CN112377537A - Dual-redundancy bidirectional backstop - Google Patents

Dual-redundancy bidirectional backstop Download PDF

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Publication number
CN112377537A
CN112377537A CN202011127703.2A CN202011127703A CN112377537A CN 112377537 A CN112377537 A CN 112377537A CN 202011127703 A CN202011127703 A CN 202011127703A CN 112377537 A CN112377537 A CN 112377537A
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CN
China
Prior art keywords
output shaft
shell
wedge block
backstop
wedge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202011127703.2A
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Chinese (zh)
Inventor
牛光冉
吴昊
聂振金
王丹阳
魏伊
李林
陈婷
薛钊
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Beijing Research Institute of Precise Mechatronic Controls
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Beijing Research Institute of Precise Mechatronic Controls
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Publication date
Application filed by Beijing Research Institute of Precise Mechatronic Controls filed Critical Beijing Research Institute of Precise Mechatronic Controls
Priority to CN202011127703.2A priority Critical patent/CN112377537A/en
Publication of CN112377537A publication Critical patent/CN112377537A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/063—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by moving along the inner and the outer surface without pivoting or rolling, e.g. sliding wedges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D2041/0603—Sprag details

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

A dual-redundancy bidirectional backstop comprises a shell, a deep groove ball bearing, an input shaft, an output shaft, a wedge block, a roller, a gasket, a truncated cone spiral spring and a straight spring; the shell of the backstop is fixed, rollers at two sides are pressed by a straight spring, so that the rollers, the shell and the output shaft are in a wedged state, and meanwhile, a truncated cone spiral spring presses a wedge block until the wedge block is kept in contact with the shell, so that reverse transmission backstopping is realized; during forward transmission, the pin rollers are pulled open by the pusher dogs of the input shaft, and the wedge blocks are enabled to rotate in the same direction, so that normal transmission of the backstop is realized. The roller and the wedge block are skillfully combined, the slipping phenomenon of the wedge block is avoided through the roller, the pusher dog of the input shaft is structurally combined with the wedge block, the problem that the traditional backstop is blocked is solved, and the requirement of high reliability of the cargo compartment door is met.

Description

Dual-redundancy bidirectional backstop
Technical Field
The invention relates to a dual-redundancy bidirectional backstop, in particular to an anti-reversion device for an electromechanical servo redundancy mechanism of an aircraft, and belongs to the field of mechanical transmission.
Background
The actuation system of a cargo door of a certain model adopts a differential scheme and is divided into an electric mode and a manual mode, and a backstop is required under the two modes. When the motor stops rotating in the electric mode, the ball screw rotates due to inertia, and in order to ensure that the cargo door does not rotate, the output end of the backstop is subjected to the action of torque to perform friction locking, so that the cargo door is prevented from falling to cause injury to personnel; when the device is in a manual mode, the transmission flexible shaft transmits force and torque to the input end of the backstop in two clockwise and anticlockwise directions, and then the opening and closing of the cargo door are manually adjusted through the differential mechanism and the ball screw. The existing backstop is easy to have the phenomenon of clamping stagnation or slipping, and can not meet the requirement of high reliability of the cargo hold door.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the defects in the prior art are overcome, and the dual-redundancy bidirectional backstop is provided.
The technical solution of the invention is as follows:
a dual-redundancy bidirectional backstop comprises a first deep groove ball bearing, a second deep groove ball bearing, an input shaft, a shell, an output shaft, a gasket, a straight spring, a truncated cone spiral spring, a wedge block, a roller and a clamp spring;
the output shaft is integrally processed and comprises two cylinders with different diameters, and the second deep groove ball bearing is sleeved on the small cylinder of the output shaft through a gasket; two bulges are symmetrically processed on the side wall of the output shaft large cylinder, the two sides of each bulge are processed into wedging surfaces, each bulge is processed with two round holes, a compressed straight spring is placed in each round hole, a roller is placed on each wedging surface on the two sides of each bulge on the output shaft large cylinder, and the rollers are kept in contact with the straight springs after being installed in place; a groove is axially processed on the large cylinder of the output shaft;
a circular groove is processed in the center of the wedge block, the large end face of the truncated cone helical spring is installed in the circular groove, and the wedge block and the truncated cone helical spring form an integral structure which is placed in a groove of a large cylinder of the output shaft;
the first deep groove ball bearing is sleeved on the input shaft; four shifting claws are machined on the input shaft, four gaps are formed among the four shifting claws, and two opposite gaps are identical in width and are called a pair of gaps; in the two pairs of gaps, the width of one pair of gaps is larger than that of the other pair of gaps;
the wedge surface of the output shaft with the roller is sleeved in the gap with larger width of the input shaft, and the wedge block is sleeved in the gap with smaller width; the integral structure after the equipment is put in place is installed in the shell, and the both ends are limited through the clamp springs.
The groove on the large cylinder of the output shaft is of an up-and-down asymmetric structure.
Arc-shaped grooves are processed on the two circular lobes of the large cylinder of the output shaft except the groove structure, after the installation in place,
the small end surface of the truncated cone helical spring is propped against the arc-shaped groove.
The wedge block has trapezoidal section, and the long side of the wedge block is arc-shaped and tangent to the inner wall of the casing.
The shell is hollow columnar structure, and during the installation, the casing axis is deviated with the connecting wire of the symmetric point on two contact surfaces of voussoir long limit and shell, and is parallel with the axis.
When the wedge is in work, the stress of any pair of contact points on the long edge of the wedge and two contact surfaces of the shell is marked as F1 and F2, and the wedge angles of F1 and F2 are theta respectively1、θ2，θ1And theta2It should satisfy:
θ2≤θ1＝5.71°。
the input shaft is connected to the external structure by a flat key.
When in work, the wedge angle of the roller should satisfy alpha less than or equal to 2 rhocWhere α is the roller wedge angle, ρcIs the rubbing angle.
The friction angle refers to an included angle between a contact line of the roller and the inner wall of the shell and a contact line of the roller and the wedging surface of the output shaft.
The section of the large cylinder groove of the output shaft is rectangular.
Compared with the prior art, the invention has the following beneficial effects:
(1) the roller and the wedge block are skillfully combined, the slipping phenomenon of the wedge block is avoided through the roller, the pusher dog of the input shaft is structurally combined with the wedge block, the problem that the traditional backstop is blocked is solved, and the requirement of high reliability of the cargo compartment door is met.
(2) The wedge block is designed in an eccentric structure, and a connecting line of any symmetrical point of the contact surface of the wedge block and the shell deviates from the axis of the shell and is parallel to the axis. Therefore, the forward transmission and reverse non-return functions of the wedge block are realized.
(3) The two side surfaces of the wedge block are arc surfaces, so that the contact area with the shell is increased, the contact stress of the contact area is reduced, and the service life is prolonged.
(4) The roller and the wedge block bear the backstop torque at the same time, the bearing capacity is strong, the abrasion conditions of the roller and the wedge block are reduced, and the service life of the backstop can be effectively prolonged.
Drawings
FIG. 1 is a block diagram of a two-way backstop;
FIG. 2 is a cross-sectional view of a two-way backstop;
FIG. 3 is a view of the input shaft configuration;
FIG. 4 is a view of the output shaft structure;
FIG. 5 is a schematic view of a wedge shape;
FIG. 6 is a partial view of the input shaft;
FIG. 7 is a partial view of the output shaft;
FIG. 8 is a force analysis diagram of a wedge;
figure 9 force analysis diagram of the roller.
Detailed Description
The invention aims to design a backstop. When the input shaft rotates clockwise and anticlockwise, the output shaft can be driven to transmit; when the output shaft rotates clockwise and anticlockwise, the backstop cannot transmit torque and is in a locking state.
As shown in fig. 1-7, the dual-redundancy bidirectional backstop of the present invention comprises a first deep groove ball bearing 13, a second deep groove ball bearing 14, an input shaft 2, a housing 3, an output shaft 4, a spacer 5, a straight spring 6, a truncated cone coil spring 7, a wedge 8, a roller and a snap spring 51.
The output shaft 4 is integrally processed and comprises two cylinders with different diameters, and the second deep groove ball bearing 14 is sleeved on the small cylinder of the output shaft 4 through a gasket 5; two bulges are symmetrically processed on the side wall of the large cylinder of the output shaft 4, the two sides of each bulge are processed into wedging surfaces, each bulge is processed with two round holes, a compressed straight spring 6 is placed in each round hole, the wedging surfaces on the two sides of each bulge on the large cylinder of the output shaft 4 are respectively provided with a roller 9, 10, 11 and 12, and after the installation is in place, the rollers are kept in contact with the shell 3 and the straight springs 6; the large cylinder of the output shaft 4 is provided with a rectangular groove along the axial direction, and the groove is of an up-down asymmetric structure. Arc-shaped grooves are processed on the two circular lobes of the large cylinder of the output shaft 4 except the groove structure.
The section of the wedge block 8 is trapezoidal, a circular groove is machined in the center of the wedge block, the truncated cone helical spring 7 is installed in the circular groove, the overall structure formed by the wedge block 8 and the truncated cone helical spring 7 is placed in a groove of a large cylinder of the output shaft 4, and the small end face of the truncated cone helical spring 7 abuts against the arc-shaped groove.
The first deep groove ball bearing 13 is sleeved on the input shaft 2; four shifting claws are machined on the input shaft 2, four gaps are formed among the four shifting claws, and two opposite gaps are identical in width and are called a pair of gaps; of the two pairs of gaps, one pair of gaps has a width greater than the other pair.
The wedge surface of the output shaft 4 provided with the balls is sleeved in the gap with larger width of the input shaft 2, and the wedge block 8 is sleeved in the gap with smaller width; the whole structure after assembling in place is installed in the shell 3, and the two ends are limited by the clamp springs 51.
The wedge block has trapezoidal section, and the long side of the wedge block is arc-shaped and tangent to the inner wall of the casing.
The shell is hollow columnar structure, and during the installation, the voussoir long limit is marked as first contact surface and second contact surface with two contact surfaces of shell, and the connecting wire of two symmetric points deviates from the shell axis on first contact surface and the second contact surface, and is parallel with the axis.
The working principle of the bidirectional backstop is as follows:
1) the working principle of forward transmission of the bidirectional backstop is as follows:
fig. 1 and 2 are structural diagrams of a bidirectional backstop, wherein a shifting fork is an input shaft 2 and transmits torque through a flat key; when the input shaft 2 rotates clockwise, the longer side of the wedge block 8 is poked, and then the output shaft 4 is driven to press the rollers 10 and 12 to the wide part in the groove (the groove formed by the shell and the wedge surface), so that the torque transmission in the clockwise direction is realized; when the input shaft 2 rotates along the counterclockwise direction, the longer side of the wedge block 8 is poked, and then the output shaft 4 is driven to press the rollers 9 and 11 to the wide part in the groove, so that the torque transmission in the counterclockwise direction is realized.
2) The working principle of reverse backstopping of the bidirectional backstop is as follows:
when the output shaft 4 rotates clockwise or counterclockwise, the rollers 10 and 12 (or the rollers 9 and 11) are always kept in contact with the shell 3 and the output shaft 4 under the action of the straight spring and are in a wedge angle self-locking state, so that the output shaft 4 cannot rotate even if a certain torque is given to the output shaft; in addition, due to the eccentric structure design of the wedge block, the wedge block and the shell are kept in a contact locking state.
Therefore, the input shaft of the backstop drives the output shaft to rotate in the same direction when moving clockwise and anticlockwise, and the backstop is always locked when the output shaft moves clockwise and anticlockwise.
As shown in FIG. 3, the input shaft is provided with a pusher dog 2-1 and a driving surface 2-2.
As shown in fig. 4, the output shaft has a wedge surface 4-1 and a wedge drive surface 4-2.
The shape of the wedge is simplified as shown in fig. 5.
As shown in fig. 6, the partial view of the input shaft mainly includes the rollers 9, the input shaft 2, the output shaft 4, and the sprags 8.
As shown in fig. 7, the partial view of the output shaft mainly includes the rollers 9, the output shaft 4, the spacers 5, and the wedge 8.
As shown in fig. 8, a force analysis of the wedge. The contact points of the wedge block and the shell are two points a and b, the wedge block and the outputThe contact point of the shaft is point c, the acting forces of the contact points a, b and c are respectively F1, F2 and Fc, and the wedge angles of F1, F2 and Fc are respectively theta1、θ2、θ4(R is the radius of the inner surface of the shell, delta 1 is the horizontal distance from the long side of the wedge block to the center o of the section of the shell, delta 2 is the horizontal distance from the short side of the wedge block to the center o of the section of the shell, mu is the friction coefficient, and d is the vertical distance from the acting point c of the output shaft to the axis line oo 1.)
Because the wedge is in a stress balance state, the stressed three force action lines are necessarily intersected at a point which is between the M point and the point q1 (the point q1 is not included), because the three forces cannot keep balance if the common point is positioned at the left side of q 1; if located to the right of point M, the wedge angle theta1Larger than the friction angle, the self-locking condition cannot be met; if the common point is not superposed with the point M, the points a and b are always in a static friction state no matter how the acting force of the point c changes, and the wedge block keeps self-locking; if the common point coincides with point M, the wedge will also be in a locked state. Taking the coincidence of the common point and the M point as an example, the self-locking condition of the wedge block obtained by establishing a balance equation and solving the balance equation is as follows:
θ2≤θ1＝5.71°
therefore, the wedge should satisfy the self-locking condition when being installed.
Fig. 9 shows a force analysis diagram of the roller. The contact points of the rollers with the shell and the output shaft are A, B two points, and the supporting force of the contact point A, B is N1、N2The friction force is respectively f1N1、f2N2And obtaining the self-locking condition of the roller by establishing a balance equation as follows: alpha is less than or equal to 2 rhoc. Where α is the roller wedge angle, ρcIs the rubbing angle. The friction angle is the included angle between the contact line of the roller and the inner wall of the shell and the contact line of the roller and the wedging surface of the output shaft.
The backstop shell is fixed, rollers at two sides are pressed by a straight spring to enable the rollers, the shell and an output shaft to be in a wedged state, and meanwhile, a truncated cone spiral spring presses a wedge block to be kept in contact with the shell, so that reverse transmission backstopping is realized; during forward transmission, the pin rollers are pulled open by the pusher dogs of the input shaft, and the wedge blocks are enabled to rotate in the same direction, so that normal transmission of the backstop is realized.
The roller and the wedge block bear the backstop torque at the same time, the bearing capacity is strong, the abrasion conditions of the roller and the wedge block are reduced, and the service life of the backstop is prolonged. The connecting line of the symmetrical point of the contact surface of the wedge block and the shell deviates from the axis of the shell and is parallel to the axis, and due to the eccentric structural design of the wedge block, the forward transmission and reverse non-return of the non-return device are realized. The both sides of the wedge block are designed into arc surfaces, so that the contact between the wedge block and the shell is increased, and the stress of the contact area between the wedge block and the shell is reduced. Simple structure, low processing difficulty and low cost. The high reliability requirement of electromechanical servo is met.
Those skilled in the art will appreciate that the invention may be practiced without these specific details.

Claims (10)

1. The utility model provides a two redundant two-way backstop which characterized in that: the device comprises a first deep groove ball bearing (13), a second deep groove ball bearing (14), an input shaft (2), a shell (3), an output shaft (4), a gasket (5), a straight spring (6), a truncated cone spiral spring (7), a wedge block (8), a roller and a clamp spring (51);
the output shaft (4) is integrally processed and comprises two cylinders with different diameters, and the second deep groove ball bearing (14) is sleeved on the small cylinder of the output shaft (4) through a gasket (5); two bulges are symmetrically processed on the side wall of the large cylinder of the output shaft (4), the two sides of each bulge are processed into wedging surfaces, each bulge is processed with two round holes, a compressed straight spring (6) is placed in each round hole, the wedging surfaces on the two sides of each bulge on the large cylinder of the output shaft (4) are respectively provided with a roller, and the rollers are kept in contact with the straight springs (6) after being installed in place; a groove is machined in the large cylinder of the output shaft (4) along the axial direction;
a circular groove is processed in the center of the wedge block (8), the large end face of the truncated cone helical spring (7) is installed in the circular groove, and the wedge block (8) and the truncated cone helical spring (7) form an integral structure which is placed in a groove of a large cylinder of the output shaft (4);
the first deep groove ball bearing (13) is sleeved on the input shaft (2); four shifting claws are machined on the input shaft (2), four gaps are formed among the four shifting claws, and two opposite gaps are identical in width and are called a pair of gaps; in the two pairs of gaps, the width of one pair of gaps is larger than that of the other pair of gaps;
the wedge surface of the output shaft (4) provided with the roller is sleeved in the gap with larger width of the input shaft (2), and the wedge block (8) is sleeved in the gap with smaller width; the integrated structure after being assembled in place is arranged in the shell (3), and two ends of the integrated structure are limited by the clamp springs (51).
2. The dual redundant bidirectional backstop of claim 1, wherein: the groove on the large cylinder of the output shaft (4) is of an up-and-down asymmetric structure.
3. The dual redundant bidirectional backstop of claim 1, wherein: arc grooves are processed on the two circular lobes of the large cylinder of the output shaft (4) except the groove structure, and after the large cylinder is installed in place, the small end face of the truncated cone helical spring (7) is propped against the arc grooves.
4. The dual redundant bidirectional backstop of claim 1, wherein: the section of the wedge block (8) is trapezoidal, and the long edge of the wedge block (8) is in arc contact with the contact surface of the shell and is tangent to the inner wall of the shell.
5. The dual redundant bidirectional backstop of claim 4, wherein: the shell is hollow columnar structure, and during the installation, the casing axis is deviated with the connecting wire of the symmetric point on two contact surfaces of voussoir long limit and shell, and is parallel with the axis.
6. The dual redundant bidirectional backstop of claim 5, wherein: when the wedge is in work, the stress of any pair of contact points on the long edge of the wedge and two contact surfaces of the shell is marked as F1 and F2, and the wedge angles of F1 and F2 are theta respectively1、θ2，θ1And theta2It should satisfy:
θ2≤θ1＝5.71°。
7. the dual redundant bidirectional backstop of claim 1, wherein: the input shaft (2) is connected with an external structure through a flat key.
8. The dual redundant bidirectional backstop of claim 1, wherein: when in work, the wedge angle of the roller should satisfy alpha less than or equal to 2 rhocWhere α is the roller wedge angle, ρcIs the rubbing angle.
9. The dual redundant bidirectional backstop of claim 1, wherein: the friction angle refers to an included angle between a contact line of the roller and the inner wall of the shell and a contact line of the roller and the wedging surface of the output shaft.
10. The dual redundant bidirectional backstop of claim 1, wherein: the section of the large cylindrical groove of the output shaft (4) is rectangular.
CN202011127703.2A 2020-10-20 2020-10-20 Dual-redundancy bidirectional backstop Pending CN112377537A (en)

Priority Applications (1)

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CN202011127703.2A CN112377537A (en) 2020-10-20 2020-10-20 Dual-redundancy bidirectional backstop

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Application Number Priority Date Filing Date Title
CN202011127703.2A CN112377537A (en) 2020-10-20 2020-10-20 Dual-redundancy bidirectional backstop

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CN112377537A true CN112377537A (en) 2021-02-19

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114006499A (en) * 2021-11-09 2022-02-01 广东常明机电有限公司 Roller blind motor comprising a reverse braking actuator
CN114017449A (en) * 2021-11-03 2022-02-08 泉州恒毅机械有限公司 Bidirectional overrunning clutch and transmission mode

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201802787U (en) * 2010-07-30 2011-04-20 西安威盛电子仪器有限公司 Bidirectional wedge block type clutch
CN201851532U (en) * 2010-11-19 2011-06-01 北京新兴超越离合器有限公司 Block and post combined type two-way overrunning clutch
CN202674098U (en) * 2012-06-15 2013-01-16 山东大学 Special backstop for rolling machine of vegetal greenhouse
CN104595478A (en) * 2015-01-26 2015-05-06 吉林大学 Mechanical type automatic transmission gear selecting and shifting actuation mechanism for vehicle
JP2017040336A (en) * 2015-08-21 2017-02-23 Ntn株式会社 Power transmission device
CN211456911U (en) * 2020-03-03 2020-09-08 长沙矿山研究院有限责任公司 Non-return brake composite driving device for continuous lifting system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201802787U (en) * 2010-07-30 2011-04-20 西安威盛电子仪器有限公司 Bidirectional wedge block type clutch
CN201851532U (en) * 2010-11-19 2011-06-01 北京新兴超越离合器有限公司 Block and post combined type two-way overrunning clutch
CN202674098U (en) * 2012-06-15 2013-01-16 山东大学 Special backstop for rolling machine of vegetal greenhouse
CN104595478A (en) * 2015-01-26 2015-05-06 吉林大学 Mechanical type automatic transmission gear selecting and shifting actuation mechanism for vehicle
JP2017040336A (en) * 2015-08-21 2017-02-23 Ntn株式会社 Power transmission device
CN211456911U (en) * 2020-03-03 2020-09-08 长沙矿山研究院有限责任公司 Non-return brake composite driving device for continuous lifting system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114017449A (en) * 2021-11-03 2022-02-08 泉州恒毅机械有限公司 Bidirectional overrunning clutch and transmission mode
CN114017449B (en) * 2021-11-03 2024-05-17 泉州恒毅机械有限公司 Bidirectional overrunning clutch and transmission mode
CN114006499A (en) * 2021-11-09 2022-02-01 广东常明机电有限公司 Roller blind motor comprising a reverse braking actuator

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Application publication date: 20210219