CN202560899U - Double tooth surface stressing type braking and load limiting coupler - Google Patents
Double tooth surface stressing type braking and load limiting coupler Download PDFInfo
- Publication number
- CN202560899U CN202560899U CN2012201009372U CN201220100937U CN202560899U CN 202560899 U CN202560899 U CN 202560899U CN 2012201009372 U CN2012201009372 U CN 2012201009372U CN 201220100937 U CN201220100937 U CN 201220100937U CN 202560899 U CN202560899 U CN 202560899U
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- coupling
- afterburning
- braking
- lever
- ring
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Abstract
The utility model relates to a double tooth surface stressing type braking and load limiting coupler which comprises an upper end cover assembly, a spring seat, a shaft retainer ring, a bearing, a hole retainer ring, a driving coupler, a large support, a stressing lever assembly, a lever stressing ring, a plane bearing, a braking ring, a friction plate support assembly and a lower end cover assembly. The double tooth surface stressing type braking and load limiting coupler is characterized in that the upper end cover assembly, the spring seat, the shaft retainer ring, the bearing, the hole retainer ring, the driving coupler, the large support, the stressing lever assembly, the lever stressing ring, the plane bearing, the braking ring, the friction plate support assembly and the lower end cover assembly are sequentially connected with one another in a series mode along a shaft axis direction of the large support. Inner layer tooth surfaces of the driving coupler and a driven coupler are meshed with each other to perform transmission and remove braking; outer layer helical tooth surfaces of the driving coupler and the driven coupler are separated to achieve overload protection of a working machine; and when the machine stops working, the spring seat pushes the stressing lever assembly to stress the friction plate support assembly to form enlarged braking torque further to achieve braking.
Description
Technical field
The utility model relates to the afterburning formula braking of a kind of bidentate face 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,, also can brake at once because of stopping of machine when machine can be protected machine when overloading; But braking moment is little; And power loss is very big when work, and under the little situation of load, braking is difficult for removing; Cause the whole heating of braking limit for tonnage coupling, 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, and under the very little situation of load; Braking is easy to remove, and remedies the deficiency of existing braking 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; 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 an end pressing spring seat; The other end withstands afterburning pivot pin; The miniature bearing of the reinforcing 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, and the endoporus of plane bearing one becomes transition fit to connect with brake hoop; The friction plate end face is fitted in brake hoop and the friction plate assembly, and the brake disc of another friction plate and driven coupling is fitted in the friction plate assembly.
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 plate assembly 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 plate 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.
Driven coupling adopts double-layer spiral flank of tooth structure; Initiatively coupling adopts double-layer spiral flank of tooth structure.
Initiatively coupling and driven coupling be owing to adopt the helical tooth flank of two-layer different helix angles, the helix angle of internal layer helical tooth flank big (starting helicoid) wherein, the helix angle of outer helical tooth flank less (working screw face).When machine start, initiatively coupling and driven coupling internal layer starting helicoid meshes at first, because the helix angle of starting helicoid is bigger; The axial force that the engagement back produces is bigger; When the axial force that produces had exceeded the axial pressure of brake spring, initiatively coupling moved axially to the rear of the flank of tooth, drove spring seat and moved after together; Eliminated and added the pressure that is pressed on the friction plate; Removed braking, active coupling and driven coupling starting this moment helicoid has been thrown off, and the working screw face begins engagement; Initiatively the axial force of the working screw face of coupling and driven coupling generation and the axial force balance of brake spring reach the function that is easy to brake off and shaft coupling.During overload; Broken balance with brake spring pressure; In order to reach the balance with brake spring pressure; Initiatively coupling has only vertically to the further compression brake spring in active coupling rear, throws off fully up to active coupling and the outer helical tooth flank of driven coupling, has played the effect of overload protection working machine.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 promotes the afterburning ring of lever, plane bearing, brake hoop and friction plate assembly and produces friction; Friction plate assembly and driven coupling brake disc produce friction, have realized 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.
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 the friction plate assembly 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 protect the working machine effect when transshipping, under the very little situation of load; Be easy to brake off, and strengthened braking moment and improved machinery driving efficiency.
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 plate assembly 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.
Accompanying drawing 14: driven coupling shape assumption diagram.
Accompanying drawing 15: active coupling shape assumption diagram.
Accompanying drawing 16: initiatively coupling and driven coupling are in working state engagement situation schematic representation.
Accompanying drawing 17: initiatively coupling and driven coupling are in starting state engagement situation schematic representation.
Accompanying drawing 18: initiatively coupling and driven coupling exchange to working screw face schematic representation from the starting helicoid.
Accompanying drawing 19: initiatively coupling and driven coupling are in static braking state profile of tooth mesh schematic representation.
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, and riveted is fixed in the aperture.
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; Friction plate 27 end faces are fitted in brake hoop 25 and the friction plate assembly, and another friction plate 27 is fitted with the brake disc of driven coupling 28 in the friction plate assembly.
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 B 31, 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.
Shown in the Figure of description 14: the F place uses the right hand helix face for work in the driven coupling, and the H place uses left-handed helicoid for work, and the G place employs the right hand helix face, and the J place employs left-handed helicoid.
Shown in the Figure of description 15: initiatively 0 place is that the right hand helix face is used in work in the coupling, and the Q place uses left-handed helicoid for work, and the P place employs the right hand helix face, and the R place employs left-handed helicoid.
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.
Figure of description 2 is with shown in the Figure of description 14: driven coupling 28 adopts bidentate face structure, and wherein internal layer flank of tooth helix angle is greater than outer flank of tooth helix angle.
Figure of description 2 is with shown in the Figure of description 15: initiatively coupling 14 adopts bidentate face structures, and wherein internal layer flank of tooth helix angle is greater than outer flank of tooth helix angle, and with driven coupling 28 internal and external layer flank of tooth helix angles coupling.
The working procedure of the afterburning formula braking of this bidentate face limit for tonnage coupling: power source is imported from active coupling 14 splined holes; Internal layer starting helical tooth flank through active coupling 14 has produced the end thrust greater than brake spring with the engagement that the internal layer of driven coupling 28 starts helical tooth flank; Brake off; After initiatively coupling 14 input torques are stablized or are continued to strengthen; Initiatively coupling 14 exchanges to outer working screw face with driven coupling 28 internal layers starting helicoid, produces axial displacement compression brake springs 22 and reaches the balance with spring pressure in order to reach coupling 14 initiatively, and 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 outer working screw flank of tooth of active coupling 14 and the outer working screw flank of tooth of driven coupling 28 fully; This moment, coupling was in the state that skids; 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 (6)
1. the afterburning formula of bidentate face 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; 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 an end pressing spring seat (18); The other end withstands afterburning pivot pin (20); The miniature bearing (7) of the reinforcing 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, and the endoporus of plane bearing one (24) becomes transition fit to connect with brake hoop (25); Friction plate (27) end face is fitted in brake hoop (25) and the friction plate assembly, and another friction plate (27) is fitted with the brake disc of driven coupling (28) in the friction plate assembly.
2. according to the afterburning formula braking of the said bidentate face of claim 1 limit for tonnage coupling, it is characterized in that: driven coupling (28) adopts double-layer spiral flank of tooth structure, and initiatively coupling (14) adopts double-layer spiral flank of tooth structure.
3. the afterburning formula braking of bidentate face according to claim 1 limit for tonnage coupling is characterized in that: internal layer flank of tooth helix angle is greater than outer flank of tooth helix angle in the driven coupling (28), and initiatively the middle internal layer flank of tooth helix angle of coupling (14) is greater than outer flank of tooth helix angle.
4. the afterburning formula braking of bidentate face according to claim 1 limit for tonnage coupling is characterized in that: driven coupling (28) and active coupling (14) internal and external layer flank of tooth helix angle are complementary.
5. the afterburning formula braking of bidentate face according to claim 1 limit for tonnage coupling is characterized in that: have a place to promote the braking conical surface that lever is used on the spring seat (18).
6. the afterburning formula braking of bidentate face according to claim 1 limit for tonnage coupling; It 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012201009372U CN202560899U (en) | 2012-03-15 | 2012-03-15 | Double tooth surface stressing type braking and load limiting coupler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012201009372U CN202560899U (en) | 2012-03-15 | 2012-03-15 | Double tooth surface stressing type braking and load limiting coupler |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202560899U true CN202560899U (en) | 2012-11-28 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012201009372U Expired - Fee Related CN202560899U (en) | 2012-03-15 | 2012-03-15 | Double tooth surface stressing type braking and load limiting coupler |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202560899U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307156A (en) * | 2012-03-15 | 2013-09-18 | 湖北省咸宁三合机电制业有限责任公司 | Double-toothed-surface forced braking and load-limitation coupling |
| 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 |
-
2012
- 2012-03-15 CN CN2012201009372U patent/CN202560899U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307156A (en) * | 2012-03-15 | 2013-09-18 | 湖北省咸宁三合机电制业有限责任公司 | Double-toothed-surface forced braking and load-limitation coupling |
| CN103307156B (en) * | 2012-03-15 | 2015-11-25 | 湖北省咸宁三合机电制业有限责任公司 | Bidentate face 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 |
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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 |