Transmission mechanism

Abstract

The utility model relates to a transmission mechanism which is applied to a hydraulic plunger pump or a hydraulic plunger motor and comprises an oil distribution disc; the cylinder body is fixedly connected with the oil distribution disc; a plunger hole is formed in the cylinder body, the plunger is arranged in the plunger hole, the plunger comprises a ball end and a conical section, a first plunger ring and a second plunger ring are arranged on the conical section, the first plunger ring is made of steel, and the second plunger ring is made of polyether-ether-ketone; the main shaft and the driving disc are of an integrated structure, a plunger ball socket is arranged at the end, close to the cylinder body, of the driving disc, and the ball end of the plunger is connected with the plunger ball socket on the driving disc. According to the transmission mechanism, reliable plunger hole clearance sealing can be provided at a low speed, the low-speed operation stability is improved, the transmission mechanism is also suitable for a high-speed working condition, the anti-pollution capacity is enhanced, the structural requirements for high-speed working condition sealing and heat generation reduction are met, the service life of a pump or a motor is prolonged, and the reliability of the pump or the motor is improved; and the environmental adaptation stability of the product is improved.

Description

Technical Field

[0001] This disclosure relates to the field of hydraulic technology, and more specifically, to a transmission mechanism. Background Technology

[0002] Hydraulic piston pumps and hydraulic piston motors are key components in fluid power systems. Hydraulic piston pumps convert mechanical energy into hydraulic energy of high-pressure hydraulic oil through the reciprocating motion of the pistons, featuring high efficiency, high pressure, and adjustable flow rate. Hydraulic piston motors, on the other hand, convert the hydraulic energy of high-pressure hydraulic oil into mechanical energy to generate rotational motion, characterized by high output torque, smooth operation, high efficiency, and good reversibility. Both are widely used in industries such as construction machinery, agricultural machinery, shipbuilding, and metallurgy. However, existing hydraulic piston pumps and motors exhibit poor stability at low speeds, are prone to leakage, and have poor resistance to contamination. Utility Model Content

[0003] In view of this, the present disclosure provides a transmission mechanism to address the technical deficiencies existing in the prior art.

[0004] To achieve the above objectives, the present disclosure adopts the following technical solution:

[0005] This disclosure provides a transmission mechanism applied to a hydraulic piston pump or a hydraulic piston motor, comprising:

[0006] Oil distribution plate;

[0007] Cylinder block, which is connected to the oil distribution plate;

[0008] A plunger is provided in the cylinder body with a plunger hole, and the plunger is placed in the plunger hole. The plunger includes a ball end and a conical section. A first plunger ring and a second plunger ring are provided in the conical section. The first plunger ring is made of steel, and the second plunger ring is made of polyetheretherketone.

[0009] The main shaft and the drive disk are integrated into one structure. The drive disk has a plunger ball socket at one end near the cylinder body, and the ball end of the plunger is connected to the plunger ball socket on the drive disk.

[0010] In one embodiment of this disclosure, the tapered section of the plunger is provided with two annular mounting grooves, and the first plunger ring and the second plunger ring are respectively assembled in the two annular mounting grooves.

[0011] In one embodiment of this disclosure, the surfaces of the first plunger ring and the second plunger ring are both spherical, and the surfaces of the first plunger ring and the second plunger ring form a line seal with the inner wall of the plunger hole in the working state.

[0012] In one embodiment of this disclosure, the transmission mechanism further includes a central shaft, a central shaft hole is provided at the center of the cylinder, the central shaft is placed in the central shaft hole, and the axis of the central shaft is at a certain angle to the axis of the main shaft.

[0013] In one embodiment of this disclosure, the central shaft includes a ball head and a cylindrical rod, and a central shaft ball socket is provided at one end of the drive disc near the cylinder body, wherein the ball head of the central shaft is connected to the central shaft ball socket.

[0014] In one embodiment of this disclosure, the transmission mechanism further includes a return plate configured to confine the plunger and the central shaft in the plunger socket and central shaft socket of the drive disc, respectively.

[0015] In one embodiment of this disclosure, an elastic member is provided inside the cylindrical rod of the central shaft, and the end face of the cylinder body facing the oil distribution plate abuts against the end face of the oil distribution plate through the elastic member.

[0016] In one embodiment of this disclosure, a plurality of plunger ball sockets and a central shaft ball socket are provided on the end face of the drive disc facing the cylinder block. The plunger ball sockets are evenly distributed on the end face of the drive disc in a circular pattern with the axis of the main shaft as the center.

[0017] In one embodiment of this disclosure, the plunger ball socket and the central shaft ball socket are respectively formed with hemispherical openings on the end face of the drive disc.

[0018] In one embodiment of this disclosure, a bearing assembly is provided on the periphery of the spindle, the bearing assembly being configured to support the spindle.

[0019] The transmission mechanism provided in this disclosure can provide reliable plunger bore clearance sealing at low speeds, improving low-speed operation stability. It is also suitable for high-speed operating conditions, enhancing its resistance to contamination and reducing the risk of damage from contaminants. It meets the structural requirements for sealing and reducing heat generation in high-speed operating conditions, thus improving the service life and reliability of the pump or motor. Furthermore, it is more adaptable to complex operating conditions across a wide temperature and speed range, meeting the requirements of different operating conditions and improving the product's environmental adaptability.

[0020] Other features and advantages of this disclosure will become clear from the following detailed description of exemplary embodiments with reference to the accompanying drawings. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the transmission mechanism provided in one embodiment of the present disclosure;

[0022] Figure 2This is a schematic diagram of the structure of a plunger provided in one embodiment of this disclosure.

[0023] 1-Oil distribution plate; 2-Cylinder block; 3-Plunger; 31-Spherical end; 32-Conical section; 4-First plunger ring; 5-Second plunger ring; 6-Main shaft; 7-Drive disc; 8-Plunger ball socket; 9-Annular mounting groove; 10-Central shaft; 101-Ball head; 102-Cylindrical rod; 11-Return plate; 12-Elastic component; 13-Bearing assembly; 14-Central shaft ball socket. Detailed Implementation

[0024] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. It should be noted that, unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the present disclosure.

[0025] The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit this disclosure or its application or use.

[0026] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0027] It should be noted that similar labels and letters in the following figures indicate similar items; therefore, once an item is defined in one figure, it does not need to be discussed further in subsequent figures.

[0028] The specific embodiments of this disclosure are described below with reference to the accompanying drawings.

[0029] In this article, terms such as "up," "down," "front," "back," "left," and "right" are used only to indicate the relative positional relationship between related parts, rather than to define the absolute position of these related parts.

[0030] In this article, "first," "second," etc., are used only to distinguish one another, and not to indicate degree of importance, order, or prerequisite for each other.

[0031] In this document, terms such as “equal” and “same” are not strict mathematical and / or geometric limitations, but also include errors that are understandable to those skilled in the art and permissible in manufacturing or use.

[0032] This disclosure provides a transmission mechanism for use in a hydraulic piston pump or hydraulic piston motor, including a distributor plate, a cylinder body, a piston, and a main shaft. The cylinder body is fixedly connected to the distributor plate. A piston bore is provided in the cylinder body, and the piston is placed in the piston bore. The piston includes a ball end and a tapered section. A first piston ring and a second piston ring are provided in the tapered section. The first piston ring is made of steel, and the second piston ring is made of polyetheretherketone (PEEK). The main shaft and the drive plate are integrated. A piston ball socket is provided at the end of the drive plate near the cylinder body, and the ball end of the piston is connected to the piston ball socket on the drive plate.

[0033] The transmission mechanism provided in this disclosure can provide reliable plunger bore clearance sealing at low speeds, improving low-speed operation stability. It is also suitable for high-speed operating conditions, enhancing its resistance to contamination and reducing the risk of damage from contaminants. It meets the structural requirements for sealing and reducing heat generation in high-speed operating conditions, thus improving the service life and reliability of the pump or motor. Furthermore, it is more adaptable to complex operating conditions across a wide temperature and speed range, meeting the requirements of different operating conditions and improving the product's environmental adaptability.

[0034] For ease of understanding, please refer to the following: Figures 1 to 2 The specific structure and working principle of the transmission mechanism disclosed herein will be described in detail with reference to the embodiments.

[0035] like Figure 1 As shown, this disclosure provides a transmission mechanism applied to a hydraulic piston pump or a hydraulic piston motor. The transmission mechanism provided by this disclosure includes a distribution plate 1, a cylinder 2, a piston 3, and a main shaft 6. The cylinder 2 is connected to the distribution plate 1. A piston bore is provided in the cylinder 2, and the piston 3 is placed in the piston bore. The piston 3 includes a ball end 31 and a tapered section 32. A first piston ring 4 and a second piston ring 5 are provided in the tapered section 32. The first piston ring 4 is made of steel, and the second piston ring 5 is made of polyetheretherketone (PEEK). The main shaft 6 and the drive disk 7 are integrated. A piston ball socket 8 is provided at one end of the drive disk 7 near the cylinder 2, and the ball end 31 of the piston 3 is connected to the piston ball socket 8 on the drive disk 7.

[0036] Specifically, in applications involving hydraulic piston pumps or motors, the distributor plate 1 is used to introduce hydraulic oil into each piston bore, ensuring that the piston 3 effectively completes the oil suction and pressure processes. Multiple piston bores are located inside the cylinder block 2. One end of the piston 3 is a ball end 31 for connection to the drive plate 7. The remaining portion of the piston 3 is a tapered section 32, on which two piston rings of different materials are mounted. For example... Figure 2 As shown, the first plunger ring 4 is located on the side closest to the oil distribution plate 1. The first plunger ring 4 is made of steel. The second plunger ring 5 is spaced apart from the first plunger ring 4. The distance between the second plunger ring 5 and the oil distribution plate 1 is greater than the distance between the first plunger ring 4 and the oil distribution plate 1. The second plunger ring 5 is made of polyetheretherketone.

[0037] The second plunger ring 5 possesses excellent wear resistance and self-lubricating properties, maintaining a low coefficient of friction even without external lubrication. This helps reduce wear between the plunger 3 and the inner wall of the cylinder 2, thereby extending the service life of the hydraulic plunger pump or hydraulic plunger motor. Furthermore, the second plunger ring 5 exhibits good high-temperature resistance and chemical stability. It not only operates stably over a wide temperature range without significant performance degradation due to temperature changes, but also demonstrates good resistance to most chemicals, reducing the risk of corrosion.

[0038] Furthermore, by placing the first plunger ring 4 closer to the distributor plate 1, it can better withstand the pressure from high-pressure oil, while its steel hardness protects the plunger 3 from damage. The second plunger ring 5, located slightly further away, utilizes its excellent wear resistance and self-lubricating properties to reduce friction between the plunger 3 and the cylinder 2, especially in areas with high shear forces generated during the plunger 3's movement. This different placement of the two plunger rings helps create a more effective sealing system. The first plunger ring 4 primarily serves to prevent high-pressure oil from directly impacting the plunger 3 body, while the second plunger ring 5 helps maintain tight contact between the plunger 3 and the cylinder 2, preventing oil leakage, ensuring the efficiency of the hydraulic system, and better adapting to various operating conditions.

[0039] like Figure 1 As shown, the transmission mechanism of this disclosure also includes a main shaft 6 and a drive disk 7. The main shaft 6 and the drive disk 7 are an integrated structure, which ensures the stability and accuracy of power transmission. A plunger ball socket 8 is provided on the drive disk 7 to accommodate the ball end 31 of the plunger 3, forming a flexible and stable mechanical connection. When the main shaft 6 rotates, it can drive all the plungers 3 to reciprocate through the drive disk 7.

[0040] When the transmission mechanism of this disclosure is applied to a hydraulic piston pump, when an external power source (such as an electric motor) drives the main shaft 6 to rotate, the main shaft 6 drives the piston 3 and the cylinder 2 to rotate together. The axis of the main shaft 6 is at a certain angle to the axis of the cylinder 2. During rotation, the distance from the center of the piston ball head 31 on the piston ball socket 8 located on the drive disc 7 to the end face of the cylinder 2 changes periodically with each rotation, and the piston 3 completes one reciprocating motion accordingly. Specifically, when the piston ball socket 8 moves to a position away from the center of the cylinder 2, the piston 3 is pulled out of the piston hole, forming an oil suction stroke; when the piston ball socket 8 moves back to a position close to the center of the cylinder 2, the piston 3 is pushed into the piston hole, forming an oil pressure stroke. During the oil suction process, the piston 3 extends out of the piston hole, generating negative pressure, causing hydraulic oil to enter the piston hole through the distribution plate 1. During the oil compression process, the plunger 3 retracts into the plunger hole, compressing the oil and causing it to be discharged through the oil distribution plate 1, forming a high-pressure oil flow to drive other hydraulic devices.

[0041] When the transmission mechanism of this disclosure is applied to a hydraulic piston motor, high-pressure oil enters the piston bore through the distribution plate 1, pushing the piston 3 to move outward. The movement of the piston 3 is converted into the rotational motion of the drive plate 7 through the contact between its ball end 31 and the piston ball socket 8 on the drive plate 7. As the drive plate 7 rotates, the main shaft 6 also rotates, outputting the required mechanical power.

[0042] like Figures 1 to 2 As shown, in one embodiment of this disclosure, the tapered section 32 of the plunger 3 is provided with two annular mounting grooves 9, and the first plunger ring 4 and the second plunger ring 5 are respectively assembled in the two annular mounting grooves 9.

[0043] Specifically, the two annular mounting grooves 9 are positioned corresponding to the first plunger ring 4 and the second plunger ring 5, respectively, and are specifically configured as annular recesses. The groove depth of the annular mounting grooves 9 is determined according to the thickness of the first plunger ring 4 and the second plunger ring 5 to ensure the fit between the first plunger ring 4 and the second plunger ring 5 and the annular mounting grooves 9. Similarly, the width of the annular mounting grooves 9 needs to be slightly larger than the width of the plunger rings to avoid ring jamming during high-speed operation, and to facilitate the smooth entry of the plunger rings into the grooves during installation without excessive looseness.

[0044] like Figure 2 As shown, in one embodiment of this disclosure, the surfaces of the first plunger ring 4 and the second plunger ring 5 are both spherical, and the surfaces of the first plunger ring 4 and the second plunger ring 5 form a line seal with the inner wall of the plunger hole in the working state.

[0045] Specifically, by setting the surfaces of the first plunger ring 4 and the second plunger ring 5 to be spherical, the contact area between the first plunger ring 4 and the second plunger ring 5 and the inner wall of their respective plunger holes can be minimized, forming two line seals. This ensures that the seal can be achieved at any position and angle during complex motion, resulting in a better sealing effect. It also helps to reduce the friction loss of the plunger 3 during reciprocating motion, improve the efficiency of the system, and extend the service life of the plunger 3 and the cylinder 2.

[0046] like Figure 1 As shown, in one embodiment of this disclosure, the transmission mechanism further includes a central shaft 10. A central shaft hole is provided at the center of the cylinder body 2, and the central shaft 10 is placed in the central shaft hole. The axis of the central shaft 10 is at a certain angle to the axis of the main shaft 6.

[0047] Specifically, the transmission mechanism of this disclosure also includes a central shaft 10, which is installed in the central shaft hole of the cylinder 2. The axis of the central shaft 10 is at a certain angle to the axis of the main shaft 6, which can stabilize the rotation angle. This angle causes the piston 3 to exhibit an inclined reciprocating motion during its reciprocating motion, making the reciprocating motion of the piston 3 more uniform, reducing impact and vibration during the motion process, thereby improving the efficiency of the system. In addition, the setting of this angle provides stable positioning support through geometric constraints and optimized motion trajectory, and can increase the effective stroke of the piston 3, thereby improving the volumetric efficiency of the pump or motor, that is, increasing the volume of oil delivered or discharged per unit time.

[0048] like Figure 1 As shown, in one embodiment of this disclosure, the central shaft 10 includes a ball head 101 and a cylindrical rod 102. The drive disc 7 is provided with a central shaft ball socket 14 at one end near the cylinder 2, and the ball head 101 of the central shaft 10 is connected to the central shaft ball socket 14.

[0049] Specifically, the central shaft 10 consists of a ball head 101 and a cylindrical rod 102. The ball head 101 is used to connect with the central shaft ball socket 14 on the drive disc 7, and the cylindrical rod 102 is installed in the central shaft hole of the cylinder body 2. The central shaft ball socket 14 allows the central shaft 10 to swing freely within a certain range, thereby adapting to the tilting movement of the plunger 3, effectively dispersing stress during the movement process, reducing stress concentration, and thus extending the service life of the components. The connection between the ball head 101 and the ball socket makes the dynamic response of the system more rapid and smooth during start-up and stop, reducing the impact and noise during start-up and stop. When the drive disc 7 rotates, the ball head 101 of the central shaft 10 swings freely in the central shaft ball socket 14 to adapt to the tilting movement of the plunger 3, while the cylindrical rod 102 of the central shaft 10 remains stable in the central shaft hole of the cylinder body 2, ensuring that the axis of the central shaft 10 is at a certain angle to the axis of the main shaft 6.

[0050] like Figure 1 As shown, in one embodiment of this disclosure, the transmission mechanism further includes a return plate 11, which is configured to confine the plunger 3 and the central shaft 10 in the plunger socket 8 and the central shaft socket 14 of the drive disc 7, respectively.

[0051] Specifically, the return plate 11 is located between the drive disc 7 and the cylinder block 2, and fits against the end face of the drive disc 7. Multiple return holes are provided on the return plate 11, corresponding to the plunger ball sockets 8 and the central shaft ball socket 14 on the drive disc 7, used to restrict the position of the plunger 3 and the central shaft 10. The return plate 11 restricts the plunger 3 and the central shaft 10 respectively in the plunger ball sockets 8 and the central shaft ball socket 14 of the drive disc 7, hinges and fixes the plunger 3 to the drive disc 7, ensuring the stability of the plunger 3 and the central shaft 10 during movement, reducing loosening and displacement, and improving the overall stability of the system. Through the restriction of the return plate 11, the plunger 3 and the central shaft 10 will not experience unnecessary displacement during movement, reducing friction with the drive disc 7 and other components, thereby extending the service life of the components. In addition, the return plate 11 also serves as a load-bearing element for the plunger 3 during the return stroke, able to withstand the return force, thus ensuring the stable operation of the entire mechanism.

[0052] like Figure 1 As shown, in one embodiment of this disclosure, an elastic member 12 is provided inside the cylindrical rod 102 of the central shaft 10, and the end face of the cylinder body 2 facing the oil distribution plate 1 abuts against the end face of the oil distribution plate 1 through the elastic member 12.

[0053] Specifically, an elastic component 12 is provided inside the cylindrical rod 102 of the central shaft 10, which can typically be a spring or other type of elastic element. The elastic component 12 ensures that the cylinder body 2 and the oil distribution plate 1 always maintain a certain preload, ensuring the sealing effect between the two, preventing oil leakage, and absorbing and buffering the impact and vibration during the movement process, reducing wear between the cylinder body 2 and the oil distribution plate 1, and extending the service life of the components.

[0054] like Figure 1 As shown, in one embodiment of this disclosure, a plurality of plunger ball sockets 8 and a central shaft ball socket 14 are provided on the end face of the drive disk 7 facing the cylinder 2. The plunger ball sockets 8 are evenly distributed on the end face of the drive disk 7 with the axis of the main shaft 6 as the center.

[0055] Specifically, the plunger ball socket 8 is used to accommodate the ball end 31 of the plunger 3, ensuring the stability and accuracy of the plunger 3 in reciprocating motion. The plunger ball sockets 8 are evenly distributed on the end face of the drive disc 7 with the axis of the main shaft 6 as the center, ensuring that the movement trajectory of each plunger 3 is consistent and uniformly distributed, thus improving the balance and stability of the system.

[0056] like Figure 1As shown, in one embodiment of this disclosure, the plunger ball socket 8 and the central shaft ball socket 14 respectively form hemispherical opening recesses on the end face of the drive disc 7.

[0057] By designing the plunger ball socket 8 and the central shaft ball socket 14 as hemispherical, a hinged connection between each ball head and its corresponding socket can be achieved. The hemispherical shape of the plunger ball socket 8 and the central shaft ball socket 14 allows the ball end 31 of the plunger 3 and the ball head 101 of the central shaft 10 to move freely during complex working processes such as rotation, reciprocation, rotation, and forces at different angles, increasing the system's flexibility and enabling it to better adapt to the tilting motion of the plunger 3. The hemispherical opening and recess design ensures more uniform contact between the plunger 3 and the central shaft 10 during movement, reducing localized wear and extending the service life of the components.

[0058] like Figure 1 As shown, in one embodiment of this disclosure, a bearing assembly 13 is provided on the periphery of the spindle 6, and the bearing assembly 13 is configured to support the spindle 6.

[0059] Bearing assembly 13 is disposed around the circumference of spindle 6 to support it and ensure its stability and accuracy during high-speed rotation. Bearing assembly 13 may include tapered roller bearings or cylindrical roller bearings, the specific type of which can be selected according to actual working conditions. Bearing assembly 13 effectively reduces friction between spindle 6 and the support structure, extending the service life of both. Bearing assembly 13 can withstand large radial and axial loads, ensuring stable operation of spindle 6 under high-load conditions. The low-friction characteristics of bearing assembly 13 reduce energy loss and improve the overall efficiency of the system.

[0060] The transmission mechanism provided in this disclosure can provide reliable plunger bore clearance sealing at low speeds, improving low-speed operation stability. It is also suitable for high-speed operating conditions, enhancing its resistance to contamination and reducing the risk of damage from contaminants. It meets the structural requirements for sealing and reducing heat generation in high-speed operating conditions, thus improving the service life and reliability of the pump or motor. Furthermore, it is more adaptable to complex operating conditions across a wide temperature and speed range, meeting the requirements of different operating conditions and improving the product's environmental adaptability.

[0061] It should be noted that, for the sake of simplicity, the foregoing method embodiments are all described as a series of actions. However, those skilled in the art should understand that this disclosure is not limited to the described order of actions, because according to this disclosure, some steps can be performed in other orders or simultaneously. Furthermore, those skilled in the art should also understand that the embodiments described in the specification are preferred embodiments, and the actions and modules involved are not necessarily essential to this disclosure.

[0062] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions of other embodiments.

[0063] The preferred embodiments disclosed above are merely illustrative of this disclosure. The optional embodiments do not exhaustively describe all details, nor do they limit the invention to the specific implementations described. Clearly, many modifications and variations can be made based on the content of this disclosure. These embodiments are selected and specifically described in this disclosure to better explain the principles and practical applications of this disclosure, thereby enabling those skilled in the art to better understand and utilize this disclosure. This disclosure is limited only by the claims and their full scope and equivalents.

Claims

1. A transmission mechanism, applied to a hydraulic piston pump or a hydraulic piston motor, characterized in that, include: Oil distribution plate (1); Cylinder block (2), which is connected to the oil distribution plate (1); A plunger (3) is provided in the cylinder body (2), and the plunger (3) is placed in the plunger hole. The plunger (3) includes a ball end (31) and a conical section (32). A first plunger ring (4) and a second plunger ring (5) are provided in the conical section (32). The first plunger ring (4) is made of steel, and the second plunger ring (5) is made of polyetheretherketone. The main shaft (6) and the drive disk (7) are an integrated structure. The drive disk (7) has a plunger ball socket (8) at one end near the cylinder (2). The ball end (31) of the plunger (3) is connected to the plunger ball socket (8) on the drive disk (7).

2. The transmission mechanism according to claim 1, characterized in that, The tapered section (32) of the plunger (3) is provided with two annular mounting grooves (9), and the first plunger ring (4) and the second plunger ring (5) are respectively assembled in the two annular mounting grooves (9).

3. The transmission mechanism according to claim 1, characterized in that, The surfaces of the first plunger ring (4) and the second plunger ring (5) are both spherical, and the surfaces of the first plunger ring (4) and the second plunger ring (5) form a line seal with the inner wall of the plunger hole in the working state.

4. The transmission mechanism according to claim 1, characterized in that, It also includes a central shaft (10), and a central shaft hole is provided at the center of the cylinder body (2). The central shaft (10) is placed in the central shaft hole, and the axis of the central shaft (10) is at a certain angle to the axis of the main shaft (6).

5. The transmission mechanism according to claim 4, characterized in that, The central shaft (10) includes a ball head (101) and a cylindrical rod (102). The drive disc (7) is provided with a central shaft ball socket (14) at one end near the cylinder (2). The ball head (101) of the central shaft (10) is connected to the central shaft ball socket (14).

6. The transmission mechanism according to claim 4, characterized in that, It also includes a return plate (11) configured to confine the plunger (3) and the central shaft (10) in the plunger socket (8) and the central shaft socket (10) of the drive disc (7), respectively.

7. The transmission mechanism according to claim 6, characterized in that, An elastic component (12) is provided inside the cylindrical rod (102) of the central shaft, and the end face of the cylinder (2) facing the oil distribution plate (1) abuts against the end face of the oil distribution plate (1) through the elastic component (12).

8. The transmission mechanism according to claim 6, characterized in that, The drive disc (7) has multiple plunger ball sockets (8) and a central shaft ball socket (14) on the end face facing the cylinder (2). The plunger ball sockets (8) are evenly distributed on the end face of the drive disc (7) with the axis of the main shaft (6) as the center.

9. The transmission mechanism according to claim 8, characterized in that, The plunger ball socket (8) and the central shaft ball socket (14) respectively form hemispherical openings on the end face of the drive disc (7).

10. The transmission mechanism according to claim 1, characterized in that, The main shaft (6) is provided with a bearing assembly (13) on its periphery, the bearing assembly (13) being configured to support the main shaft (6).

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