portion 18 and the second ring portion 19.

[0074] It can be understood that the inner surface of the center hole of the guide sleeve 15 of the present application is embedded with a guide bushing 17; wherein, the inner surface of the guide bushing 17 is flush with the inner surface of the remaining part of the center hole of the guide sleeve 15; the advantage of this design is that by utilizing the inner surface of the guide bushing 17 to replace part of the inner surface of the center hole of the guide sleeve 15 to complete the sliding contact with the piston rod, thereby ensuring that the guide sleeve 15 completes the overall movement limit of the piston rod, achieving the technical effect of reducing the friction of the piston rod, and also ensuring the sealing effect inside the hydraulic oil chamber.

[0075] It should be further explained that, since the outer diameter of the first ring portion 18 is larger than the outer diameter of the second ring portion 19 , when the third flexible protective cover 19A moves with the piston rod, there is sufficient gap between the third flexible protective cover 19A and the piston rod to avoid frictional contact.

[0076] Furthermore, a first O-ring is provided on the inner surface of the center hole of the guide sleeve 15 near the left outlet; wherein, a second O-ring is also provided on the inner surface of the guide sleeve 15 in contact with the hydraulic oil chamber.

[0077] It is understood that when the load direction of the external actuator is not aligned with the lateral force resistance shaft 22, a lateral reaction force will inevitably be generated at the first ball seat 24 and the second ball seat 25. Specifically, the lateral reaction force at the second ball seat 25 is directly borne by the lateral force resistance shaft 22, the lateral force resistance support housing 100, and the second protective bushing 5, and is not transmitted to the piston rod 13. The lateral reaction force at the first ball seat 24 is borne by the piston rod 13, the connecting arm 3, the lateral force resistance shaft 22, the lateral force resistance support housing 100, and the first protective bushing 4. The overall stiffness of these components is much greater than that of the piston rod 13 itself, ultimately resulting in a very small lateral reaction force transmitted to the piston rod 13. Most of the lateral reaction force is borne by the lateral force resistance shaft 22, but the lateral force resistance shaft 22 is much less sensitive to deformation and sealing than the piston rod 13, thereby indirectly significantly improving the hydraulic cylinder assembly's ability to resist lateral impact forces.

[0078] It can be understood that compared with the existing technology, the present application designs a dedicated and highly integrated hydraulic power cylinder assembly, thereby improving the overall ability to resist lateral forces, and avoiding the external effects of lateral impact forces on the piston rod during operation, resulting in hydraulic seal failure inside the hydraulic oil chamber and increased friction and wear during the movement of the piston rod, resulting in performance failure.

[0079] On the other hand, the present application provides a steering system including the hydraulic power cylinder assembly.

[0080] On the other hand, the present application provides a vehicle comprising the steering system.

[0081] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the above embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A hydraulic power cylinder assembly, characterized in that: include: A hydraulic power supply mechanism (1) and an external output power mechanism (2) arranged in parallel; The hydraulic power supply mechanism (1) includes a movable first output shaft; the external output power mechanism (2) includes a movable second output shaft; The end of the first output shaft is rigidly connected to the end of the second output shaft; The hydraulic power supply mechanism (1) further comprises a first lateral force resistance housing (11); the external output power mechanism (2) further comprises a second lateral force resistance housing (21); wherein the side wall of the first lateral force resisting shell (11) is connected to the side wall of the second lateral force resisting shell (21); When the input end of the external output power mechanism (2) is subjected to a lateral impact force, the hydraulic power supply mechanism (1) drives the first output shaft located inside the first lateral force resistance housing (11) to move, thereby synchronously driving the second output shaft located inside the second lateral force resistance housing (21) to move.

2. The hydraulic power cylinder assembly according to claim 1, characterized in that: The first lateral force resisting housing (11) and the second lateral force resisting housing (21) are arranged vertically to form a lateral force resisting support housing (100) of an integral structure; wherein the front cross-section of the lateral force resisting support housing (100) is in the shape of an 8; a first channel (12) for sliding of a first output shaft provided inside the first lateral force resisting housing (11) and a second channel (20) for sliding of a second output shaft provided inside the second lateral force resisting housing (21) are arranged parallel to each other; wherein the first output shaft sliding inside the first channel (12) is designed as a piston rod (13), and the second output shaft sliding inside the second channel (20) is designed as a lateral force resisting shaft (22); wherein the internal chamber of the first channel (12) constitutes a hydraulic oil chamber that can slide relative to the piston rod (13).

3. The hydraulic power cylinder assembly according to claim 2, characterized in that: The end of the piston rod (13) is connected to the corresponding end of the lateral force resisting shaft (22) through the connecting arm (3); through the setting of the connecting arm (3), the piston rod (13) is driven by the hydraulic power supply mechanism (1) to synchronously drive the lateral force resisting shaft (22) to move back and forth; the end of the piston rod (13) extending out of the hydraulic oil chamber is fixedly connected to the lower part of the connecting arm (3); the upper part of the connecting arm (3) is fixedly connected to the lateral force resisting shaft (22).

4. The hydraulic power cylinder assembly according to claim 3, characterized in that: The lateral cross-section shape formed by the lateral force resistance support housing (100), the lateral force resistance shaft (22), the connecting arm (3) and the piston rod (13) is a rectangular shape.

5. The hydraulic power cylinder assembly according to claim 4, characterized in that: The lateral force resisting shaft (22) is connected to the end of the connecting arm (3) and is fixedly provided with a first ball head seat (24), and the other end away from the connecting arm (3) is fixedly provided with a second ball head seat (25); the connecting arm (3) is close to the upper side of the lateral force resisting shaft (22) and is provided with a first ring sleeve (26) that covers the outer peripheral part of the lateral force resisting shaft (22), and the corresponding side of the second lateral force resisting shell (21) is provided with a second ring sleeve (27); a retractable first flexible protective cover (28) is provided between the first ring sleeve (26) and the second ring sleeve (27); wherein the first flexible protective cover (28) is provided with a plurality of protruding rings. 8) The left side portion of the lateral force resisting shaft (22) extending from the second lateral force resisting shell (21) can be wrapped; a third ring sleeve (29) is provided on the side of the second lateral force resisting shell (21) away from the second ring sleeve (27), and correspondingly, a fixed sleeve (200) is provided on the end of the lateral force resisting shaft (22) away from the connecting arm (3); wherein a retractable second flexible protective cover (23) is provided between the third ring sleeve (29) and the fixed sleeve (200); the second flexible protective cover (23) can wrap the right side portion of the lateral force resisting shaft (22) extending outside the third ring sleeve (29).

6. The hydraulic power cylinder assembly according to claim 5, characterized in that: A first protective bushing (4) and a second protective bushing (5) are respectively provided at both ends of the second channel (20) inside the second lateral force resisting shell (21) near the outlet; wherein the first protective bushing (4) and the second protective bushing (5) together with the outer surface of the lateral force resisting shaft (22) and the inner surface of the second channel (20) form a lubricating gap (6) inside which can be filled with grease.

7. The hydraulic power cylinder assembly according to claim 6, characterized in that: The hydraulic power supply mechanism (1) further comprises: an end cover (14) enclosing the right end opening of the hydraulic oil chamber, a guide sleeve (15) enclosing the left end opening of the hydraulic oil chamber, and a piston (16) slidably arranged in the hydraulic oil chamber and connected to one end of the piston rod (13); wherein the piston rod (13) passes through the guide sleeve (15) and is fixedly connected to the connecting arm (3); the piston (16) divides the hydraulic oil chamber into left and right chambers; at least two sets of sealing rings are provided on the outer surface of the side wall of the piston (16); and hydraulic oil delivery ports are provided on the side walls of both the left and right chambers.

8. The hydraulic power cylinder assembly according to claim 7, characterized in that: A guide bushing (17) is provided in the center hole of the guide sleeve (15) for sliding with the piston rod (13); a first ring portion (18) is provided on the side opposite to the guide sleeve (15) and the connecting arm (3); correspondingly, a second ring portion (19) is provided on the surface of the lower side of the connecting arm (3); wherein the outer diameter of the first ring portion (18) is greater than the outer diameter of the second ring portion (19); a third flexible protective cover (19A) is provided between the first ring portion (18) and the second ring portion (19) for wrapping the portion of the piston rod (13) extending out of the hydraulic oil chamber; and the two ends of the third flexible protective cover (19A) are respectively sleeved on the outer surfaces of the first ring portion (18) and the second ring portion (19).

9. A steering system, characterized in that: The invention comprises the hydraulic power cylinder assembly according to any one of claims 1 to 8.

10. A vehicle, characterized in that: The invention comprises the steering system described in claim 9.

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