CN110758998A - Backstop and have its permanent magnetism cylinder - Google Patents
Backstop and have its permanent magnetism cylinder Download PDFInfo
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- CN110758998A CN110758998A CN201911196063.8A CN201911196063A CN110758998A CN 110758998 A CN110758998 A CN 110758998A CN 201911196063 A CN201911196063 A CN 201911196063A CN 110758998 A CN110758998 A CN 110758998A
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- disc
- backstop
- ring
- shell
- housing
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- 229910052802 copper Inorganic materials 0.000 claims description 6
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- 230000008878 coupling Effects 0.000 claims description 2
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- 230000005540 biological transmission Effects 0.000 abstract description 14
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G23/00—Driving gear for endless conveyors; Belt- or chain-tensioning arrangements
- B65G23/02—Belt- or chain-engaging elements
- B65G23/04—Drums, rollers, or wheels
- B65G23/08—Drums, rollers, or wheels with self-contained driving mechanisms, e.g. motors and associated gearing
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
Abstract
The application discloses backstop and have its permanent magnetism cylinder, the 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 shell is connected with the rotating part, and a torque transmission assembly is arranged between the shell and the outer ring and used for realizing the unidirectional rotation of the shell relative to the outer ring; the inner ring is fixed, and an outer disc and an inner disc are arranged between the inner ring and the outer ring; by adjusting the combination state of the outer disc and the inner disc, the outer ring can freely rotate relative to the inner ring or can transmit torque. The permanent magnet roller comprises the backstop. The application has the advantages that: the inner ring of the backstop is fixed, the shell rotates, the structure of the backstop is just opposite to that of the existing 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 backstop 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.
Description
Technical Field
The application relates to the technical field of brakes, in particular to a 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 backstop and a permanent magnet drum having the same that overcome or at least alleviate at least one of the above-mentioned deficiencies of the prior art.
To achieve the above object, the present application provides a backstop, 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;
a torque transfer assembly disposed between the housing and the outer race, the housing being freely rotatable relative to the outer race in a first rotational direction, the torque transfer assembly for coupling the housing and the outer race and preventing rotation of the housing relative to the outer race in a second rotational direction;
at least one outer disc connected to a radially inner surface of the outer ring 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 outer ring and the inner ring are provided with supports in the radial direction, so that the outer ring can freely rotate relative to the inner ring in the separated state; 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 in the separated state.
Preferably, the non-return device further comprises:
and the pushing mechanism is fixedly connected with the inner ring and is used for mutually switching the outer disc and the inner disc between a combined state and a separated state.
Preferably, the pushing mechanism comprises:
a piston having one end for contacting an axial side of 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 non-return device further comprises:
the first end cover is fixedly connected with the axial end face of the shell, and a rotary seal is arranged between an inner hole of the first end cover and the outer ring.
Preferably, the non-return device further comprises:
and the second end cover is fixedly connected with the axial end face of the outer ring, and a rolling bearing and a rotary seal are arranged between the inner hole of the second end cover and the inner ring.
Preferably, the non-return device further comprises:
the transition ring is fixedly connected with the other axial end face of the outer ring; a rotary seal is arranged between the transition ring and the shell; and a rotary seal and a rolling bearing or a copper sleeve are arranged between the transition ring and the shell.
The application also provides a permanent magnet roller, permanent magnet roller contains as above the backstop.
The beneficial effect of this application lies in:
the backstop can be switched between a combined state and a separated state through the outer disc and the inner disc, and can meet the 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 backstop works, the inner ring is fixed, and the shell rotates along with equipment needing backstopping, so that the 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 second end cover and outer lane fixed connection to be provided with the bearing support between the hole of second 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, traditional backstop is compared to this application, no longer need install the contrary arm of force of ending alone, and the installation is simple and convenient, more is fit for the site work condition.
Drawings
Fig. 1 is a schematic half-sectional structure view of a non-return device according to an embodiment of the present disclosure.
Fig. 2 is a schematic structural diagram of the connection between the backstop and the permanent magnet roller.
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 backstop; 9-axis; 10-a permanent magnet drum; 11-a first end cap; 31-a second end cap; 32-a transition ring; 33-positioning plate; 34-framework oil seal; 35-rolling bearings; 36-a copper sleeve; 71-a limiting block; 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 screw.
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 half-sectional structure view of a non-return device according to one embodiment completed by the present application is shown. The non-return means 8 are designed to be associated with a rotating member rotating about an axis 9, defining the direction of rotation of said rotating member in normal operation as a positive 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 non-return means 8 can again allow the rotation of the rotation member in reverse about the axis 9 when the rotation member is overloaded in the operating condition. The 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 second end cover 31, a transition ring 32, a rolling bearing 35, a positioning plate 33, a framework oil seal 34, a copper sleeve 36 and a limiting block 71.
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.
In this embodiment, the inner bore of the housing 1 is provided as a stepped bore having two diameters, a smaller diameter bore portion for cooperation with the torque transfer assembly 7 and a larger diameter bore portion for cooperation with the transition ring 32 to form a mounting portion for the backbone oil seal. The aperture with the smaller diameter is far away from one end of the aperture with the larger diameter and the spigot of the first end cover 11 are matched for radial positioning, and meanwhile, the first end cover 11 is fixedly connected with the axial end face of the shell 1 through a screw.
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 bore of the first end cap 11 is also provided with a rotary seal mounting structure for mounting a skeleton oil seal which may be used to seal lubricating oil in the sealed space formed by the housing 1 and the outer ring 3 and transition ring 32 for lubricating the torque transfer assembly 7.
The inner ring 2 is arranged in the shell 1 and is fixed; in this embodiment, the excircle of inner circle 2 has two shaft shoulder structures in the axial, and the excircle diameter of interlude is greater than the excircle diameter at both ends, has processed the external splines on the diameter of interlude, the external splines are used for being connected with the cooperation of inner disc 5. An outer circle section on the left side (in the direction of fig. 1) of the middle section and an inner hole of the second end cover 31 form a mounting part of a rolling bearing 35, and the rolling bearing 35 is arranged between the second end cover 31 and the inner ring 2 and plays a supporting role; antifriction bearing 35 carries out axial positioning through locating plate 33, and locating plate 33 passes through screw and second end cap 31 fixed connection, and is provided with rotary seal in the hole department of locating plate 33, and rotary seal is skeleton oil blanket 34 in this embodiment. The inner bore of the rolling bearing 35 is mounted on the inner ring 2. The first end cover 11 is fixedly supported and connected with the housing 1, the second end cover 31 and the outer ring 3 are radially supported through spigot fit, meanwhile, the second end cover 31 is fixedly connected with the axial end face of the outer ring 3 through a screw, and the outer ring 3 and the housing 1 are radially supported by the torque transmission assembly 7, so that the housing 1 can rotate relative to the inner ring 2 through the support of the rolling bearing 35, and the inner ring 2 is still. 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 outer lane 3's hole sets up to the step hole that has the diameter change, and the diameter of middle hole section is less than the aperture of both ends hole section the internal surface of middle hole section is provided with the internal spline, the internal spline is used for being connected with the cooperation of outer dish 4. One end of the hole sections at the two ends is used for carrying out radial spigot matching positioning with the second end cover 31, and the other end is used for carrying out radial spigot matching positioning with the transition ring 32.
The outer circle of the outer ring 3 and the inner hole diameter of the housing 1 form a raceway for mounting the torque transfer component 7. A torque transfer assembly 7 is provided between the housing 1 and the outer race 3, the housing 1 being free to rotate relative to the outer race 3 in a first rotational direction (e.g. clockwise facing the shaft end), the torque transfer assembly 7 being adapted to couple the housing 1 and the outer race 3 and to prevent rotation of the housing 1 relative to the outer race 3 in a second direction (i.e. in reverse, when counterclockwise facing the shaft end); 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 an inner spline of the outer ring 3 in a matched mode through the outer spline, and the outer disc can move freely 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 inner circle 2, 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 embodiment, the housing 1 and the first end cover 11 are positioned in a matching way through a radial spigot, are radially supported and are fixedly connected through screws; the shell 1 and the outer ring 3 are radially supported through the torque transmission assembly 7, and an inner hole of the outer ring 3 and the second end cover 32 are matched and positioned through a radial spigot for radial support; the inner bore of the second end cap 32 is in turn supported in the radial direction by the rolling bearing 35 with the inner ring 2, so that the housing 1 can rotate freely relative to the inner ring 2 in the disengaged state.
It will be appreciated that the housing 1 may also be supported directly radially from the inner ring 2 so that the housing is free to rotate relative to the inner ring. For example, in an alternative embodiment, the housing 1 is radially supported by a radial spigot with a first end cap to which the end face of the housing is fixedly connected, and the inner bore of the first end cap directly cooperates with the outer circumference of the inner ring 2 to form a mounting for the rolling bearing, the mounting being configured to mount the rolling bearing such that the housing is free to rotate relative to the inner ring.
The free rotation described in this embodiment is not unconditionally free rotation, and for example, it may be necessary in some cases to free rotation in a state where the outer disc is separated from the inner disc. The free rotation is only meant to be possible when a rotational condition is present.
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.
In the present embodiment, the pushing mechanism 6 includes a piston 61, a spring 62, a housing 63, a pump station, a pushing force adjusting mechanism 65, a pressing ring 66, and an adjusting screw 68.
One end of the piston 61 is for contacting the side of the outer disc 4 for applying pressure to the outer disc 4; it will be appreciated that the axial end face of the piston 61 may also be in contact with the axial side face of the inner disc 5 for applying pressure to the inner disc 5, depending on the number of outer and inner discs. 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 is transmitted between the outer disc 4 and the inner disc 5, the outer ring 3 is limited by the outer disc 4 to be stationary, and the torque transmission assembly 7 between the outer shell 1 and the outer ring 3 is provided with the roller, so that the outer shell 1 can freely rotate relative to the outer ring 3 and the inner ring 2 at the moment, and the inner ring 2 and the outer ring 3 are stationary. 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 is understood that after the thrust adjusting mechanism 65 is fixedly connected with the housing 63, the radial outer circle of the thrust adjusting mechanism can continue to extend outwards to form a flange structure, and the flange structure on the thrust adjusting mechanism 65 can be detachably and fixedly connected with the flange of the first end cover 11 in the direction of the axis 9 through bolts or screws; the flange structure on the thrust adjustment mechanism 65 may also be screwed to the axial side of the housing 1 or the transition ring 32 to facilitate handling during transportation and field run-in. After the non-return device 8 is installed on site, the connecting bolts or screws on the flange structure of the thrust adjusting mechanism 65 should be removed before operation, so that the first end cover 11 can freely rotate along with the rotating component, and the thrust adjusting mechanism 65 is still. The number of the connecting bolts or screws on the flange structure of the thrust adjusting mechanism 65 is at least 2 in the circumferential direction.
Optionally, for the transportation and hoisting of the backstop, a limit cover can be further mounted on the side surface of the shell 1 far away from the first end cover, and the limit cover is used for axial movement of the axial limit 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.
In the present embodiment, the diameter of the outer circle of the second end cap 31 in the radial direction is the same as the diameter of the outer circle 3, and the diameter of the outer circle 3 is the diameter matched with the first end cap 11. The inner hole of the framework oil seal installed in the inner hole of the first end cover 11 can also be matched with the outer circle of the second end cover 31, and the advantage is that no additional sealing is needed between the matching surfaces of the second end cover and the outer ring.
The transition ring 32 is arranged to be of an annular structure and is provided with a spigot structure, the spigot structure is radially matched with one end of an inner hole of the outer ring 3 for positioning and supporting, and the end face of the transition ring 32 and the end face of the outer ring 3 are fixedly connected in a detachable mode through screws. A copper sleeve 36 and a framework oil seal are arranged between the inner hole of the transition ring 32 and the radial direction of the shell 63, and the copper sleeve 36 is used for enabling the transition ring 32 to freely rotate relative to the shell 63. It will be appreciated that the copper bush may also be replaced by a rolling bearing.
As shown in fig. 1, sealing rings are provided between the piston 61 and the mating surfaces of the housing 63 and the inner ring. An oil hole is formed in the outer circumferential surface of the outer shell 1 in the radial direction and used for injecting lubricating oil between the outer disc and the inner disc and between the outer shell and the outer ring or releasing the lubricating oil inside.
As shown in fig. 1, in the figure, a sealed space is formed by the housing 1, the first end cover 11, the second end cover 31, the transition ring 32, the inner ring 2, the pushing mechanism 6, the seal ring and the framework oil seal, the outer disk 4, the inner disk 5, the outer ring 3 and the torque transmission assembly 7 are enclosed inside, in order to prevent the sealed environment from forming into the sealed space and generate the internal pressure, a vent hole communicated with the external atmosphere is arranged on the pushing mechanism 6 which is static, 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 backstop has more stable performance during working, after the backstop is installed, the inner ring of the backstop needs to be axially positioned so as to limit the movement of the inner ring in the direction of the axis 9.
The 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 the 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, so that the types of the plurality of backstops are reduced.
In addition, when the backstop works, the inner ring 2 is fixed, and the shell 1 rotates along with the equipment, so that the 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 second end cover 31 and outer lane 3 fixed connection to be provided with antifriction bearing 35 between the hole of second end cover 31 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, traditional backstop is compared to this application, no longer need install the contrary arm of force of ending alone, and the installation is simple and convenient, more is fit for the site work condition.
The application also provides a permanent magnet roller, as shown in fig. 2, which comprises the backstop. The figure only shows the connection of the backstop and the permanent magnet roller, and the backstop can be connected with the side plate of the permanent magnet roller. Because the pushing mechanism 6 in the 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 keys, 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 ring 3 is still under the limitation of the outer disc 4, the inner ring 2 is still, and the shell 1 rotates freely. And finishing the no-load starting of the permanent magnet roller.
In order to ensure that the backstop has more stable performance during working, after the backstop is installed, the inner ring of the 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.
Claims (10)
1. A 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 housing and the outer race, the housing being freely rotatable relative to the outer race in a first rotational direction, the torque transfer assembly being for coupling the housing and the outer race and preventing rotation of the housing relative to the outer race in a second direction;
at least one outer disc (4), said outer disc (4) being connected to a radially inner surface of said outer ring 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 outer ring (3) and the inner ring (2) are provided with supports in the radial direction, so that the outer ring can freely rotate relative to the inner ring in the separated state; or the outer shell (1) 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 in the separated state.
2. The backstop of claim 1, further comprising:
and the pushing mechanism (6) is fixedly connected with the inner ring and is used for mutually switching the outer disc and the inner disc between a combined state and a separated state.
3. The backstop of claim 2, wherein said urging mechanism comprises:
a piston (61) having one end for contacting an axial side of 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 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 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 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 backstop of claim 6, further comprising:
the first end cover (11), the first end cover with the axial terminal surface fixed connection of shell (1), the hole of first end cover with be provided with rotary seal between the outer lane.
8. The backstop of claim 7, further comprising:
the second end cover (31), the second end cover (31) with the axial terminal surface fixed connection of outer lane, the hole of second end cover (31) with be provided with antifriction bearing and rotary seal between the inner circle.
9. The backstop of claim 8, further comprising:
the transition ring (32) is fixedly connected with the other axial end face of the outer ring; a rotary seal is arranged between the transition ring (32) and the shell; and a rotary seal and a rolling bearing or a copper sleeve are arranged between the transition ring (32) and the shell (63).
10. A permanent magnet drum, characterized in that it comprises a backstop according to any one of claims 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911196063.8A CN110758998A (en) | 2019-11-27 | 2019-11-27 | Backstop and have its permanent magnetism cylinder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911196063.8A CN110758998A (en) | 2019-11-27 | 2019-11-27 | Backstop and have its permanent magnetism cylinder |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110758998A true CN110758998A (en) | 2020-02-07 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911196063.8A Pending CN110758998A (en) | 2019-11-27 | 2019-11-27 | Backstop and have its permanent magnetism cylinder |
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| Country | Link |
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| CN (1) | CN110758998A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113606264A (en) * | 2021-09-13 | 2021-11-05 | 泰安英迪利机电科技有限公司 | Backstop for permanent magnet roller and permanent magnet roller comprising backstop |
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| CN113606264A (en) * | 2021-09-13 | 2021-11-05 | 泰安英迪利机电科技有限公司 | Backstop for permanent magnet roller and permanent magnet roller comprising backstop |
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