阅读说明：本技术 一种双向旋转逆止器及具有其的永磁滚筒 (Bidirectional rotation backstop and permanent magnet roller with same ) 是由 高冠华 于 2019-11-27 设计创作，主要内容包括：本申请公开了一种双向旋转逆止器及具有其的永磁滚筒,所述双向旋转逆止器包括：外壳、内圈、外圈、转矩传递组件、至少一个外盘及至少一个内盘；外壳与旋转部件连接,内圈固定不动,转矩传递组件设置在内圈与外圈之间,用于实现外圈相对内圈的单向旋转；外盘和内盘设置在外壳与外圈之间,通过调整外盘与内盘的结合状态,可实现外壳相对内圈自由转动或传递转矩。所述永磁滚筒包含如上所述的双向旋转逆止器。本申请的优点是：双向旋转逆止器内圈固定,外圈旋转,与现有逆止器结构恰好相反,并解决了传统逆止器只能单向旋转的限制,当需要逆止器反向旋转时,通过调整外盘与内盘的结合状态,即可实现；同时解决了永磁滚筒在启动时需要反转的问题。(The application discloses two-way rotation backstop and have its permanent magnetism cylinder, two-way rotation backstop includes: the torque transmission assembly comprises a shell, an inner ring, an outer ring, a torque transmission assembly, at least one outer disc and at least one inner disc; the outer shell is connected with the rotating component, the inner ring is fixed, and the torque transmission component is arranged between the inner ring and the outer ring and used for realizing the unidirectional rotation of the outer ring relative to the inner ring; the outer disc and the inner disc are arranged between the outer shell and the outer ring, and the outer shell can freely rotate relative to the inner ring or transmit torque by adjusting the combination state of the outer disc and the inner disc. The permanent magnet drum comprises the bidirectional rotation backstop. The application has the advantages that: the inner ring of the bidirectional rotation backstop is fixed, the outer ring rotates, the structure is just opposite to that of the traditional backstop, the limitation that the traditional backstop can only rotate in one direction is solved, and when the backstop needs to rotate in the reverse direction, the effect can be realized by adjusting the combination state of the outer disc and the inner disc; meanwhile, the problem that the permanent magnet roller needs to be reversed when being started is solved.)

1. A bidirectional rotary backstop, comprising:

a housing (1) for connection to a rotating member and for rotation about an axis of rotation;

the inner ring (2) is arranged in the shell (1) and is fixed;

an outer ring (3), the outer ring (3) being disposed in the housing (1) and radially outward of the inner ring (2);

a torque transfer assembly (7) disposed between the inner race and the outer race, the outer race being freely rotatable relative to the inner race in a first rotational direction, the torque transfer assembly being configured to couple the inner race and the outer race and prevent rotation of the outer race relative to the inner race in a second rotational direction;

at least one outer disc (4), said outer disc (4) being connected to a radially inner surface of said housing and being freely movable in the axial direction;

at least one inner disc (5), said inner disc (5) being connected to a radially outer surface of said inner ring and being freely movable in the axial direction;

the outer disc and the inner disc have a coupled state in which torque can be transmitted therebetween and a decoupled state; in the separated state, the outer disc can freely rotate relative to the inner disc;

the housing (1) and the outer ring are provided with a support in a radial direction such that the housing is free to rotate relative to the outer ring; or the shell (1) and the inner ring are provided with supports in the radial direction, so that the shell can freely rotate relative to the inner ring.

2. The bidirectional rotary backstop of claim 1, further comprising:

the pushing mechanism (6) is fixedly connected with the inner ring and used for mutually switching the outer disc and the inner disc between a combined state and a separated state; and a thrust bearing or a thrust needle roller and a retainer assembly are arranged between the contact surfaces of the pushing mechanism and the inner disc or the outer disc.

3. The bidirectional rotary backstop of claim 2 wherein said urging mechanism comprises:

a piston (61) having one axial end for applying an axial force to the outer or inner disc;

a spring (62) for generating an axial force in the axial direction to urge the piston in the axial direction toward the outer or inner disc.

4. The bidirectional rotary backstop of claim 3 wherein said urging mechanism further comprises:

a housing (63) forming an annular oil reservoir chamber (64) with the piston;

and the pump station is communicated with the annular oil storage cavity through the shell, and is used for injecting hydraulic oil into the annular oil storage cavity so as to overcome the axial force applied by the piston and make the piston move towards the direction far away from the outer disc or the inner disc.

5. The bidirectional rotary backstop of claim 4 wherein said urging mechanism further comprises:

a thrust adjustment mechanism (65) fixedly connected with the inner ring and the housing (63);

a plurality of springs (62) are uniformly distributed in the circumferential direction of the piston, and a pressing ring (66) is arranged at one end, far away from the outer disc or the inner disc, of each spring;

the thrust adjusting mechanism (65) is provided with an adjusting screw (68) at a position corresponding to each spring, and the adjusting screw is used for adjusting the compression amount of the spring.

6. The bidirectional rotary backstop of claim 5 wherein said urging mechanism further comprises: the abrasion indicating pin, abrasion indicating pin one end with piston is with detachable mode fixed connection, and the other end passes along the axis direction thrust adjustment mechanism (65) and outwards stretches out a section length, abrasion indicating pin is provided with the scale mark along its axial.

7. The bidirectional rotary backstop of claim 1, further comprising:

the first end cover (11) is fixedly connected with the axial end face of the shell (1), and a rolling bearing is arranged between an inner hole of the first end cover and the inner ring.

8. The bidirectional rotary backstop of claim 7 wherein axial sides of said outer race are provided with thrust bearings or thrust needles and retainer assemblies.

9. The bidirectional rotation brake of claim 4, wherein a rolling bearing or a copper sleeve is disposed radially between the outer shell and the housing.

10. A permanent magnet drum, characterized in that it comprises a bidirectional rotation backstop as claimed in any one of claims 1 to 9.

Technical Field

The application relates to the technical field of backstops, in particular to a bidirectional rotating backstop and a permanent magnet roller with the same.

Background

In the field of material transport, in particular when bulk material is transported by means of conveyors, it is often necessary to limit the direction of material transport, for example, inclined belt conveyors. During normal transported substance material, the conveyer upwards moves, when equipment trouble or power failure suddenly appear, needs the reverse operation of restriction conveyer to prevent system damage or personnel's injury.

With the development of industrial technology, the driving technology is also updated at present. The driving system is updated to direct drive of the roller from the original motor acceleration and deceleration driving roller, namely the current permanent magnet roller. The permanent magnet roller is opposite to the traditional roller in structure, a roller shaft of the traditional roller is fixedly connected with a roller body, the general roller shaft extends out of two axial end faces of the roller body, one end of the roller shaft is connected with an output shaft of a speed reducer, an output shaft at the other end can be used for installing a backstop, an inner ring of the backstop and the roller shaft rotate synchronously, and an outer ring of the backstop is limited on a base through a force arm. When the drum normally works, the drum shaft and the drum body synchronously rotate, the inner ring of the backstop synchronously rotates along with the drum shaft, and when the drum trends to reversely rotate, the backstop plays a role to prevent the drum from reversely rotating.

And the structure of permanent magnetism cylinder is different with traditional cylinder structure, and the drum shaft both ends of permanent magnetism cylinder are fixed on the base, can not rotate, and the barrel is rotatory around the drum shaft, has just so appeared the first problem: the backstop has no mounting position and the drum shaft is stationary.

In addition, since the driving principle of the permanent magnet drum is different from the prior art, another problem exists in the starting of the permanent magnet drum: the barrel of permanent magnetism cylinder can have the condition of reversal, if reuse the backstop of original structure, the backstop will directly prevent the rotation of cylinder, leads to unable normal start.

When a plurality of backstops are used, the stress of the plurality of backstops has asynchronism, so that the model selection coefficient of each backstop is overlarge; even if the types of the backstops are enlarged, if a plurality of backstops have larger installation errors during installation, the backstops stressed firstly still can be overloaded, and the other backstops are not stressed, so that the backstops are damaged quickly.

The problem four is that the permanent magnet roller can be directly driven, a motor and a speed reducer in the existing drive are not needed, and the permanent magnet roller can be directly installed on a driving machine, so that the force arm of the backstop also loses a limiting base, and the reverse backstop force cannot be provided.

Accordingly, a technical solution is desired to overcome or at least alleviate at least one of the above-mentioned drawbacks of the prior art.

Content of application

It is an object of the present application to provide a bidirectional rotation backstop and a permanent magnet drum having the same that overcomes or at least alleviates at least one of the above-mentioned deficiencies of the prior art.

To achieve the above object, the present application provides a bidirectional rotation brake, comprising:

a housing for connection with the rotary member and for rotation about the axis of rotation;

an inner ring disposed in the housing and fixed;

an outer race disposed in the housing and radially outward of the inner race; the outer ring is arranged radially outward of the inner ring;

a torque transfer assembly disposed between the inner race and the outer race, the outer race being free to rotate in a first rotational direction relative to the inner race, the torque transfer assembly being configured to couple the inner race and the outer race and prevent rotation of the outer race in a second rotational direction relative to the inner race;

at least one outer disc connected to a radially inner surface of the housing and freely movable in the axial direction;

at least one inner disc connected to a radially outer surface of the inner ring and freely movable in the axial direction;

the outer disc and the inner disc have a coupled state in which torque can be transmitted therebetween and a decoupled state; in the separated state, the outer disc can freely rotate relative to the inner disc;

the shell and the outer ring are provided with supports in the radial direction, so that the shell can freely rotate relative to the outer ring; or the outer shell and the inner ring are provided with supports in the radial direction, so that the outer shell can freely rotate relative to the inner ring.

Preferably, the bidirectional rotation check device further includes:

the pushing mechanism is fixedly connected with the inner ring and used for mutually switching the outer disc and the inner disc between a combined state and a separated state; and a thrust bearing or a thrust needle roller and a retainer assembly are arranged between the contact surfaces of the pushing mechanism and the inner disc or the outer disc.

Preferably, the pushing mechanism comprises:

a piston having one axial end for applying an axial force to the outer or inner disc;

a spring for generating an axial force in the axial direction to urge the piston in the axial direction toward the outer or inner disc.

Preferably, the pushing mechanism further comprises:

the shell and the piston form an annular oil storage cavity;

and the pump station is communicated with the annular oil storage cavity through the shell, and is used for injecting hydraulic oil into the annular oil storage cavity so as to overcome the axial force applied by the piston and make the piston move towards the direction far away from the outer disc or the inner disc.

Preferably, the pushing mechanism further comprises:

the thrust adjusting mechanism is fixedly connected with the inner ring and the shell;

a plurality of springs are uniformly distributed in the circumferential direction of the piston, and a pressing ring is arranged at one end, far away from the outer disc or the inner disc, of each spring;

the thrust adjusting mechanism is provided with an adjusting screw at a position corresponding to each spring, and the adjusting screw is used for adjusting the compression amount of the spring.

Preferably, the pushing mechanism further comprises: the piston is fixedly connected with the piston in a detachable mode, the other end of the piston penetrates through the thrust adjusting mechanism in the axial direction and extends out for a length, and the abrasion indicating pin is provided with scale marks along the axial direction of the abrasion indicating pin.

Preferably, the bidirectional rotation check device further includes:

the first end cover is fixedly connected with the axial end face of the shell, and a rolling bearing is arranged between an inner hole of the first end cover and the inner ring.

Preferably, the axial two sides of the outer ring are provided with a thrust bearing or a thrust needle roller and a retainer assembly.

Preferably, a rolling bearing or a copper bush is arranged between the outer shell and the housing in the radial direction.

The application also provides a permanent magnet drum, permanent magnet drum contains as above two-way rotation backstop.

The beneficial effect of this application lies in:

the bidirectional rotation backstop can be switched between a combined state and a separated state through the outer disc and the inner disc, and can meet rotation requirements in different directions; when torque does not need to be transmitted between the outer shell and the inner ring, the outer disk and the inner disk are in a separated state, and the outer shell can freely rotate relative to the inner ring in two directions. When torque needs to be transmitted between the outer shell and the inner ring, the outer disc and the inner disc are in a combined state, the outer shell can only freely rotate in one direction relative to the inner ring, and the other direction realizes a non-return effect; if the torque transmitted in the combined state of the outer disc and the inner disc exceeds a set value, the combined surface of the outer disc and the inner disc slips, and the backstop can be prevented from being damaged; if a plurality of backstops are installed, the load balancing among the plurality of backstops can be realized at the moment, so that the types of the plurality of backstops are reduced.

In addition, when the bidirectional rotation backstop works, the inner ring is fixed, and the shell rotates along with equipment needing backstopping, so that the bidirectional rotation backstop is just opposite to the structure of the existing backstop, and can be applied to the permanent magnet roller in the latest technology.

Moreover, this application is through first end cover and shell fixed connection to be provided with the bearing support between the hole of first end cover and inner circle, its advantage lies in having reduced the model of bearing, has reduced product cost.

Fourth, this application still is provided with the wearing and tearing indicator pin, if the back that appears wearing and tearing between outer dish and the inner disc, can show the wearing and tearing volume through the scale on the wearing and tearing indicator pin to can in time adjust the spring force, with the ability of guaranteeing transmission torque between outer dish and the inner disc.

Fifth, the two-way non-return ware that changes of this application need not additionally install the contrary arm of force of ending, simple structure, simple to operate.

Drawings

Fig. 1 is a schematic half-sectional structure view of a bidirectional rotation check device according to an embodiment of the present disclosure.

Fig. 2 is a schematic structural diagram of the connection between the bidirectional rotation check device and the permanent magnet drum.

1-a housing; 2-inner ring; 3-an outer ring; 4-outer disc; 5-inner disc; 6-a pushing mechanism; 7-a torque transfer assembly; 8-a bidirectional rotation backstop; 9-axis; 10-a permanent magnet drum; 11-a first end cap; 12-a rolling bearing; 13-positioning plate; 14-framework oil seal; 15-copper sheathing; 71-a limiting block; 31-thrust needle and cage assembly; 61-a piston; 62-a spring; 63-a housing; 64-an annular reservoir chamber; 65-a thrust adjustment mechanism; 66-a pressure ring; 67-the interface; 68-adjusting screws; 69-thrust roller pin and cage assembly.

Detailed Description

In order to make the implementation objects, technical solutions and advantages of the present application clearer, the technical solutions in the embodiments of the present application will be described in more detail below with reference to the drawings in the embodiments of the present application. In the drawings, the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The described embodiments are a subset of the embodiments in the present application and not all embodiments in the present application. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present application and should not be construed as limiting the present application. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application. Embodiments of the present application will be described in detail below with reference to the accompanying drawings.

In the description of the present application, it is to be understood that the terms "central," "longitudinal," "lateral," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in the orientation or positional relationship indicated in the drawings for convenience in describing the present application and for simplicity in description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be operated in a particular manner and are not to be considered limiting of the scope of the present application.

As shown in fig. 1, a schematic half-sectional structure of a bidirectional rotation check according to one embodiment completed by the present application is shown. The double-rotation check 8 is designed to be coupled to a rotating member rotating about an axis 9, defining the direction of rotation of said rotating member in normal operation as the forward direction. Upon activation of the rotary member, the rotary member may be allowed to counter-rotate about axis 9; after starting, under the normal working state of the rotating component, the rotating component is stopped from rotating reversely around the axis 9; the double rotation check 8 can again allow the rotation of the rotation part in the reverse direction about the axis 9 after the overload of the rotation part occurs in the operating state. The bidirectional rotation backstop 8 comprises a shell 1, an inner ring 2, an outer ring 3, a torque transmission assembly 7, an outer disc 4, an inner disc 5, a pushing mechanism 6, a first end cover 11, a rolling bearing 12, a positioning plate 13, a framework oil seal 14, a copper bush 15, a limiting block 71, a thrust roller pin and a retainer assembly 31.

The housing 1 is annular in configuration for connection with a rotating member and rotates about an axis of rotation 9; the rotating member may be a permanent magnet drum. The shell 1 can be directly and fixedly connected with a rotating part of the permanent magnet drum, and can also be connected with the rotating part of the permanent magnet drum through an intermediate part. The inner bore surface of the housing 1 is provided with internal splines for connection with the outer disc 4.

In this embodiment, the hole of shell 1 sets up to have the structure that the aperture changes in the axial, and middle part aperture is minimum for processing the internal spline, both ends aperture all is greater than the major diameter size of internal spline, the hole one end of shell 1 is through the cooperation of the tang of interior tang and first end cover 11 for radially supporting the shell, shell 1 through first end cover 11 with rotary part (being the rotating part of permanent magnetism cylinder) fixed connection. An inner hole at the other axial end of the shell 1 is used for installing a rolling bearing or a wear-resistant copper sleeve and radially supporting the shell 1, and a sealing element is arranged on the outer axial side (the side far away from the internal spline) of the rolling bearing or the wear-resistant copper sleeve.

The first end cover 11 can be regarded as a part of the housing 1 or an independent component, the first end cover 11 is fixedly connected with the housing 1 in a detachable mode through screws, a flange structure extends outwards in the radial direction after the first end cover 11 is matched with the housing 1, and a plurality of bolt holes are uniformly distributed on the circumference of the flange part and used for penetrating bolts to be connected with the rotating component. The inner hole of the first end cover 11 is further provided with a bearing mounting structure for mounting a rolling bearing 12, the rolling bearing 12 is axially positioned through a positioning plate 13, the positioning plate 13 is fixedly connected with the first end cover 11 through a screw, and a framework oil seal 14 is arranged at the inner hole of the positioning plate 13. The inner bore of the rolling bearing 12 is mounted on the inner ring 2 so that free rotation of the first end cap relative to the inner ring is achieved.

The inner ring 2 is arranged in the shell 1 and is fixed; in this embodiment, the structure of the inner ring 2 is the same as that of the inner ring of the prior backstop, the rolling bearing 12 is arranged between the first end cover 11 and the inner ring for supporting, and the first end cover 11 is fixedly and supportively connected with the outer shell, so that the outer shell 1 can rotate relative to the inner ring 2 through the support of the rolling bearing 12, and the inner ring 2 is stationary. In this embodiment, the inner ring 2 is connected to the drum shaft of the permanent magnet drum by a key. Two ends of the roller shaft are fixed by the base.

An outer ring 3 is provided in the housing 1 radially outward of the inner ring 2; outer lane 3 sets up to annular structure, and the excircle of outer lane 3 is provided with the external splines, the external splines is used for being connected with the inner disc. Thrust bearings or thrust roller pins and retainer assemblies are arranged on two axial end faces of the outer ring 3, so that the axial sliding of the outer ring 3 can be limited, and the two end faces of the outer ring and adjacent parts can be prevented from being abraded.

In this embodiment, the thrust needle roller and cage assembly 31 is provided between the two axial end surfaces of the outer ring 3 and the adjacent members, which is advantageous in that the size is small and the volume of the check valve can be reduced.

A torque transfer assembly 7 is disposed between the inner race 2 and the outer race 3, the outer race 3 being free to rotate relative to the inner race 2 in a first rotational direction (e.g., clockwise facing the shaft end), the torque transfer assembly 7 being configured to engage the inner race 2 and the outer race 3 and prevent rotation of the outer race 3 relative to the inner race 2 in a second rotational direction (i.e., reverse rotation, with the shaft end facing counterclockwise); the torque transmission assembly 7 is provided with stoppers 71 at both axial sides thereof for restricting axial sliding of the torque transmission assembly 7. In this embodiment, the structures of the torque transmission assembly 7 and the limiting block 71 are the same as those of the conventional backstop, and are not described herein again.

The outer disc 4 is arranged as an annular friction plate, an outer spline is arranged on the excircle of the outer disc 4, the outer disc 4 is connected with the inner spline of the shell 1 in a matching way through the outer spline, and the outer disc can freely move along the direction of an axis 9;

at least one inner disc 5, inner disc 5 set up to annular friction disc, and the hole of inner disc 5 is provided with the internal spline, the internal spline is connected with the external spline cooperation of outer lane 3, and can freely remove along the direction of axis 9.

The outer discs 4 alternate with the inner discs 5 in the direction of the axis 9.

The outer disc 4 and the inner disc 5 have a coupled state in which the contact surfaces of the outer disc 4 and the inner disc 5 are pressed and the outer disc 4 and the inner disc 5 can transmit torque, and a separated state; in the separated state, the pressing force between the outer disc 4 and the inner disc 5 is removed, and the outer disc 4 is free to rotate relative to the inner disc 5.

It is understood that the separated state described in the present embodiment means that the pressing force for transmitting the torque between the outer disc and the inner disc is removed regardless of whether the outer disc and the inner disc are in contact or completely separated.

In the present embodiment, the housing 1 is provided with a support in the radial direction with the inner ring 2 via the first end cap 11 and the rolling bearing 12, so that the housing 1 can rotate freely with respect to the inner ring 2. It will be appreciated that, as the torque transfer assembly 7 is arranged between the outer ring 3 and the inner ring 2 for radial support, the housing 1 may also be provided with support in a radial direction with the outer ring 3, such that the housing 1 is able to rotate freely relative to the outer ring 3, thereby enabling free rotation of the housing 1 relative to the inner ring 2.

The direction of the axis 9 described in the present embodiment refers to the axial direction, i.e., the left-right direction in the example of fig. 1.

The pushing mechanism 6 is fixedly connected with the inner ring 2 and used for mutually switching the outer disc 4 and the inner disc 5 between a combined state and a separated state, and a thrust bearing or a thrust roller pin and retainer assembly is arranged between the contact surfaces of the pushing mechanism and the inner disc or the outer disc so that the outer disc and the inner disc can rotate relative to the piston in the combined state; the thrust bearing can be a thrust ball bearing or a thrust roller bearing; in this embodiment, a thrust roller and cage assembly 69 is used, the thrust roller and cage assembly 69 being used in conjunction with a thrust washer (GB/T4605 and 2003); the shell 1 can rotate freely relative to the pushing mechanism 6, and a rotary seal is arranged between the shell 1 and the pushing mechanism 6.

In this embodiment, the pushing mechanism 6 includes a piston 61, a spring 62, a housing 63, a pump station, a thrust adjusting mechanism 65, a pressing ring 66, an adjusting screw 68, and a thrust needle roller and cage assembly 69.

One axial end of the piston 61 is used to apply an axial force to the outer or inner disc; for example, one end of the piston 61 is adapted to contact the side of the outer disc 4 via a thrust roller and cage assembly 69 for applying pressure to the outer disc 4; it will be appreciated that depending on the number of outer discs and inner discs, the axial end faces of the thrust roller pin and cage assembly 69 may also contact the axial sides of the inner discs 5 for applying pressure to the inner discs 5. Since the outer discs 4 and the inner discs 5 are both free to move in the axial direction, when the side of one outer disc or inner disc is pressed by the piston 61, it will move axially until all outer and inner discs abut against each other and pressure is generated between the contact surfaces to transmit torque.

The spring 62 is used to generate an axial force in the direction of the axis 9 to urge the piston 61 in the direction of the axis towards the outer or inner disc, generating a pressing force between the inner and outer discs and thereby transmitting a torque.

The housing 63 and the piston 61 form an annular oil reservoir chamber 64; the annular oil storage cavity 64 is communicated with a pump station through a connector 67 arranged on the shell 63, and the pump station is used for injecting hydraulic oil into the annular oil storage cavity 64 so as to overcome the axial force applied to the piston 61 by the spring 62, so that the piston 61 moves towards the direction far away from the outer disc or the inner disc, and the pressing force between the outer disc 4 and the inner disc 5 is released, further the torque is not transmitted any more, and the shell 1 can rotate reversely relative to the inner disc. The reverse direction refers to: for example, the permanent magnet roller rotates clockwise when in normal work, the shell 1 freely rotates along with the permanent magnet roller, and the inner ring 2 is fixed on the roller shaft and does not stand still; because the permanent magnet roller has a reverse rotation phenomenon (namely, anticlockwise) when being started, at this time, before the permanent magnet roller is started, a pump station is started firstly, the pump station injects pressure oil into the annular oil storage cavity 64, overcomes the force of the spring 62, enables the piston 61 to move towards the direction far away from the outer disc or the inner disc (to move towards the right in the example of fig. 1), eliminates the pressing force between the outer disc 4 and the inner disc 5, then starts the permanent magnet to roll, at this time, the shell 1 can idle along with the permanent magnet roller in a reverse direction without transmitting torque, and the inner ring is static. After the permanent magnet roller is started, normal clockwise rotation is started, oil pressure provided by a pump station can be released at the moment, pressure oil in the annular oil storage cavity 64 flows back to the pump station under the action of the spring 62, meanwhile, the piston moves leftwards again to apply pressing force to the outer disc 4 and the inner disc 5, torque begins to be transmitted between the outer disc 4 and the inner disc 5, the outer shell 1 drives the outer ring 3 to rotate freely through the matching of the outer disc and the inner disc, and the inner ring 2 is static. And finishing the no-load starting of the permanent magnet roller.

The thrust adjusting mechanism 65 is fixedly connected to the inner race 2 and the housing 63 in a detachable manner.

A plurality of springs 62 are uniformly distributed in the circumferential direction of the piston 61, and a pressing ring 66 is arranged at one end, far away from the outer disc or the inner disc, of each spring; the thrust adjusting mechanism 65 is provided with an adjusting screw 68 at a position corresponding to each spring, and the adjusting screw 68 is pressed against the pressing ring 66 and used for adjusting the compression amount of the spring 62, further adjusting the force of the spring on the piston 61 and transmitting the force between the joint surfaces of the outer disc and the inner disc, thereby adjusting the torque value transmitted between the outer disc and the inner disc.

It can be understood that, after the thrust adjusting mechanism 65 is fixedly connected with the housing 63, the radial outer circle thereof may continue to extend outward to form a flange corresponding to the first end cap 11, and the flange on the thrust adjusting mechanism 65 and the flange of the first end cap 11 are fixedly connected in a detachable manner by bolts or screws in the direction of the axis 9, so as to facilitate transportation and field scouting during transportation. After the bidirectional rotation check device 8 is installed on site, before operation, the connection part between the flange of the thrust adjusting mechanism 65 and the flange of the first end cap 11 should be removed, so that the first end cap 11 can freely rotate along with the rotating component, and the thrust adjusting mechanism 65 is still. The number of the bolts or screws for connecting the flange of the thrust adjusting mechanism 65 and the flange of the first end cap 11 is at least 2 in the circumferential direction.

Optionally, for the convenience of transportation and hoisting of the bidirectional rotation backstop, the shell 1 can be further far away from a side face of the first end cover, and the limiting cover is used for axial movement of the axial limiting pushing mechanism 6. For example, the limit cover, after being fixedly connected with the side surface of the housing, further has a limit surface, the limit surface is located at the right side of the thrust adjusting mechanism 65, and a thrust bearing or a thrust needle roller and retainer assembly is arranged between the limit surface and the thrust adjusting mechanism in the direction of the axis 9, and is used for placing abrasion between contact surfaces.

In the present embodiment, the thrust adjusting mechanism 65 further includes: and a wear indicating pin (not shown in fig. 1) having one end fixedly connected to the right end surface of the piston 61 in a detachable manner and the other end extending outward by a length in the direction of the axis 9 through the thrust adjusting mechanism 65, the wear indicating pin being provided with scale marks along its axial direction. When the outer disc and/or the inner disc are abraded to reduce the thickness of the outer disc and/or the inner disc, the piston 61 moves leftwards under the action of the spring 62, the length of the abrasion indicating pin extending out of the thrust adjusting mechanism is reduced, and the torque value which can be transmitted by the outer disc and the inner disc at present can be determined according to the scale value on the abrasion indicating pin; the value of the torque transmission between the outer and inner discs can be adjusted, if necessary, by means of the adjusting screw 68.

In the present embodiment, the spring 62 is a cylindrical compression spring, and it is understood that the spring 62 may be other compression springs such as a disc spring.

The first end cover 11 is fixedly connected with the axial end face of the shell 1, and a rolling bearing is arranged between an inner hole of the first end cover 11 and the inner ring 2.

In this embodiment, a copper sleeve 15 and a skeleton oil seal are disposed radially between the housing 1 and the casing 63, and the copper sleeve 15 is used to radially support the housing 1, so that the housing 1 can freely rotate relative to the pushing mechanism 6. It will be appreciated that the copper bush may also be replaced by a rolling bearing.

As shown in fig. 1, seal rings are provided between the piston 61 and the mating surfaces of the housing 63 and the thrust adjusting mechanism. And the outer circumferential surface in the radial direction of the shell 1 is provided with an oil hole for injecting lubricating oil between the outer disc and the inner disc and between the outer ring and the inner ring or releasing the internal lubricating oil.

As shown in fig. 1, in the figure, a sealed space is formed by the housing 1, the first end cover 11, the inner ring 2, the pushing mechanism 6, the sealing ring and the framework oil seal, the outer disc 4, the inner disc 5, the outer ring 3 and the torque transmission assembly 7 are enclosed inside, in order to prevent a sealed environment from being formed in the sealed space, a vent hole communicated with the external atmosphere can be arranged on the static pushing mechanism 6, and an air cleaner is arranged on the vent hole; for example, the vent hole may be provided in the case 63, or the vent hole may be provided in the thrust adjusting mechanism 65.

In order to ensure that the bidirectional rotation backstop has more stable performance during working, after the bidirectional rotation backstop is installed, the inner ring of the bidirectional rotation backstop needs to be axially positioned so as to limit the movement of the inner ring in the direction of the axis 9.

The bidirectional rotation backstop can be switched between a combined state and a separated state through the outer disc 4 and the inner disc 5, and can meet rotation requirements in different directions; when no torque is required to be transmitted between the outer casing 1 and the inner ring 2, the outer disc 4 and the inner disc 5 are in a separated state, and the outer casing 1 can freely rotate in both directions relative to the inner ring 2. When torque needs to be transmitted between the outer shell 1 and the inner ring 2, the outer disc 4 and the inner disc 5 are in a combined state, the outer shell 1 can only freely rotate in one direction relative to the inner ring, and the other direction realizes a non-return effect; if the torque transmitted in the combined state of the outer disc 4 and the inner disc 5 exceeds a set value, the combined surface of the outer disc 4 and the inner disc 5 slips, and the backstop can be prevented from being damaged; if a plurality of backstops are installed, the load balancing among the plurality of backstops can be realized at the moment, and because when one backstop slips, the other backstops begin to bear force, the backstop force provided by the plurality of backstops can be superposed, so that the types of the plurality of backstops are reduced.

In addition, when the bidirectional rotation backstop works, the inner ring 2 is fixed, and the shell 1 rotates along with equipment, so that the bidirectional rotation backstop is just opposite to the structure of the existing backstop and can be applied to a permanent magnet roller in the latest technology.

Moreover, this application is through first end cover 11 and shell 1 fixed connection to be provided with antifriction bearing 12 between the hole of first end cover 11 and inner circle 2 and support, its advantage lies in having reduced the model of bearing, has reduced product cost.

Fourth, this application still is provided with the wearing and tearing indicator pin, if the back that appears wearing and tearing between outer dish and the inner disc, can show the wearing and tearing volume through the scale on the wearing and tearing indicator pin to can in time adjust the spring force, with the ability of guaranteeing transmission torque between outer dish and the inner disc.

Fifth, the two-way non-return ware that changes of this application need not additionally install the contrary arm of force of ending, simple structure, simple to operate.

The present application further provides a permanent magnet drum, as shown in fig. 2, comprising the bidirectional rotation brake as described above. The figure only shows the connection of the bidirectional rotation backstop and the permanent magnet roller, and the bidirectional rotation backstop can be connected with a side plate of the permanent magnet roller. Because the pushing mechanism 6 in the bidirectional rotation backstop 8 is fixedly connected with the inner ring, and the inner ring 2 is connected with the roller shaft of the permanent magnet roller through a key, the pushing mechanism 6 cannot rotate, and conditions are created for connecting the pushing mechanism 6 with a pump station. For example, the permanent magnet roller rotates clockwise in normal operation, the shell 1 freely rotates along with the permanent magnet roller, and the inner ring 2 is fixed on the roller shaft and does not stand still; because the permanent magnet roller has a reverse rotation phenomenon (namely, anticlockwise) when being started, at this time, before the permanent magnet roller is started, a pump station is started firstly, the pump station injects pressure oil into the annular oil storage cavity 64, overcomes the force of the spring 62, enables the piston 61 to move towards the direction far away from the outer disc or the inner disc (to move towards the right in the example of fig. 1), eliminates the pressing force between the outer disc 4 and the inner disc 5, then starts the permanent magnet to roll, at this time, the shell 1 can idle along with the permanent magnet roller in a reverse direction without transmitting torque, and the inner ring is static. After the permanent magnet roller is started, normal clockwise rotation is started, oil pressure provided by a pump station can be released at the moment, pressure oil in the annular oil storage cavity 64 flows back to the pump station under the action of the spring 62, meanwhile, the piston moves leftwards again to apply pressing force to the outer disc 4 and the inner disc 5, torque begins to be transmitted between the outer disc 4 and the inner disc 5, the outer shell 1 drives the outer ring 3 to rotate freely through the matching of the outer disc and the inner disc, and the inner ring 2 is static. And finishing the no-load starting of the permanent magnet roller.

In order to ensure that the bidirectional rotation backstop has more stable performance during working, after the bidirectional rotation backstop is installed, the inner ring of the bidirectional rotation backstop needs to be axially positioned so as to limit the movement of the inner ring in the direction of the axis 9.

Finally, it should be pointed out that: the above examples are only for illustrating the technical solutions of the present application, and are not limited thereto. Although the present application has been described in detail with reference to the foregoing embodiments, it should be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions in the embodiments of the present application.