CN202560898U - Boosting type braking load-limiting coupling - Google Patents
Boosting type braking load-limiting coupling Download PDFInfo
- Publication number
- CN202560898U CN202560898U CN2012201009211U CN201220100921U CN202560898U CN 202560898 U CN202560898 U CN 202560898U CN 2012201009211 U CN2012201009211 U CN 2012201009211U CN 201220100921 U CN201220100921 U CN 201220100921U CN 202560898 U CN202560898 U CN 202560898U
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- coupling
- afterburning
- lever
- ring
- braking
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- Expired - Fee Related
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Abstract
The utility model relates to a boosting type braking load-limiting coupling. The coupling comprises an upper end cover assembly, a spring seat, a shaft blocking ring, a bearing, a hole blocking ring, a driving coupling, a large support, a boosting lever assembly, a lever boosting ring, a plane bearing, a braking ring, a friction piece support assembly and a lower end cover assembly. The coupling is characterized in that the upper end cover assembly, the spring seat, the shaft blocking ring, the bearing, the hole blocking ring, the driving coupling, the large support, the boosting lever assembly, the lever boosting ring, the plane bearing, the braking ring, the friction piece support assembly and the lower end cover assembly are sequentially connected in series along an axial lead direction of the large support. By the aid of the meshing of gear teeth of the driving coupling and a driven coupling and the pressure of a braking spring, the transmission is performed. When spiral gear teeth of the driving coupling and the driven coupling are separated, the overloading is performed and machines are protected. When machines are shut down, the spring seat pushes the boosting lever assembly to pressure the friction piece support assembly, the boosting braking moment is formed and the braking is achieved.
Description
Technical field
The utility model relates to a kind of afterburning formula braking limit for tonnage coupling.
Background technique
Existing braking limit for tonnage coupling has the function of coupling, load limiter and break; Can reach the effect of shaft coupling transmission; When machine can be protected machine when overloading, also can brake, but braking moment is little because of stopping of machine at once; And power loss is very big when work, and therefore existing braking limit for tonnage coupling can not adapt to the working environment that requires very large braking moment and high mechanical efficiency.
Summary of the invention
The purpose of the utility model: design a kind of existing shaft coupling and limit for tonnage function, very big braking moment is arranged again, the braking limit for tonnage coupling that machinery driving efficiency is high remedies existing deficiency of braking the limit for tonnage coupling.
The utility model solves the technological scheme that its technical problem adopted:
Afterburning lever is assemblied on the big support through pivot pin; Two miniature bearings are assemblied on the power end and afterburning end of afterburning lever through two bearing pivot pins respectively, and spring seat is positioned on the active coupling with back-up ring through shaft block ring A, rolling bearing and hole, and many brake springs become to be arranged in parallel; One end pressing spring seat; The other end withstands afterburning pivot pin, and the miniature bearing of the afterburning end of afterburning lever directly is pressed on the afterburning ring of lever along the direction of axis line of big support, and plane bearing one is positioned on the afterburning ring of lever with cylindrical; The endoporus of plane bearing one becomes transition fit to connect with brake hoop, brake hoop and friction plate end face are fitted
Upper end cap assembly parts, spring seat, shaft block ring, bearing, hole are with back-up ring, initiatively coupling, big support, afterburning lever combination part, the afterburning ring of lever, plane bearing, brake hoop, friction disc support assembly parts and lower end cap assembly parts be along direction of axis line coupled in series successively.
Locking nut is fixed on the upper end cap through locked spacer; Afterburning ring is close to locked spacer; As the stressed fulcrum of afterburning pivot pin, energy stored drive spring seat moves to the friction disc support direction vertically during the brake spring compression, and the conical surface on the spring seat promotes to be installed in the miniature bearing on the afterburning lever; Make the lever reinforcing press the afterburning ring of lever pressure is passed to friction disc support assembly and driven coupling brake disc through plane bearing and brake hoop, produce big braking moment.
Driven coupling is the coupling that is fixed on the driven shaft; Initiatively coupling is installed on the driving shaft through spline and (refers generally to motor shaft); Friction disc support is stuck on the big support, and a certain amount of displacement is arranged vertically, can not produce angular displacement; The friction disc support two sides is glued to the friction disc support two sides through the gummed ways of connecting, is installed in vertically between brake hoop and the driven coupling brake disc.
Initiatively coupling and driven coupling are realized the transmission of moment of torsion owing to the helical tooth flank engagement adds the axial pressure effect of pressure spring, reach the function of shaft coupling.During overload, broken balance of axial force, in order to reach the balance with brake spring pressure; Initiatively coupling has only mobile to the back-end vertically; Drive spring seat compression brake spring, throw off fully, the effect of working machine of having played overload protection up to active coupling and driven coupling profile of tooth.When the active coupling runs out of steam; Energy stored discharged immediately when brake spring was compressed; When the braking conical surface through spring seat promoted the afterburning ring of lever, plane bearing, brake hoop and friction plate assembly and produces friction, friction plate assembly produced friction with driven coupling brake disc, acts on because lever is afterburning; Formation has strengthened many times braking moment, has realized the purpose of braking.
Upper end cap or lower end cap adopt and are bolted on the frame of working machine, upper end cap and lower end cap adopt Bolt Connection support greatly two ends.
The sliding bearing sleeve cylindrical adopts the mode of interference fit to connect with the upper end cap endoporus; Many afterburning pivot pins distribute equably and are inserted in the upper end cap axis hole, and become slip cooperating relationship, and every adds and puts an identical brake spring on the mechanical axis respectively; Afterburning ring withstands many and adds mechanical axis; The spring adjusting nut is spun in the upper end cap screw thread, after adjusting is accomplished, and locking with the locked spacer locking.
The lever pivot pin is fixed on lever on the big support.
There is a place to promote the braking conical surface that lever is used on the spring seat.
The lever reinforcing is to utilize the conical surface of spring seat to promote lever to push down the afterburning ring of lever along the swing of lever pivot pin; And move to friction plate assembly parts direction vertically; Successively power is passed to plane bearing, brake hoop, friction plate, friction disc support, friction plate and driven coupling brake disc, afterburning size is relevant with lever ratio.
The beneficial effect of the utility model is; The function that not only possesses coupling; Simultaneously have the function of break and load limiter again, played to shut down and braked immediately and protection working machine effect when transshipping, and how extraordinarily big braking moment and improved the machinery driving efficiency effect.
Below in conjunction with Figure of description the utility model is specified.
Description of drawings
Accompanying drawing 1: afterburning formula braking limit for tonnage coupling profile schematic representation.
Accompanying drawing 2: afterburning formula braking limit for tonnage coupling overall structure figure.
Accompanying drawing 3: brake hoop and active coupling assembly relation schematic representation in the afterburning formula braking limit for tonnage coupling.
Accompanying drawing 4: afterburning formula braking big support of limit for tonnage coupling and afterburning lever combination part schematic representation.
Accompanying drawing 5: friction disc support assembly parts schematic representation.
Accompanying drawing 6: afterburning formula braking limit for tonnage coupling upper end cap assembly parts.
Accompanying drawing 7: afterburning formula braking limit for tonnage coupling lower end cap assembly parts.
Accompanying drawing 8: the afterburning lever combination part of afterburning formula braking limit for tonnage coupling.
Accompanying drawing 9: spring seat structural representation.
Accompanying drawing 10: afterburning formula braking limit for tonnage coupling brake hoop, friction plate and driven coupling position when shutting down braking state concern schematic representation.
Accompanying drawing 11: afterburning formula braking limit for tonnage coupling brake hoop, friction plate and driven coupling position when starting and working state concern schematic representation.
Accompanying drawing 12: relative position relation intention when brake hoop is with the work of active coupling in the afterburning formula braking limit for tonnage coupling.
Accompanying drawing 13: relative position relation intention when brake hoop is shut down braking with the active coupling in the afterburning formula braking limit for tonnage coupling.
In the accompanying drawing: 1-lower end cap, 2-bolt A, 3-spring washer B, the big support of 4-, 5-lever pivot pin, the afterburning lever of 6-, 7-miniature bearing; 8-bearing pivot pin, 9-bolt B, 10-spring washer B, the afterburning ring of 11-, 12-spring adjusting nut, 13-upper end cap; 14-is coupling initiatively, 15-shaft block ring, 16-bearing, 17-sliding bearing sleeve, 18-spring seat, 19-locked spacer; The afterburning pivot pin of 20-, 21-circlip for hole, 22-brake spring, the afterburning ring of 23-lever, 24-plane bearing one, 25-brake hoop; The 26-friction disc support, 27-friction plate, the driven coupling of 28-, 29-plane bearing two, 30-rolling bearing, 31-shaft block ring.
Embodiment
Shown in the Figure of description 2: upper end cap 13 is fixed on the big support 4 with spring pad B10 through bolt B 9, and lower end cap 1 is fixed on the big support 4 through bolt A2 and spring pad A3.
Figure of description 2 is with shown in the Figure of description 6: sliding bearing sleeve 17 adopts the mode of interference fit to connect with upper end cap 13, and many afterburning pivot pins 20 are through on the supporting hole of upper end cap 13, and becomes the sliding connection mode; Afterburning ring 11 is enclosed within on the upper end cap 13; And withstand on many afterburning pivot pins 20, spring adjusting nut 12 is regulated axial position along the outside thread on the upper end cap 13, after mixing up; And, prevent to produce angular displacement and axial displacement with locked spacer 19 lockings.
Shown in the Figure of description 2: spring seat 18 is positioned on the active coupling 14 with back-up ring 21 through shaft block ring A15, rolling bearing 16 and hole, and many brake springs are arranged in parallel for 22 one-tenth, an end pressing spring seat 18, and the other end withstands afterburning pivot pin 20.
Shown in Figure of description 2, accompanying drawing 4 and the accompanying drawing 8: afterburning lever combination part is positioned on the big support 4 through pivot pin 5.
Figure of description 2 is with shown in the Figure of description 8: two miniature bearings 7 are assemblied on the power end and afterburning end of afterburning lever 6 through two bearing pivot pins 8.
Shown in the Figure of description 2: the miniature bearing 7 that is installed in the reinforcing end of afterburning lever 6 directly is pressed on the afterburning ring 23 of lever along the direction of axis line of big support 4; Plane bearing 1 is positioned on the afterburning ring 23 of lever with cylindrical; 25 one-tenth transition fit of the endoporus of plane bearing 1 and brake hoop connect, and brake hoop 25 is fitted with friction plate 27 end faces.
Figure of description 2 is with shown in the Figure of description 5: two friction disc supports 26 form with adopting the adhesive bonding connecting of two friction plates 27.
Figure of description 2 is with shown in the Figure of description 7: driven coupling 28 is positioned on the lower end cap 1 through plane bearing 2 29, rolling bearing 30 and shaft block ring B31, and the brake disc on the driven coupling 28 directly contacts with friction plate 27 and produces friction.
Figure of description 2 is with shown in the Figure of description 3: initiatively coupling 14 and brake hoop 25 adopt the splines connection that is slidingly matched.
Figure of description 2 is with shown in the Figure of description 9: the A place promotes the braking conical surface that lever is used on the spring seat 18.
Shown in the Figure of description 10: the B place is in braking state for driven coupling brake disc and friction plate, and the C place is in braking state for brake hoop and friction plate.
Shown in the Figure of description 11: the D place is in disengaged condition for driven coupling brake disc and friction plate, and the E place is in disengaged condition for brake hoop and friction plate.
Figure of description 12 is with shown in the Figure of description 13: the difference of relative position relation was that the latter Duoed a size S than the former when relative position relation was shut down braking with brake hoop 25 and active coupling 14 when brake hoop 25 was with 14 work of active coupling in the afterburning formula braking limit for tonnage coupling; The former S is zero, i.e. assembling is accomplished the relative brake hoop of active coupling and also had a displacement amount backward vertically.
The working procedure of this reinforcing formula braking limit for tonnage coupling: power source is imported from active coupling 14 splined holes; The engagement of the helical tooth flank through active coupling 14 and the helical tooth flank of driven coupling 28 adds the pressure of brake spring 22; Initiatively behind coupling 14 input torques; On active coupling 14 shaft axiss, produce an end thrust of pointing to the power source direction, make coupling 14 initiatively produce axial displacement compression brake springs 22 and reach the balance with spring pressure, at this moment initiatively coupling 14 drives that the afterburning ring of brake hoops 25, plane bearing 1 and lever 23 is reverse to be promoted many afterburning levers 6 and move along the braking conical surface of spring seat 18; Lay down simultaneously and add the braking force that is pressed on the friction plate 27; Brake off, the effect of performance coupling is carried out transmission; When working machine transshipped, initiatively the axial force of coupling 14 upper edge axial directions also increased thereupon, and initiatively coupling 14 must produce displacement along axial direction; Further compression brake spring 22 in order to reach the balance with brake spring 22 thrusts, is thrown off up to the helical tooth flank of active coupling 14 and the spirality flank of tooth of driven coupling 28 fully; This moment, coupling was in the state that skids; Work machine has been protected in no longer transmission, has realized the limit for tonnage protection; Power source is removed; Torque disappears, and the pressure of the brake spring 22 that receives on axially at active coupling 14 also resets into the state before shutting down thereupon, and the energy that this moment, brake spring 22 was saved discharges immediately; Promoting initiatively, coupling 14 moves to driven coupling 28 directions; Drive is positioned at the spring seat 18 same moved further on the coupling 14 initiatively, and the braking conical surface on the spring seat 18 promotes to be installed in the miniature bearing 7 on the afterburning lever 6, drives afterburning lever 6 and gives the lever brake disc that afterburning ring 23 passes on plane bearing 1, brake hoop 25, friction plate 27, friction disc support 26, friction plate 27 and the driven coupling 28 successively through another miniature bearing 7 pressurizations; The brake disc of brake hoop 25 and driven coupling 28 is combined with friction plate 27 respectively; Produce friction, form the braking moment that has strengthened, realize braking.
Afterburning formula braking limit for tonnage coupling is reasonable in design, and compact structure is sensitive reliable, can be widely used in the multiclass mechanical transmission coupling.
Claims (3)
1. an afterburning formula is braked the limit for tonnage coupling; It is characterized in that: afterburning lever (6) is assemblied on the big support (4) through pivot pin (5); Two miniature bearings (7) are assemblied on the power end and afterburning end of afterburning lever (6) through two bearing pivot pins (8) respectively, and spring seat (18) is positioned on the active coupling (14) with back-up ring (21) through shaft block ring A (15), rolling bearing (16) and hole, and many brake springs (22) become to be arranged in parallel; One end pressing spring seat (18); The other end withstands afterburning pivot pin (20), and the miniature bearing (7) of the afterburning end of afterburning lever (6) directly is pressed on the afterburning ring of lever (23) along the direction of axis line of big support (4), and plane bearing one (24) is positioned on the afterburning ring of lever (23) with cylindrical; The endoporus of plane bearing one (24) becomes transition fit to connect with brake hoop (25), brake hoop (25) is fitted with friction plate (27) end face.
2. afterburning formula braking limit for tonnage coupling according to claim 1 is characterized in that: initiatively coupling (14) and brake hoop (25) adopt spline connections that be slidingly matched, initiatively the relative brake hoop (25) of coupling (14) displacement amount backward in addition vertically.
3. afterburning formula braking limit for tonnage coupling according to claim 1 is characterized in that: have a place to promote the braking conical surface that lever is used on the spring seat (18).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012201009211U CN202560898U (en) | 2012-03-15 | 2012-03-15 | Boosting type braking load-limiting coupling |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012201009211U CN202560898U (en) | 2012-03-15 | 2012-03-15 | Boosting type braking load-limiting coupling |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202560898U true CN202560898U (en) | 2012-11-28 |
Family
ID=47210558
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012201009211U Expired - Fee Related CN202560898U (en) | 2012-03-15 | 2012-03-15 | Boosting type braking load-limiting coupling |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202560898U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307155A (en) * | 2012-03-15 | 2013-09-18 | 湖北省咸宁三合机电制业有限责任公司 | Stressing-type brake load-limiting coupler |
| CN105299110A (en) * | 2014-06-25 | 2016-02-03 | 湖北省咸宁三合机电制业有限责任公司 | Power-on de-braking load-limiting coupler |
| CN107489381A (en) * | 2017-09-28 | 2017-12-19 | 山西风雷钻具有限公司 | Antioverloading helicoid hydraulic motor |
-
2012
- 2012-03-15 CN CN2012201009211U patent/CN202560898U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307155A (en) * | 2012-03-15 | 2013-09-18 | 湖北省咸宁三合机电制业有限责任公司 | Stressing-type brake load-limiting coupler |
| CN103307155B (en) * | 2012-03-15 | 2015-10-21 | 湖北省咸宁三合机电制业有限责任公司 | Thrust type braking load-limiting coupler |
| CN105299110A (en) * | 2014-06-25 | 2016-02-03 | 湖北省咸宁三合机电制业有限责任公司 | Power-on de-braking load-limiting coupler |
| CN107489381A (en) * | 2017-09-28 | 2017-12-19 | 山西风雷钻具有限公司 | Antioverloading helicoid hydraulic motor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20121128 Termination date: 20140315 |