Swing cylinder capable of bearing axial and radial loads

Abstract

The utility model relates to a kind of swing cylinder with bearing axial and radial load, including oil cylinder shell, the swing rotating shaft being set in the inside of oil cylinder shell can rotate, the both ends of swing rotating shaft are respectively equipped with the swing output flange that rotates with the rotation of swing rotating shaft, each swing output flange is sealedly connected between oil cylinder shell side wall and can rotate relative to the side wall of oil cylinder shell, the clearance between the end portion side wall of swing rotating shaft, the end portion inner wall of oil cylinder shell and the side wall of swing output flange is formed as installation clearance, the inside of installation clearance is equipped with the radial support mechanism that provides radial support to swing rotating shaft and the axial support mechanism that provides axial support to swing rotating shaft;The utility model overcomes the defect that traditional swing cylinder has limited bearing capacity, by innovatively integrating axial and radial composite support mechanism in end cap space, realize compact structure, improve bearing capacity, enhance rigidity and prolong service life.

Description

Technical Field

[0001] This utility model relates to the field of swing hydraulic cylinder technology, specifically to a swing cylinder capable of bearing axial and radial loads. Background Technology

[0002] A vane-type oscillating cylinder is an actuator that converts hydraulic energy into mechanical oscillating motion. Its core structure employs a radially arranged vane design. When pressurized oil enters the oil chamber and acts on the vanes, it drives the drive shaft to rotate and output torque, achieving reciprocating oscillation at a limited angle. This design gives it significant advantages: low moment of inertia, sensitive action response, uniform output rotation, and weak pulsation, making it suitable for precision control scenarios with high dynamic performance requirements.

[0003] Authorization number CN119435501B discloses a swing-type hydraulic actuator. According to its specification and drawings, the bearing supporting the rotation of the hollow shaft is a deep groove ball bearing. The inner ring of the deep groove ball bearing has a clearance fit with the hollow shaft. The end face of the inner ring of the deep groove ball bearing contacts the locating shoulder of the hollow shaft bearing. The outer ring of the deep groove ball bearing has an interference fit with the bearing seat hole on the end cover. The end face of the outer ring of the deep groove ball bearing fits with the lower end face of the pressure cap. The pressure cap and the end cover are connected by a second bolt to press the deep groove ball bearing, thereby supporting the free rotation of the hollow shaft.

[0004] However, this design also has certain limitations: 1. During operation, the pressure oil acting on the rotor and blades may generate a certain axial force. If this axial force is too large, it will severely shorten the life of the deep groove ball bearing, leading to premature failure; 2. When radial load and large axial load exist simultaneously, the contact angle between the balls and raceways of the deep groove ball bearing is not fixed, resulting in poor stress conditions and making it prone to fatigue spalling; 3. If the vane-type oscillating cylinder is used in conditions such as frequent start-stop, reversing impact, or unstable load, such as in construction machinery, the deep groove ball bearing may not be able to provide sufficient support rigidity, affecting the overall machine accuracy and lifespan. Summary of the Invention

[0005] This invention addresses the aforementioned shortcomings in the internal design of swing hydraulic cylinders by proposing a swing cylinder capable of withstanding axial and radial loads. It overcomes the limitation of traditional swing cylinders in terms of load-bearing capacity by innovatively integrating an axial and radial composite support mechanism within the end cap space, thereby achieving a compact structure, improved load-bearing capacity, enhanced rigidity, and extended service life.

[0006] The objective of this invention is achieved through the following technical solution: a swing cylinder capable of bearing axial and radial loads, comprising a cylinder housing, a rotatable swing shaft disposed inside the cylinder housing, and swing output flanges at both ends of the swing shaft that rotate with the swing shaft. Each swing output flange is sealed to the side wall of the cylinder housing and is rotatable relative to the side wall of the cylinder housing. The gap between the end side wall of the swing shaft, the end inner wall of the cylinder housing, and the side wall of the swing output flange forms an installation gap. The installation gap is provided with a radial support mechanism that provides radial support for the swing shaft and an axial support mechanism that provides axial support for the swing shaft.

[0007] Preferably, the inner walls of both ends of the cylinder housing are provided with a first annular groove, a second annular groove and a third annular groove with different diameters. The interior of the first annular groove is connected to the interior of the second annular groove. Both ends of the swing shaft are provided with a fourth annular groove. Each radial support mechanism is disposed between the first annular groove and the fourth annular groove. Each axial support mechanism is disposed between the first annular groove, the second annular groove and the fourth annular groove. A sealing ring is also provided between the interior of each third annular groove and the side wall of the swing shaft. In this setup, multiple annular grooves form a "mounting skeleton," providing precise, predefined mounting positions for the radial and axial support mechanisms. This ensures that each support component can be quickly and accurately positioned during assembly, guaranteeing final assembly precision and consistency.

[0008] Preferably, each of the axial support mechanisms includes an axial support sleeve and a first cylindrical roller. The axial support sleeve is hollow and is fitted inside the first annular groove and the second annular groove. Both ends of the swing shaft pass through the interior of the axial support sleeve. A plurality of first cylindrical rollers capable of rolling are provided between the interior of the axial support sleeve and the surface of the fourth annular groove. The axis of each first cylindrical roller is parallel to the axis of the swing shaft. In this configuration, the line contact of the first cylindrical roller and the fourth annular groove of the swing shaft form a large contact area, which can withstand the large axial force generated by the hydraulic oil acting on the blade and the limiting plate, effectively preventing mechanism failure due to excessive axial force; the first cylindrical roller replaces sliding friction by rolling on the wall of the fourth annular groove, which significantly reduces the resistance of the axial movement of the swing shaft, making the cylinder more responsive and the transmission efficiency higher.

[0009] Preferably, the axial support sleeve includes a hollow annular base and a hollow annular boss, the diameters of which are adapted to the interior of the first annular groove and the interior of the second annular groove, respectively, and the annular base and the annular boss are respectively engaged inside the first annular groove and the second annular groove.

[0010] Preferably, the radial support mechanism includes an annular side retaining ring, a roller support ring, and a second cylindrical roller. One side of the annular side retaining ring is connected to the swing output flange, and the other side of the annular side retaining ring is connected to the roller support ring. The roller support ring is rotatably provided with a second cylindrical roller. A plurality of second cylindrical rollers are circumferentially arranged on the roller support ring, and the axis of each second cylindrical roller is oriented toward the axis of the swing shaft.

[0011] Preferably, the roller support ring is provided with a plurality of mounting grooves, and a second columnar roller is rotatably provided inside each mounting groove. The mounting groove is positioned so as not to contact the second columnar roller, and the surface of each second columnar roller is in contact with the annular base.

[0012] Preferably, the cylinder housing is further provided with an oil filling groove coaxial with the swing shaft. A stator plate is fixedly installed inside the oil filling groove. Several blades and a limiting plate are also fixedly installed on the side wall of the swing shaft. The volume of oil between the side wall of the stator plate and the side wall of the limiting plate determines the rotation angle of the swing shaft.

[0013] Preferably, the cylinder housing includes a support housing and detachable housing end caps disposed on both sides of the support housing. The connection between each housing end cap and the cylinder housing is sealed by a number of sealing rings. Each swing output flange is also sealed to the side wall of the housing end cap by a sealing ring, and the swing output flange can rotate relative to the side wall of the cylinder housing. The detachable design of the red support housing and housing end cap makes it very convenient to disassemble and repair internal components (such as blades, stator plates, and support mechanisms) without damaging the overall structure, which greatly reduces maintenance costs and downtime.

[0014] 1. The axial support mechanism bears the axial load transmitted from the external force to the swing shaft; the radial support mechanism bears the radial load transmitted from the external force to the swing output flange. These two functionally independent mechanisms are highly integrated within the narrow installation gap formed by the end inner wall of the cylinder housing, the swing shaft, and the swing output flange, thus maximizing space utilization. 2. The axial support mechanism uses a first cylindrical roller with its axis parallel to the swing shaft. Unlike the point contact of the deep groove ball bearing, the cylindrical roller has a line contact with the fourth annular groove. Its large contact area and strong load-bearing capacity can effectively withstand the large axial force generated by the pressure oil on the blades and limit plates, fundamentally avoiding premature failure caused by excessive axial force. At the same time, to address the problem of inconsistent contact angle under combined loads, the first cylindrical roller bears the pure axial force, and the second cylindrical roller bears the radial force. Neither of them suffers from the deterioration of the stress state caused by combined loads. The stress state between the roller and the raceway is always in the optimal state, greatly delaying the occurrence of fatigue damage. 3. The second columnar rollers of the radial support mechanism are arranged circumferentially, with their axes all facing the axis of the swing shaft. They form dense line contact support with the annular base sidewall of the axial support sleeve. This layout provides radial support rigidity. The first columnar rollers of the axial support mechanism also provide axial support in a line contact manner, with extremely high rigidity. When facing working conditions such as frequent start-stop and reversing impacts in engineering machinery, this composite support system can effectively suppress the radial movement and axial displacement of the swing shaft, ensuring the positioning accuracy of the swing output flange and the smooth operation of the whole machine, and significantly improving the service life of the hydraulic cylinder under harsh working conditions. Attached Figure Description

[0015] Figure 1 This is a perspective view of the present utility model; Figure 2 This is a cross-sectional view of the present invention; Figure 3 For the present utility model in Figure 2 Enlarged view of region A in the image; Figure 4 This is a cross-sectional view of the present invention after one of the supporting shells has been removed; Figure 5 For the present utility model in Figure 4 Enlarged view of region B in the image; Figure 6 This is a cross-sectional view of the present invention after removing one of the supporting shells and the axial support sleeve; Figure 7 For the present utility model in Figure 6 Enlarged view of region C in the image; Figure 8 This is a cross-sectional view of the present invention.

[0016] The markings in the diagram are: 1. Cylinder housing; 11. Support housing; 12. Housing end cap; 111. First annular groove; 112. Second annular groove; 113. Third annular groove; 2. Swing shaft; 20. Blade; 21. Fourth annular groove; 22. Limiting plate; 3. Swing output flange; 4. Installation clearance; 5. Radial support mechanism; 51. Annular side retaining ring; 52. Roller support ring; 53. Second cylindrical roller; 521. Inner mounting groove; 6. Axial support mechanism; 61. Axial support sleeve; 62. First cylindrical roller; 611. Annular base; 612. Annular boss. Detailed Implementation

[0017] The present invention will be further described below with reference to the embodiments shown in the accompanying drawings: like Figure 1 , Figure 2 and Figure 3 As shown, a swing cylinder capable of withstanding axial and radial loads includes a cylinder housing 1 and a rotatable swing shaft 2 disposed inside the cylinder housing 1. The cylinder housing 1 includes a support housing 11 and detachable housing end caps 12 disposed on both sides of the support housing 11. The connection between each housing end cap 12 and the cylinder housing 1 is sealed by a sealing ring. The sidewall of the swing shaft 2 is also sealed to the interior of the housing end cap 12 by a sealing ring. The housing end cover 12 and the supporting housing 11 are detachably connected by bolts. This design makes it easier to inspect and maintain the internal components of the cylinder housing 1. Each swing output flange 3 is also sealed to the side wall of the housing end cover 12 by a sealing ring, and the swing output flange 3 can rotate relative to the side wall of the cylinder housing 1.

[0018] like Figure 8 As shown, in this embodiment, the cylinder housing 1 is further provided with an oil filling groove 14 coaxial with the swing shaft 2. A stator plate 15 is fixedly installed inside the oil filling groove 14. Several blades 20 and a limiting plate 22 are also fixedly installed on the side wall of the swing shaft 2. The volume of oil between the side wall of the stator plate 15 and the side wall of the limiting plate 22 determines the rotation angle of the swing shaft 2. During implementation, the limiting plate 22 abuts against the stator plate 15 after the blade 20 abuts against it, thereby controlling the rotation angle of the subsequent swing shaft 2. The oil filling tank 14 inside the cylinder housing 1 is a container for holding oil. The stator plate 15 fixed inside the oil filling tank 14 is a static separator, and the gap between the stator plate 15 and the limiting plate 22 divides the oil filling tank 14 into two independent working oil chambers.

[0019] The swing shaft 2 is the power output element. The blade 20 and the limiting plate 22 fixed on the swing shaft 2 are the core driving elements for the swing shaft 2 to rotate. The limiting plate 22 rotates with the swing shaft 2 and further divides the oil chamber separated by the stator plate 15 into an oil inlet chamber and an oil return chamber.

[0020] When pressurized oil enters the sealed oil chamber formed by the stator plate 15, blades 20, support housing 11, and housing end cap 12 from one oil port, the oil pressure acts directly on the side surface of the limiting plate 22. Since the stator plate 15 is fixed, the oil pressure cannot push it; therefore, the reaction force is entirely used to push the limiting plate 22, thereby driving the swing shaft 2 to generate rotational torque. As the position of the limiting plate 22 changes, the volume of the oil chamber on the opposite side decreases, and the oil within is squeezed out and discharged back to the oil tank from the other oil port.

[0021] The volume of oil between the side wall of the stator plate 15 and the side wall of the limiting plate 22 determines the rotation angle of the swing shaft 2. By controlling the volume of oil entering the oil chamber, the displacement angle, i.e. the rotation angle of the swing shaft 2, can be precisely controlled.

[0022] In this embodiment, the two ends of the swing shaft 2 are respectively provided with swing output flanges 3 that rotate with the swing shaft 2. Each swing output flange 3 is sealed to the side wall of the cylinder housing 1 and can rotate relative to the side wall of the cylinder housing 1. like Figure 2 As shown, since the swing output flange 3 and the swing shaft 2 are fixedly connected, the component or object to be driven is connected to the swing output flange 3, and the power output by the swing shaft 2 is transmitted to the designated component or object through the swing output flange 3. Since the swing output flange 3 has two parts, left and right, the swing output flange 3 is often subjected to axial and radial reaction forces when driving the component or object, and these forces are further transmitted to the swing shaft 2.

[0023] In order to achieve better stability, better support strength, excellent rotation effect and longer service life of the swing shaft 2 in the axial and radial directions, the gap between the end side wall of the swing shaft 2, the end inner wall of the cylinder housing 1 and the side wall of the swing output flange 3 is formed as the installation gap 4. The installation gap 4 is provided with a radial support mechanism 5 that provides radial support for the swing shaft 2 and an axial support mechanism 6 that provides axial support for the swing shaft 2. Please continue to refer to the reference. Figure 3 and Figure 5The inner walls of both ends of the cylinder housing 1 are provided with a first annular groove 111, a second annular groove 112 and a third annular groove 113 with different diameters. The interior of the first annular groove 111 is connected to the interior of the second annular groove 112. The two ends of the swing shaft 2 are provided with a fourth annular groove 21. Each radial support mechanism 5 is disposed between the first annular groove 111 and the fourth annular groove 21. Each axial support mechanism 6 is disposed between the first annular groove 111, the second annular groove 112 and the fourth annular groove 21. A sealing ring is also provided between the interior of each third annular groove 113 and the side wall of the swing shaft 2. like Figure 3 As shown, within the narrow space of the installation gap 4, since the radial support mechanism 5 is only located between the first annular groove 111 and the fourth annular groove 21, the side of the radial support mechanism 5 closest to the axial support mechanism 6 is used to support and guide the axial support mechanism 6. Furthermore, the axial support mechanism 6 is located between the first annular groove 111, the second annular groove 112, and the fourth annular groove 21, and the rollers inside the axial support mechanism 6 are in direct contact with the swing shaft 2. Therefore, while the axial support mechanism 6 provides axial support to the swing shaft 2, the swing shaft 2, when subjected to radial force, transmits the force to the radial support mechanism 5 through the swing output flange 3. The radial support mechanism 5 then provides radial support and guidance to both the axial support mechanism 6 and the swing output flange 3.

[0024] Please refer to the reference. Figure 4 and Figure 5 In this embodiment, each of the axial support mechanisms 6 includes an axial support sleeve 61 and a first cylindrical roller 62. The axial support sleeve 61 is hollow and is fitted inside the first annular groove 111 and the second annular groove 112. Both ends of the swing shaft 2 pass through the interior of the axial support sleeve 61. A plurality of first cylindrical rollers 62 capable of rolling are provided between the interior of the axial support sleeve 61 and the surface of the fourth annular groove 21. The axis of each first cylindrical roller 62 is parallel to the axis of the swing shaft 2. During implementation, whenever the swing output flange 3 is subjected to an externally generated axial thrust or tension during its rotation, these forces are transmitted and act on the swing shaft 2. Since the axis of the first cylindrical roller 62 is parallel to the axis of the swing shaft 2, the first cylindrical roller 62 supports and guides the fourth annular groove 21 at the end of the swing shaft 2. During the continuous rotation of the swing shaft 2, each first cylindrical roller 62 is in close contact with the fourth annular groove 21 and rotates simultaneously. This rolling support parallel to the axis has lower friction and better support.

[0025] Please refer to the reference. Figure 3 , Figure 6 and Figure 7In this embodiment, the axial support sleeve 61 includes a hollow annular base 611 and a hollow annular boss 612. The diameters of the annular base 611 and the annular boss 612 are respectively adapted to the interior of the first annular groove 111 and the interior of the second annular groove 112. The annular base 611 and the annular boss 612 are respectively engaged inside the first annular groove 111 and the second annular groove 112. With this configuration, the shape between the annular base 611 and the annular boss 612 fills the connection area between the first annular groove 111 and the second annular groove 112, allowing the two ends of the axial support sleeve 61 to abut against the interior of the second annular groove 112 and the side wall of the radial support mechanism 5, respectively. This ensures that when the swing output flange 3 and the swing shaft 2 are subjected to radial force, there is a gap between the side wall of the radial support mechanism 5 and the first cylindrical roller 62. Therefore, the radial support mechanism 5 is limited by the abutment of the axial support sleeve 61, preventing interference with the first cylindrical roller 62. This ensures that when both radial and axial forces are applied, both the radial support mechanism 5 and the axial support mechanism 6 can provide normal support and guidance.

[0026] Please continue to refer to this. Figure 6 and Figure 7 In this embodiment, the radial support mechanism 5 includes an annular side retaining ring 51, a roller support ring 52, and a second columnar roller 53. One side of the annular side retaining ring 51 is connected to the swing output flange 3, and the other side of the annular side retaining ring 51 is connected to the roller support ring 52. The roller support ring 52 is rotatably provided with a second columnar roller 53. A plurality of second columnar rollers 53 are circumferentially arranged on the roller support ring 52, and the axis of each second columnar roller 53 is oriented toward the axis of the swing shaft 2. During implementation, the radial force on the swing output flange 3 is transmitted to the annular side retaining ring 51 and the roller support ring 52. If the swing output flange 3 and the annular side retaining ring 51 are considered as a whole, and the housing end cover 12 and the axial support sleeve 61 are considered as another whole; During the process of the second cylindrical roller 53 on the roller support ring 52 providing radial support and guidance to the side wall of the axial support sleeve 61, it also effectively provides radial support and guidance to the swing output flange 3. As the swing shaft 2 drives the swing output flange 3 to rotate continuously, each second cylindrical roller 53 is in close contact with the side wall of the axial support sleeve 61 and rotates simultaneously. In addition, the axis of each second cylindrical roller 53 is oriented towards the axis of the swing shaft 2. Therefore, this rolling support also has lower radial friction and better support. In this embodiment, the roller support ring 52 is provided with a plurality of mounting inner grooves 521, and each mounting inner groove 521 is rotatably provided with a second columnar roller 53. The mounting inner groove 521 is positioned so as not to contact the second columnar roller 53, and the surface of each second columnar roller 53 is in contact with the annular base 611. With this setting, the installation position of the inner groove 521 ensures that the installation position and rotation position of the second columnar roller 53 cannot come into contact with the position of the first columnar roller 62, thus preventing any impact on the support and guiding effect of the first columnar roller 62 and the second columnar roller 53. Since the radial directions of both ends of the swing shaft 2 are limited by the swing output flange 3 and the housing end cover 12, the swing shaft 2 will not move radially during rotation.

[0027] The working principle and usage method of this utility model.

[0028] The stator plate 15 fixed inside the oil filling tank 14 is a static separator. The gap between the stator plate 15 and the limiting plate 22 divides the oil filling tank 14 into two independent working oil chambers.

[0029] The swing shaft 2 is the power output element. The blade 20 and the limiting plate 22 fixed on the swing shaft 2 are the core driving elements for the swing shaft 2 to rotate. The limiting plate 22 rotates with the swing shaft 2 and further divides the oil chamber separated by the stator plate 15 into an oil inlet chamber and an oil return chamber.

[0030] When pressurized oil enters the sealed oil chamber formed by the stator plate 15, blades 20, support housing 11, and housing end cap 12 from one oil port, the oil pressure acts directly on the side surface of the limiting plate 22. Since the stator plate 15 is fixed, the oil pressure cannot push it; therefore, the reaction force is entirely used to push the limiting plate 22, thereby driving the swing shaft 2 to generate rotational torque. As the position of the limiting plate 22 changes, the volume of the oil chamber on the opposite side decreases, and the oil within is squeezed out and discharged back to the oil tank from the other oil port.

[0031] The volume of oil between the side wall of the stator plate 15 and the side wall of the limiting plate 22 determines the rotation angle of the swing shaft 2. By controlling the volume of oil entering the oil chamber, the displacement angle, i.e. the rotation angle of the swing shaft 2, can be precisely controlled.

[0032] When the swing output flange 3 is subjected to an axial force (thrust or tension), the force is transmitted through the swing shaft 2 to the fourth annular groove 21 at its end. The first cylindrical roller 62 in the fourth annular groove 21 distributes the axial force to the axial support sleeve 61 through rolling contact, and it is ultimately borne by the cylinder housing 1. Since the first cylindrical roller 62 has line contact with the shaft, it has the advantages of high load-bearing capacity and high rigidity.

[0033] When the swing output flange 3 is subjected to a radial force (a force perpendicular to the axis), this force is transmitted to the roller support ring 52 through the annular side retaining ring 51. The second columnar rollers 53 arranged circumferentially on the ring (their axes all pointing towards the center of the shaft) roll accordingly, applying the radial force to the outer wall of the annular base 611 of the axial support sleeve 61, and ultimately transmitting it to the cylinder housing 1. This radial roller arrangement provides uniform and highly rigid radial support.

[0034] The axial support mechanism 6 and the radial support mechanism 5 are ingeniously integrated in the narrow installation gap 4. The two are structurally linked through the axial support sleeve 61, but the force paths are clear and independent and do not interfere with each other, thus ensuring the stable rotation of the swing shaft 2 under complex working conditions.

[0035] The specific embodiments described herein are merely illustrative examples illustrating the spirit of this utility model. Those skilled in the art to which this utility model pertains may make various modifications or additions to the described specific embodiments or use similar methods to replace them, without departing from the spirit of this utility model or exceeding the scope defined by the appended claims.

Claims

1. A swing cylinder capable of bearing axial and radial loads, comprising a cylinder housing (1) and a rotatable swing shaft (2) disposed inside the cylinder housing (1), characterized in that, The two ends of the swing shaft (2) are respectively provided with swing output flanges (3) that rotate with the swing shaft (2). Each swing output flange (3) is sealed to the side wall of the cylinder housing (1) and can rotate relative to the side wall of the cylinder housing (1). The gap between the end side wall of the swing shaft (2), the end inner wall of the cylinder housing (1) and the side wall of the swing output flange (3) forms an installation gap (4). The installation gap (4) is provided with a radial support mechanism (5) that provides radial support to the swing shaft (2) and an axial support mechanism (6) that provides axial support to the swing shaft (2).

2. The swing cylinder capable of withstanding axial and radial loads according to claim 1, characterized in that, The inner walls of both ends of the cylinder housing (1) are provided with a first annular groove (111), a second annular groove (112) and a third annular groove (113) of different diameters. The interior of the first annular groove (111) is connected to the interior of the second annular groove (112). Both ends of the swing shaft (2) are provided with a fourth annular groove (21). Each radial support mechanism (5) is located between the first annular groove (111) and the fourth annular groove (21). Each axial support mechanism (6) is located between the first annular groove (111), the second annular groove (112) and the fourth annular groove (21). A sealing ring is also provided between the interior of each third annular groove (113) and the side wall of the swing shaft (2).

3. The swing cylinder capable of withstanding axial and radial loads according to claim 2, characterized in that, Each of the axial support mechanisms (6) includes an axial support sleeve (61) and a first cylindrical roller (62). The axial support sleeve (61) is hollow and is fitted inside the first annular groove (111) and the second annular groove (112). Both ends of the swing shaft (2) pass through the interior of the axial support sleeve (61). A plurality of first cylindrical rollers (62) capable of rolling are provided between the interior of the axial support sleeve (61) and the surface of the fourth annular groove (21). The axis of each first cylindrical roller (62) is parallel to the axis of the swing shaft (2).

4. The swing cylinder capable of withstanding axial and radial loads according to claim 3, characterized in that, The axial support sleeve (61) includes a hollow annular base (611) and a hollow annular boss (612). The diameters of the annular base (611) and the annular boss (612) are respectively adapted to the interior of the first annular groove (111) and the interior of the second annular groove (112). The annular base (611) and the annular boss (612) are respectively locked inside the first annular groove (111) and the second annular groove (112).

5. The swing cylinder capable of withstanding axial and radial loads according to claim 4, characterized in that, The radial support mechanism (5) includes an annular side retainer (51), a roller support ring (52), and a second columnar roller (53). One side of the annular side retainer (51) is connected to the swing output flange (3), and the other side of the annular side retainer (51) is connected to the roller support ring (52). The roller support ring (52) is rotatably provided with a second columnar roller (53). A plurality of second columnar rollers (53) are circumferentially arranged on the roller support ring (52), and the axis of each second columnar roller (53) is oriented toward the axis of the swing shaft (2).

6. The swing cylinder capable of withstanding axial and radial loads according to claim 5, characterized in that, The roller support ring (52) is provided with a plurality of mounting grooves (521), and each mounting groove (521) is provided with a second columnar roller (53) that can rotate inside. The mounting groove (521) is positioned so as not to contact the second columnar roller (53) and the surface of each second columnar roller (53) is in contact with the annular base (611).

7. The swing cylinder according to claim 1, characterized in that, The cylinder housing (1) is also provided with an oil filling groove (14) coaxial with the swing shaft (2). A stator plate (15) is fixedly installed inside the oil filling groove (14). Several blades (20) and a limiting plate (22) are also fixedly installed on the side wall of the swing shaft (2). The oil volume between the side wall of the stator plate (15) and the side wall of the limiting plate (22) determines the rotation angle of the swing shaft (2).

8. The swing cylinder according to claim 7, characterized in that, The cylinder housing (1) includes a support housing (11) and detachable housing end caps (12) disposed on both sides of the support housing (11). The connection between each housing end cap (12) and the cylinder housing (1) is sealed by several sealing rings. Each swing output flange (3) is also sealed to the side wall of the housing end cap (12) by sealing rings, and the swing output flange (3) can rotate relative to the side wall of the cylinder housing (1).

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