CN219655259U - Actuator - Google Patents

Abstract

The utility model provides an actuator, relates to the technical field of sealing of rotating shafts, and is designed for solving the problem of poor sealing of the actuator. The actuator comprises a rotating shaft and a sealing support assembly, wherein an axial air passage and a radial air passage communicated with the axial air passage are arranged in the rotating shaft, the sealing support assembly is provided with a first inner flange part, an annular air cavity is formed between the first inner flange part and the peripheral surface of the rotating shaft, the two axial ends of the annular air cavity are sealed by an inner sealing ring sleeved on the rotating shaft, the sealing support assembly is provided with a first accommodating groove, and the inner sealing ring is positioned in the first accommodating groove. The actuator provided by the utility model can improve the tightness of the actuator.

Description

Actuator

Technical Field

The utility model relates to the technical field of sealing of rotating shafts, in particular to an actuator.

Background

With the development of technology, industrial automation equipment is rapidly moving into large enterprises, especially technical fields such as semiconductors, electronic equipment processing, biopharmaceuticals and the like or labor-intensive enterprises, and the degree of automation is higher and higher. Actuators are often required to execute various actions on an automation production line of an enterprise so as to save human resources and improve production efficiency.

However, in the prior art, some actuators utilize pressure changes at the air passage port inside the rotating shaft to realize negative pressure suction parts, but an air passage leading to the air passage inside the rotating shaft may have a condition of loose sealing on the surface of the rotating shaft, so that the risk of dropping an object sucked by the end part of the rotating shaft is increased, and the production line cannot run smoothly.

Disclosure of Invention

The first object of the present utility model is to provide an actuator, which solves the technical problem of poor sealing of the existing actuator.

The utility model provides an actuator, which comprises a rotating shaft and a sealing support assembly, wherein an axial air passage and a radial air passage communicated with the axial air passage are arranged in the rotating shaft, the sealing support assembly is provided with a first inner flange part, an annular air passage is formed between the first inner flange part and the peripheral surface of the rotating shaft, the two axial ends of the annular air passage are sealed by an inner sealing ring sleeved on the rotating shaft, the sealing support assembly is provided with a first accommodating groove, and the inner sealing ring is positioned in the first accommodating groove.

The actuator provided by the utility model has the beneficial effects that:

through the cover establish the inner seal circle in the pivot, can seal the annular air flue between seal support assembly and the pivot, improve the leakproofness of executor to prevent annular air flue gas leakage. In particular, in the case of sucking the parts under negative pressure, it is possible to prevent the sucked parts from falling off due to loss of negative pressure in the annular air passage.

In a preferred technical scheme, the width of the first accommodating groove is larger than the axial dimension of the inner sealing ring.

In a preferred technical solution, the width of the first accommodating groove is 1.2 times or less than the axial dimension of the inner seal ring, and the first accommodating groove is configured as: when the annular air passage is in positive air pressure, the inner sealing ring is abutted with the groove wall of the pair of first accommodating grooves, which is farthest from each other; when the annular air passage is in negative air pressure, the inner sealing ring is abutted with the nearest groove wall of the pair of first accommodating grooves; when the annular air passage is in natural air pressure, the inner sealing ring is separated from the opposite groove walls of the first accommodating groove.

In a preferred technical scheme, the inner sealing ring and the bottom of the first accommodating groove are radially spaced, and the inner peripheral surface of the inner sealing ring is abutted to the rotating shaft.

In a preferred technical scheme, the seal support assembly comprises a shell, a first seal support piece and a second seal support piece, wherein the first seal support piece and the second seal support piece are fixedly arranged relative to the shell, each second seal support piece is provided with a second inner flange portion, and the end face of the first inner flange portion and the opposite second inner flange portions form the first accommodating groove respectively.

In a preferred embodiment, the first seal support has an end face recess, and the second seal support has an end face projection, which is in close fit with the end face recess.

In the preferred technical scheme, the outer peripheral face of first seal support piece still is equipped with annular ventilation groove, annular ventilation groove with set up the annular chamber of casing corresponds the setting, first seal support piece be equipped with the radial air vent of annular air flue intercommunication, annular ventilation groove's width is greater than the aperture of radial air vent.

In a preferred technical scheme, the number of the radial vent holes is a plurality of, and the radial vent holes are uniformly distributed along the circumferential direction of the first sealing support piece.

In the preferred technical scheme, the outer peripheral surface of first seal support piece still is equipped with the second accommodation groove, the second accommodation groove holds the outer sealing washer, the second accommodation groove is located the axial both sides of annular ventilation groove.

In a preferred embodiment, the second seal support further has a sleeve portion that abuts against a bearing outer ring of a rolling bearing fixedly provided in the housing.

In a preferred technical scheme, a gas containing space is formed between the second sealing support and the rotating shaft.

Drawings

In order to more clearly illustrate the technical solutions of embodiments or background art of the present utility model, the drawings that are needed in the description of the embodiments or background art will be briefly described below, and it is apparent that the drawings in the following description are only embodiments of the present utility model, and that other drawings can be obtained according to the provided drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic view of a partial structure of an actuator according to an embodiment of the present utility model;

fig. 2 is a schematic diagram of a partial structure of an actuator provided in an embodiment of the present utility model in a state in which an annular airway is in a positive pressure state;

fig. 3 is a schematic diagram of a partial structure of an actuator provided in an embodiment of the present utility model in a state in which an annular air passage is under negative pressure;

FIG. 4 is a cross-sectional view of a first seal support in an actuator provided in an embodiment of the present utility model;

FIG. 5 is a cross-sectional view of a second seal support in an actuator provided in an embodiment of the present utility model;

fig. 6 is a cross-sectional view of an actuator provided in an embodiment of the present utility model perpendicular to the axial direction of the shaft at the radial vent.

Reference numerals illustrate:

100-rotating shaft; 110-axial airway; 120-radial airway; 200-an inner sealing ring; 310-a first seal support; 311-a first inner flange portion; 312-a first accommodation groove; 313-annular vent slots; 314-radial vent holes; 315-end face depression; 320-a second seal support; 321-a second inner flange portion; 322-a second accommodation groove; 323-a sleeve portion; 324-end face projections; 325-gas containing space; 330-a housing; 331-an annular cavity; 400-an outer sealing ring; 500-annular airway; 600-rolling bearings; 610-bearing outer race.

Detailed Description

In order that the above objects, features and advantages of the utility model will be readily understood, a more particular description of the utility model will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the utility model.

Fig. 1 is a schematic partial structure of an actuator according to an embodiment of the present utility model, where fig. 1 is a partial enlarged area of an inner seal ring located in a first accommodating groove, and fig. 2 and 3, which will be described later, are also the same partial enlarged areas. As shown in fig. 1, the actuator provided in the first embodiment of the present utility model includes a rotating shaft 100 and a seal support assembly, wherein an axial air passage 110 and a radial air passage 120 communicating with the axial air passage 110 are provided in the rotating shaft 100, the seal support assembly has a first inner flange portion 311, an annular air passage 500 is formed between the first inner flange portion 311 and a circumferential surface of the rotating shaft 100, two axial ends of the annular air passage 500 are sealed by an inner seal ring 200 sleeved on the rotating shaft 100, the seal support assembly has a first accommodating groove 312, and the inner seal ring 200 is located in the first accommodating groove 312.

Specifically, the actuator of the present embodiment may further include a housing 330, which is described below, to linearly move in addition to the rotation of the rotating shaft 100, and the sealing support assembly drives the rotating shaft 100 to linearly move, so as to extend and retract the rotating shaft 100. The rotating shaft 100 extends out to be in contact with the adsorbed part, then negative pressure is formed in the axial air passage 110, the part can be adsorbed on the end part of the rotating shaft 100, and the actuator can drive the part to move after the rotating shaft 100 retracts. If the actuator moves to the release position, the shaft 100 is extended, positive pressure greater than atmospheric pressure is applied to the axial air passage 110, the adsorption force of the end of the shaft 100 on the part is lost, and the part is released.

In this embodiment, the axial air passages 110 of the rotating shaft 100 extend to an end of the rotating shaft 100 extending out of the housing 330, and the radial air passages 120 may be arranged on the rotating shaft 100 in two groups, each group has two radial air passages 120, and the two radial air passages 120 of each group are arranged 180 ° apart and located at the same axial position on the rotating shaft 100. Specifically, the two radial air passages 120 of each group have the same diameter, i.e., a group of two radial air passages 120 may be machined by drilling from one side of the rotating shaft 100 and penetrating the rotating shaft 100 along the diameter of the rotating shaft 100. By adopting the arrangement, the processing is convenient, and the manufacturing cost is reduced. Accordingly, the position and effective length of annular airway 500 covers two sets of radial airways 120, i.e., the length of annular airway 500 is greater than the sum of the center distance of two sets of radial airways 120, the radius of one set of radial airways 120, and the radius of the other set of radial airways 120.

While the two sets of radial air passages 120 may have the same circumferential position on the shaft 100, i.e., the two sets of radial air passages 120 have the same projected position as viewed inwardly along the protruding end of the shaft 100. Furthermore, in this embodiment, each radial airway 120 has a diameter that is smaller than the diameter of axial airway 110. In this embodiment, the diameters of the two sets of radial airways 120 are preferably the same.

In this embodiment, the annular air passage 500 may be formed in the following manner: the seal support assembly is spaced from the outer circumferential surface of a section of the shaft 100, which forms an annular air channel 500. More specifically, in the present embodiment, a part of the outer peripheral surface of the rotating shaft 100 inside the annular air channel 500 has the same outer diameter as the outer peripheral surfaces of the two sides of the part along the axial direction, and the radius of the area of the position corresponding to the part of the seal supporting component is larger than that of the part. In addition, compared with the scheme of forming the annular air passage 500 by providing the annular groove on the rotating shaft 100, the diameter variation generated when the inner sealing ring 200 is mounted on the rotating shaft 100 or dismounted from the rotating shaft 100 is reduced, and the inner sealing ring 200 is convenient to mount and dismount.

Through the cover establish the inner seal circle 200 on pivot 100, can seal the annular air flue 500 between seal support assembly and the pivot 100, improve the leakproofness of executor to prevent annular air flue 500 gas leakage. Particularly in the case of sucking the parts in the negative pressure condition, the loss of the negative pressure in the annular air passage 500 can be prevented from causing the sucked parts to fall.

As shown in fig. 1, the width of the first receiving groove 312 is preferably greater than the axial dimension of the inner seal ring 200.

More specifically, in this embodiment, the inner seal ring 200 may be an O-ring. The width of the first accommodating groove 312, that is, the dimension between the two groove walls of the first accommodating groove 312 in the axial direction of the rotating shaft 100, is greater than the dimension of the inner seal ring 200 in the axial direction of the rotating shaft 100 when the inner seal ring 200 abuts against the rotating shaft 100, and is not only greater than the dimension of the inner seal ring 200 in the natural state or the dimension of being flattened in the radial direction.

The width of the first accommodating groove 312 is set to be larger than the axial dimension of the inner sealing ring 200, in a natural state, the first accommodating groove 312 does not deform the inner sealing ring 200 in the axial direction, so that acting force between the sealing ring and the groove wall of the first accommodating groove 312 in a sealing ring bearing state is reduced, and when the annular air passage 500 is in different air pressure states, different positions of the inner sealing ring 200 are contacted with different positions of the sealing support assembly, so that the abrasion speed of a certain or certain specific areas of the inner sealing ring 200 can be reduced, the actual service life of the sealing ring depends on the abrasion degree of the most worn area, the abrasion degree of the certain or certain specific areas is reduced, and the service life of the inner sealing ring 200 can be prolonged.

If the width of the first accommodating groove 312 is smaller than or equal to the axial dimension of the inner seal ring 200, both end faces of the inner seal ring 200 in the axial direction may be extruded by the groove wall of the first accommodating groove 312, and when the air pressure of the annular air channel 500 changes, the acting force of the groove wall on the seal ring is the acting force of the accommodating groove directly extruding the seal ring to deform, and the acting force of the groove wall on the seal ring due to the air pressure is the sum of the acting force of the groove wall on the seal ring. Furthermore, when the inner seal ring 200 rotates relative to the first accommodating groove 312, both end surfaces of the inner seal ring 200 will wear with the groove wall, and the wear speed will be faster due to the larger stress.

As shown in fig. 1-3, the width of the first receiving groove 312 is preferably 1.2 times or less the axial dimension of the inner seal ring 200, and the first receiving groove 312 is configured to: when the annular air passage 500 is at positive air pressure, the inner sealing ring 200 is abutted with the groove walls of the pair of first accommodating grooves 312 which are farthest from each other; when the annular air passage 500 is under negative air pressure, the inner sealing ring 200 is abutted with the nearest groove walls of the pair of first accommodating grooves 312; when the annular air passage 500 is under natural air pressure, the inner seal ring 200 is separated from the opposite groove walls of the first accommodating groove 312.

Since the inner seal ring 200 is not an absolute rigid body, its shape may be different in different pneumatic conditions. Specifically, when the annular air passage 500 is at positive air pressure, that is, when the air pressure in the annular air passage 500 is greater than the external air pressure, the air in the annular air passage 500 presses the inner seal rings 200 in the relatively far direction in the axial direction, so that the two inner seal rings 200 deform in the relatively far direction, that is, the inner seal ring 200 on the left side in fig. 2 abuts the second seal support 320 on the left side to the left, and the inner seal ring 200 on the right side in fig. 2 abuts the second seal support 320 on the right side to the right. The left second seal support 320 and the right second seal support 320 are the furthest groove walls of the pair of first receiving grooves 312.

Specifically, when the annular air passage 500 is under negative air pressure, that is, when the air pressure in the annular air passage 500 is smaller than the external air pressure, the two inner seal rings 200 are deformed in a relatively approaching direction, that is, the left seal ring in fig. 3 abuts right against the left end face of the first inner flange portion 311, and the right seal ring in fig. 3 abuts left and right against the right end face of the first inner flange portion 311. The left and right end surfaces of the first inner flange are the closest groove walls of the pair of first receiving grooves 312.

When the annular air passage 500 is under positive air pressure, the inner sealing ring 200 is abutted against the groove walls of the pair of first accommodating grooves 312, which are furthest apart, so that the air can be prevented from leaking outwards along the axial direction of the first accommodating grooves 312 when the annular air passage 500 is under positive pressure. When the annular air passage 500 is under negative air pressure, the inner seal ring 200 abuts against the opposite end surfaces of the first inner flange 311, so that the loss of the sucking action of the axial air passage 110 on the parts due to air leakage of the annular air passage 500 can be prevented, and the parts fall. When the annular air passage 500 is in a natural state, that is, when the air pressure in the annular air passage 500 is equal to the air pressure outside the annular air passage 500, the inner sealing ring 200 is separated from the opposite side wall of the first accommodating groove 312 and cannot contact with the first accommodating groove 312, and even if the inner sealing ring 200 rotates relative to the first accommodating groove 312, no abrasion occurs, so that the time proportion of the inner sealing ring 200 generated by abrasion in the rotating process of the rotating shaft 100 can be reduced, and the nominal service life of the inner sealing ring 200 is further prolonged. Wherein nominal service life of the inner seal ring 200 refers to the accumulation of the operating time of the actuator before the inner seal ring 200 is damaged.

As shown in fig. 1, the inner seal ring 200 is preferably spaced from the bottom of the first accommodation groove 312 in the radial direction, and the inner peripheral surface of the inner seal ring 200 abuts against the rotating shaft 100.

Specifically, in the present embodiment, the inner seal ring 200 is tied on the peripheral surface of the rotating shaft 100, and is not plugged at the bottom of the first accommodating groove 312 in a filling manner. The diameter of the bottom of the first accommodating groove 312 is not more than 10% greater than that of the inner sealing ring 200, and when the inner sealing ring 200 rotates at high speed, the radius of the inner sealing ring 200 increases due to the centrifugal effect, and the inner sealing ring 200 can be tightly attached to the bottom of the first accommodating groove 312, so that the sealing effect is enhanced. The inner seal ring 200 normally works within the air pressure range of-95 KPa to 1 MPa.

By doing so, the inner seal ring 200 is not in contact with the groove bottom of the first receiving groove 312 when the rotation shaft 100 rotates, and on one hand, abrasion of the position of the maximum radial dimension of the inner seal ring 200, which is an important factor of abrasion of the inner seal ring 200, can be eliminated. And when the rotation speed is the same, the larger the radius of the contact point and the rotation axis is, the higher the linear speed of the friction contact point is, the larger the friction heat effect is, and the more abrasion of the inner sealing ring 200 is easy to be increased. In this embodiment, the inner seal ring 200 is separated from the bottom of the first accommodating groove 312, so that the abrasion factor can be eliminated. In other words, in this embodiment, the radius of the inner seal ring 200 where the inner seal ring contacts the position having the relative rotational speed is reduced, so that the rotational speed of the rotating shaft can be made higher with the same allowable wear speed.

On the other hand, since the position of the maximum radial dimension of the inner seal ring 200 is separated from the groove bottom of the first accommodating groove 312, when the inner seal ring 200 is subjected to the air pressure in different directions, the factor that blocks the deformation of the inner seal ring along the axial direction is also obviously reduced under the action of the air pressure, which is beneficial to enabling the inner seal ring to move towards the groove wall of the first accommodating groove 312 more quickly under the action of the air pressure, thereby realizing the sealing quickly.

Fig. 2 is a schematic view of a partial structure of an actuator according to a first embodiment of the present utility model in a state in which an annular airway is in a positive pressure state; fig. 3 is a schematic view of a partial structure of an actuator provided in an embodiment of the utility model in a state in which an annular air passage is under negative pressure. As shown in fig. 1 to 3, preferably, the seal support assembly includes a housing 330, a first seal support 310 and a second seal support 320, each of the first seal support 310 and the second seal support 320 being fixedly disposed opposite to the housing 330, each of the second seal supports 320 having a second inner flange portion 321, and an end surface of the first inner flange portion 311 forming a first receiving groove 312 with the opposite second inner flange portion 321, respectively.

Specifically, based on the direction shown in fig. 1, the left end face of the first inner flange portion 311 and the right end face of the second inner flange portion 321 located on the left form the opposing groove wall of the first accommodating groove 312, and the inner peripheral face side adjacent to the left of the left end face of the first inner flange portion 311 forms the groove bottom of the first accommodating groove 312. The right end face of the first inner flange portion 311 forms the opposing groove wall of the other first accommodation groove 312 with the left end face of the second inner flange portion 321 located on the right side, and the inner peripheral face side adjacent to the right side of the right end face of the first inner flange portion 311 forms the groove bottom of the other first accommodation groove 312.

By arranging the first seal support 310 and the second seal support 320 respectively and forming the first accommodating groove 312 with the second inner flange 321 by using the end face of the first inner flange 311, the second seal support 320, one inner seal ring 200, the first seal support 310, the other seal ring and the other second seal support 320 can be assembled in sequence when assembling the parts on the rotating shaft 100, thereby facilitating assembly and avoiding the position deviation of the inner seal ring 200 with softer material.

Of course, in another implementation manner, the first seal support 310 and the second seal support 320 may be integrally provided with an integral part, however, in this arrangement manner, the inner seal ring 200 needs to be first embedded into the first accommodating groove 312 during the assembly process, and then the rotating shaft 100 is inserted into the seal support assembly, however, in this case, a gap between the inner peripheral surface of the second inner flange 321 of the integral part and the rotating shaft 100 needs to be smaller, so as to prevent the inner seal ring 200 from being blocked into the gap between the two parts during the assembly, which would result in the assembly being not in place.

As shown in fig. 1-5, preferably, the first seal support 310 has an end face recess 315 and the second seal support 320 has an end face protrusion 324, the end face protrusion 324 being a tight fit with the end face recess 315.

Since the radial maximum position of the inner seal ring 200 is located at the groove bottom of the first receiving groove 312 to be separated, when the annular air passage 500 is in the positive air pressure state, the inner seal ring 200 cannot seal the groove bottom of the first receiving groove 312 to the position adjacent to the second seal supporter 320, and by tightly fitting the end surface concave portion 315 with the end surface convex portion 324, air of the annular air passage 500 is prevented from leaking therefrom to achieve the sealing of the first seal supporter 310 and the second seal supporter 320.

Of course, in other implementations, since the annular airway 500 is in a positive air pressure state, it is the axial airway 110 that is vented to release the sucked up parts, even if there is some slight leakage at this time, that does not result in failure of the action. Moreover, the resistance of the relief feature is also much less than the resistance of the gap between the first seal support 310 and the second seal support 320, and the gas is primarily expelled from the axial gas passage 110, so even if it leaks, its leakage amount is negligible relative to the flow of gas expelled from the axial gas passage 110.

As shown in fig. 1 to 3, preferably, the outer circumferential surface of the first seal support 310 is further provided with an annular vent groove 313, the annular vent groove 313 is disposed corresponding to the annular cavity 331 provided in the housing 330, the first seal support 310 is provided with a radial vent hole 314 communicating the annular vent groove 313 with the annular air passage 500, and the width of the annular vent groove 314 is larger than the aperture of the radial vent hole 314.

By providing the annular vent groove 313 and the radial vent holes 314 communicating with the annular vent groove 313, air fed from the annular chamber 331 can be input into the annular air passage 500 without the first seal support 310 being assembled into the housing 330 at a specific angle, thereby reducing the difficulty of operation and improving the assembly efficiency.

Fig. 6 is a cross-sectional view of an actuator provided in an embodiment of the present utility model perpendicular to the axial direction of the shaft at the radial vent. As shown in fig. 6, preferably, the number of radial ventilation holes 314 is plural, and the plurality of radial ventilation holes 314 are uniformly distributed along the circumferential direction of the first seal support 310.

Specifically, in this embodiment, the number of radial ventilation holes 314 on the first seal support 310 may be four, and the four radial ventilation holes 314 have the same axial position and are uniformly distributed at intervals of 90 °.

The plurality of radial ventilation holes 314 uniformly distributed along the circumferential direction of the first sealing support 310 can make the airflow flowing into or out of the annular air passage 500 from the radial ventilation holes 314 more uniform, so that the flow direction in the axial air passage 110 is more accurate finally, the change of the position of the part caused by the deviation of the airflow direction when the part is sucked or released is reduced, and the precision of grabbing and releasing the part is improved.

As shown in fig. 1 to 3, preferably, the outer circumferential surface of the first seal support 310 is further provided with a second receiving groove 322, the second receiving groove 322 receiving the outer seal ring 400, the second receiving groove 322 being located at both sides of the annular ventilation groove 313 in the axial direction.

Specifically, the second receiving groove 322 is provided at one of both axial ends of the annular ventilation groove 313, and the outer seal ring 400 of the second receiving groove 322 is in contact with both the inner circumferential surface of the housing 330 and the groove bottom of the second receiving groove 322.

By providing the second receiving groove 322 to receive the outer packing 400, it is possible to prevent the negative pressure suction failure caused by air leakage of the actuator when sucking the parts, and the parts are dropped.

As shown in fig. 1 to 3, the second seal support 320 preferably further has a sleeve portion 323, and the sleeve portion 323 abuts against the bearing outer race 610 of the rolling bearing 600 fixedly provided to the housing 330.

In general, the outer bearing ring 610 of the rolling bearing 600 is in an interference fit with the housing 330, i.e., the outer bearing ring 610 of the rolling bearing 600 is fixedly disposed in the housing 330. While abutting the sleeve portion 323 with the bearing outer race 610 of the rolling bearing 600, both the second seal support 320 and the first seal support 310 may be kept fixedly disposed with the housing 330.

As shown in fig. 1 to 3, it is preferable that the second seal support 320 forms an air accommodating space 325 with the rotation shaft 100.

In fig. 1 to 3, the space between the sleeve portion 323 of the second seal support 320 located at the left side in the drawing and the rotating shaft 100 forms a major part of the air accommodating space 325, and the space between the second inner flange portion 321 at the left side and the rotating shaft 100 may also form a part of the air accommodating space 325. The space between the sleeve portion 323 on the right side in the drawing and the rotating shaft 100 may be a part of the air accommodating space 325 although the axial length is short, and the space between the second inner flange portion 321 on the right side and the rotating shaft 100 may be a part of the air accommodating space 325.

In this embodiment, the rolling bearing 600 may be a deep groove ball bearing with a dust cover to accommodate grease in the outer ring 610 and the inner ring, and since the rolling bearing 600 has a certain sealing function, the second seal support 320 has an air-accommodating space between the rotating shaft 100 and the rolling bearing 610, and air pressure is also present in the air-accommodating space, which can play a role in buffering, thereby avoiding impact caused by abrupt change of air pressure.

Although the present utility model is disclosed above, the present utility model is not limited thereto. Various changes and modifications may be made by one skilled in the art without departing from the spirit and scope of the utility model, and the scope of the utility model should be assessed accordingly to that of the appended claims.

Finally, it is further noted that relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.

In the above embodiments, descriptions of orientations such as "up", "down", and the like are shown based on the drawings.

The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present utility model. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the utility model.

Thus, the present utility model is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims (10)

1. The utility model provides an executor, its characterized in that includes pivot and seal support assembly, be equipped with axial air flue in the pivot and with the radial air flue of axial air flue intercommunication, seal support assembly has first inner flange portion, first inner flange portion with form annular air flue between the global of pivot, the axial both ends of annular air flue are sealed by the inner seal circle that the cover was established the pivot, seal support assembly has first accommodation groove, the inner seal circle is located in the first accommodation groove.

2. The actuator of claim 1, wherein the width of the first receiving groove is greater than the axial dimension of the inner seal ring.

3. The actuator of claim 2, wherein the width of the first receiving groove is 1.2 times or less the axial dimension of the inner seal ring, the first receiving groove configured to: when the annular air passage is in positive air pressure, the inner sealing ring is abutted with the groove wall of the pair of first accommodating grooves, which is farthest from each other; when the annular air passage is in negative air pressure, the inner sealing ring is abutted with the nearest groove wall of the pair of first accommodating grooves; when the annular air passage is in natural air pressure, the inner sealing ring is separated from the opposite groove walls of the first accommodating groove.

4. The actuator according to claim 2 or 3, wherein the inner seal ring is spaced from the groove bottom of the first accommodation groove in a radial direction, and an inner peripheral surface of the inner seal ring abuts against the rotation shaft.

5. The actuator of claim 2, wherein the seal support assembly comprises a housing, a first seal support and a second seal support, each of the first seal support and the second seal support being fixedly disposed relative to the housing, each of the second seal supports having a second inner flange portion, an end face of the first inner flange portion forming the first receiving channel with the opposing second inner flange portion, respectively.

6. The actuator of claim 5, wherein the first seal support has an end face recess and the second seal support has an end face projection that is a tight fit with the end face recess.

7. The actuator of claim 5, wherein the outer peripheral surface of the first seal support is further provided with an annular vent groove disposed in correspondence with an annular cavity provided in the housing, the first seal support being provided with a radial vent hole communicating with the annular air passage, the annular vent groove having a width greater than a bore diameter of the radial vent hole.

8. The actuator of claim 7, wherein the outer peripheral surface of the first seal support is further provided with a second receiving groove, the second receiving groove receiving an outer seal ring, the second receiving groove being located on both axial sides of the annular vent groove.

9. The actuator of claim 5, wherein the second seal support further has a sleeve portion that abuts a bearing outer race of a rolling bearing fixedly disposed on the housing.

10. The actuator of claim 9, wherein the second seal support and the shaft form a gas-containing space therebetween.