CN202883816U

CN202883816U - Swing type bidirectional overrunning clutch

Info

Publication number: CN202883816U
Application number: CN 201220595495
Authority: CN
Inventors: 吴长钰
Original assignee: Individual
Current assignee: Individual
Priority date: 2012-11-13
Filing date: 2012-11-13
Publication date: 2013-04-17
Anticipated expiration: 2022-11-13

Abstract

A swing type bidirectional overrunning clutch solves the problem of how to completely return a drive end of a swing type bidirectional overrunning clutch to an original position. The swing type bidirectional overrunning clutch comprises a driving component, a driven component, a shifting fork and a rolling element, the shifting fork comprises internal claws, and the internal claws and the rolling element are positioned in a cavity formed by the driving component and the driven component. In a drive stroke, the shifting fork lags behind the driving component by one angle. In a return stroke, the shifting fork overruns the driving component by one angle, so that the shifting fork returns to a middle point before the driving component returns to the original position, effective torque applied to the shifting fork in the direction consistent with the return stroke direction is higher than the sum of resistance torque applied to the shifting fork in the direction opposite to the return stroke direction at least when the shifting fork is positioned at the middle point, the shifting fork crosses the middle point and continues to rotate along the return stroke direction, and the driving component continues to rotate. Finally, the shifting fork deviates from the middle point by one angle along the return stroke direction, and the driving component returns to the original position.

Description

The swing type double rolling key clutch

Technical field

The utility model relates to mechanical clutch, and specifically, the utility model provides the swing type double rolling key clutch that makes its drive end get back to initial position fully when backhaul.

Background technique

Free wheel device is that a kind of rotating speed based on driving link and Passive part is different and realize the clutch of automatic clutch function.Mono-directional overrun clutch is a known technology, and its driving link only has a rotation direction, when the rotating speed of driving link surpasses the rotating speed of Passive part, and the automatic combination of driving link and Passive part; When the rotating speed of driving link was lower than the rotating speed of Passive part, driving link separated automatically with Passive part.

When the driving link of free wheel device has two rotation directions (clockwise with counterclockwise), just need to use double rolling key clutch, existing background technique about double rolling key clutch is as follows.

In " mechanical design handbook " 5-276 page or leaf that China's chemical industry publishing house published in 2004, double rolling key clutch has been proposed basic theories: " compare with the one-way type roller overrunning clutch, working surface and roller change adjacent symmetric into by unidirectional layout and arrange.No matter outer shroud and star-wheel which be initiatively, can both both direction transmission campaign and torque, and can motion be interrupted by pusher dog, be a kind of reversing clutch ".

The technical problem how existing double rolling key clutch technology makes drive end get back to initial position fully when backhaul when not relating to double rolling key clutch being used for the occasion of swing type operation.

Summary of the invention

The technical problems to be solved in the utility model is the problem that how to make the drive end of swing type double rolling key clutch get back to initial position fully when backhaul.

The technical solution of the utility model is described below.

The utility model comprises driving component, passive component, rolling element, shift fork, and shift fork comprises interior to pawl, interiorly all is positioned at the cavity that driving component and passive component form to pawl and rolling element.Passive component connects with the load of the utility model demand motive.

In discussion of the present utility model, relational language defines and is explained as follows.

The swing type double rolling key clutch refers to that the drive end of this double rolling key clutch can carry out the swing type operation clockwise or counterclockwise.

Drive end refers to driving component.

Drive stroke and refer to that driving component drives the working stroke of passive component under external force.In driving stroke, driving component and passive component are in engagement, and driving component departs from its initial position under external force, thereby drive the passive component motion; Rolling element and shift fork also can move along driving direction.

Backhaul refers to after driving stroke, driving component is to the stroke of initial position return.In backhaul, driving component is in passive component and separates (removing engagement) state, and driving component carries out returning movement to its initial position, and rolling element and shift fork also move along the backhaul direction.

Initial position refers to the position of driving component, that driving component is driving stroke and the common start position that drives counterclockwise stroke clockwise, when clockwise driving stroke and the rotation amplitude that drives counterclockwise stroke are set as when consistent, initial position is that driving component is at the middle position of two rotation amplitudes.

Intermediate point refers to the position of shift fork, be the clockwise driving stroke of driving component with drive counterclockwise in the stroke, the common start position of shift fork, when the clockwise driving stroke of driving component and the counterclockwise rotation amplitude of driving stroke are set as when consistent, intermediate point is the middle position of the rotation amplitude of shift fork in the driving stroke at both direction.

Effective torque refers to, in backhaul when shift fork is positioned at intermediate point and after crossing intermediate point, the moment consistent with the backhaul direction that is subject to of shift fork.

Press the residing position of driving component, can driving component be set to the outer ring part of structure, then passive component is inner round portion; Also can driving component be set to the inner round portion of structure, then passive component is the outer ring part.

The cavity that driving component and passive component form comprises paired wedge shape space, rolling element is positioned at wedge shape space, rolling element also is to occur in pairs, and rolling element can be roller, needle roller or ball, also the cross section of rolling element can be made other curve shape that needs.Rolling element is divided into two groups, and one group is the rolling element of clockwise group, and the responsible engagement driving that drives clockwise stroke drives in the stroke clockwise, and the rolling element of clockwise group is positioned at the small end of wedge shape space, plays engagement driving; Another group is the rolling element of counterclockwise group, and the responsible engagement driving that drives counterclockwise stroke drives in the stroke counterclockwise, and the rolling element of counterclockwise group is positioned at the small end of wedge shape space, plays engagement driving.

Shift fork comprises interior to pawl, interior be positioned at rolling element to pawl by, interiorly be positioned at the cavity that driving component and passive component form to pawl.

Now take clockwise driving stroke and counterclockwise backhaul as example working principle of the present utility model is described.

Drive clockwise stroke: the external force clockwise direction drives drive end, and the rolling element three of driving component, passive component, clockwise group is in engagement, clockwise rotates thereby drive passive component; And the rolling element that organize this moment counterclockwise is in separated state, and the rolling element that will organize counterclockwise to pawl in the shift fork is pushed the large extreme direction of wedge shape space to, and rolling element, the shift fork of group also can clockwise rotate along with driving component counterclockwise; Shift fork is driving in the stroke clockwise, can be subject to the resistance opposite with driving direction (source of resistance is described in an embodiment), make shift fork than the driving component angle that lags behind, that is the shift fork angle that departs from its intermediate point depart from the angle of its initial position less than driving component.

Counterclockwise backhaul: after entering counterclockwise backhaul, the rolling element of driving component, passive component, clockwise group always is in separation (removing engagement) state; Counterclockwise under the effect of pawl and be positioned at the large end of wedge shape space, driving component, passive component, the rolling element three of group also is in separated state to the rolling element of group counterclockwise in shift fork; It is motionless that passive component keeps under the effect of load, and driving component carries out returning movement under the effect of staff or other power; In backhaul, shift fork can be subject to the power consistent with the backhaul direction (source of power is described in an embodiment), makes shift fork also make returning movement.

In counterclockwise backhaul, as previously mentioned since shift fork in driving stroke than the driving component angle that lags behind, so in backhaul, can be understood as shift fork than the super previous angle of driving component, thereby cause before driving component is got back to its initial position, shift fork gets back to first intermediate point; At this moment, be positioned at intermediate point at shift fork, when driving component does not also arrive its initial position, as long as the effective torque consistent with the backhaul direction that be subject to of shift fork is greater than that this moment, shift fork was subject to and the resisting moment sum backhaul opposite direction, then shift fork is just crossed the intermediate point continuation and is rotated an angle along the backhaul direction, make driving component, passive component, the rolling element three of group keeps separated state counterclockwise, make driving component can continue revolution, until driving component (drive end) is got back to its initial position fully, this moment, shift fork also arrived its backhaul terminal point, and obviously the backhaul terminal point of shift fork has been crossed intermediate point.

Owing to comprising paired wedge shape space and paired rolling element in the cavity that driving component and passive component form, and rolling element comprises clockwise group rolling element and the rolling element of organizing counterclockwise, can in like manner analyze obviously, in driving counterclockwise stroke and clockwise backhaul thereof, also can realize driving and in backhaul, making drive end get back to its initial position fully.

No matter driving component is positioned at the inner round portion of structure or is positioned at the outer ring part, above-mentioned principle all can realize, not give unnecessary details herein.

According to above-mentioned discussion, the technological scheme that can summarize the swing type double rolling key clutch that the utility model provides is: in backhaul, when shift fork is positioned at intermediate point, the effective torque consistent with the backhaul direction that shift fork is subject to is greater than that this moment, shift fork was subject to and the resisting moment sum backhaul opposite direction, make shift fork be rotated further an angle along the backhaul direction, thereby make driving component and passive component continue to keep separated state, so that drive end can be got back to its initial position fully.Obviously, after shift fork is crossed intermediate point, can make shift fork continue to turn round along the backhaul direction because of inertia, the effective torque consistent with the backhaul direction that also can continue shift fork is subject to that be subject to greater than shift fork with the resisting moment sum backhaul opposite direction, thereby make shift fork continue to rotate along the backhaul direction.

Combine it, the important feature that goes out the swing type double rolling key clutch that the utility model provides is: in backhaul, at least when shift fork is positioned at intermediate point, the effective torque consistent with the backhaul direction that shift fork is subject to that be subject to greater than shift fork with the resisting moment sum backhaul opposite direction, make the backhaul terminal point of shift fork cross the intermediate point of shift fork.

Simultaneously, the drive end that makes the swing type double rolling key clutch that can summarize the utility model provides is got back to initial position fully in backhaul method: the control step of its backhaul is, in backhaul, shift fork and driving component are all turned round, and before driving component is got back to initial position, make shift fork get back to intermediate point; Then, be positioned at intermediate point and driving component when also not getting back to initial position at shift fork, make shift fork cross intermediate point and continue along the backhaul direction to rotate, driving component continues revolution simultaneously; Last shift fork departs from angle of intermediate point along the backhaul direction, and driving component is got back to initial position.

According to the above, the utility model provides the swing type double rolling key clutch that makes its drive end can get back to initial position fully when backhaul, compared with prior art, good result of the present utility model is: behind each this double rolling key clutch of manipulation, its drive end can be got back to initial position fully.

Description of drawings

Fig. 1 is that embodiment one driving component is at initial position, the shift fork schematic diagram at intermediate point.

Fig. 2 is the A--A cross-sectional schematic of Fig. 1.

Fig. 3 is that E-E of Fig. 1 is to partial schematic sectional view.

Fig. 4 is that the F of Fig. 2 is to partial schematic diagram.

Schematic diagram when Fig. 5 is clockwise drives of the present embodiment one.

Fig. 6 is the schematic diagram of the counterclockwise backhaul of the present embodiment one.

Fig. 7 is the schematic diagram that the shift fork in the counterclockwise backhaul of the present embodiment one is got back to intermediate point.

Continue revolution and driving component after the shift fork that Fig. 8 is the present embodiment one in counterclockwise backhaul is got back to intermediate point and get back to the schematic diagram of initial position fully.

Fig. 9 is the improved schematic diagram of the export-oriented pawl of elasticity power-assisted assembly, bounding means and shift fork to Fig. 1 of embodiment one.

Figure 10 is the improvement schematic diagram to Fig. 2 of embodiment one.

Figure 11 is the another improved schematic diagram to Fig. 2 of embodiment one.

Figure 12 is that embodiment two driving component when not driving is positioned at the schematic diagram that initial position, shift fork are positioned at the state of rest of intermediate point.

Figure 13 is the B--B cross-sectional schematic of Figure 12.

Figure 14 is that the C--C of Figure 13 analyses and observe partial schematic diagram.

Figure 15 is the improved schematic diagram to the elasticity power-assisted assembly of Figure 12 of embodiment two.

Figure 16 is that embodiment three driving component when not driving is positioned at the schematic diagram that initial position, shift fork are positioned at the state of rest of intermediate point.

Figure 17 is the D--D cross-sectional schematic of Figure 16.

Embodiment

(embodiment one).

The present embodiment one provides preferential mode of execution of the present utility model.

In Fig. 1,1 is out star wheel; 2 is small pressure spring, and small pressure spring 2 can replace with shell fragment or rubber parts or other elastic component; 301 is the rolling element of organizing clockwise, and 302 is the rolling element of organizing counterclockwise; 401 is the interior to pawl of shift fork, and 402 is the export-oriented pawl of shift fork, interiorly all is fixed on the shift fork to pawl 401 and export-oriented pawl 402, belongs to the part of shift fork; 5 is interior ring; 6 is elasticity power-assisted assembly, is torsion spring herein, and 601 and 602 is two curved pawls of torsion spring 6; In driving stroke, torsion spring 6 provides the resistance opposite with driving direction to shift fork.7 is bounding means, and bounding means 7 is a plate herein, and bounding means 7 plays the effect that the curved pawl 601 of torsion spring and 602 are installed.

In Fig. 1, out star wheel 1 belongs to driving component, and interior ring 5 belongs to passive component, has spline and load to connect on the interior ring 5; Clearly out star wheel 1 is positioned at the outer ring part, and interior ring 5 is positioned at inner round portion.Have three interior dogs 101 and interior ring 5 Spielpassung on the out star wheel 1; Comprise six wedge shape spaces in the cavity that out star wheel 1 and interior ring 5 form.Six small pressure springs 2, three clockwise the rolling elements 301 of group and three counterclockwise group rolling element 302, and the interior of shift fork all be positioned at the cavity that out star wheel 1 and ring 5 form to pawl 401; Shift fork interior between the rolling element 301 of clockwise group and the rolling element 302 of organizing counterclockwise, and has the gap of circumferencial direction to pawl 401; Small pressure spring 2 rolling element 301,302 and the interior dog 101 of out star wheel between.When static, the elastic force of small pressure spring 2 is pushed

rolling element

301 and 302 to the small end of wedge shape space.The export-oriented pawl 402 of torsion spring 6, bounding means 7 and shift fork is positioned at outside the cavity of out star wheel 1 and ring 5 formation.Two curved pawls 601 of

torsion spring

6 and 602 are installed on the both sides of bounding means 7, two curved pawls 601,602 and bounding means 7 form one less than 180 ° circumferential working space, the export-oriented pawl 402 of shift fork is positioned at this circumferential working space and circular gap is arranged, and between the export-oriented pawl 402 of shift fork and the curved pawl 601 of torsion spring and 602 circular gap is arranged all among this Fig. 1; That is to say that it is elasticity power-assisted assembly with torsion spring 6(that the export-oriented pawl 402 of shift fork is positioned at bounding means 4) the circumferential working space that forms, and the circumferential width of export-oriented pawl 402 is less than the circumferential inner width of this circumferential working space.

In Fig. 1, out star wheel 1(driving component) is positioned at initial position; The export-oriented pawl 402 of shift fork is positioned at the neutral position of the curved pawl 601 of torsion spring and 602, and the export-oriented pawl 402 of shift fork is centerings with bounding means 7 in other words, and the residing position of shift fork this moment is intermediate point.

Fig. 2 is the A--A cross-sectional schematic of Fig. 1.

Among Fig. 2,1 is out star wheel, and 8 is upper cover plate, and 9 is lower cover plate, and the method for out star wheel 1, upper cover plate 8 and the riveted joint of lower cover plate 9 usefulness or spiral marking connection is fixed together, has consisted of driving component; 4 is shift fork, and 401 is the interior to pawl of shift fork, and 402 is the export-oriented pawl of shift fork; The export-oriented pawl 402 of shift fork passes the via hole of upper cover plate 8; 5 is interior ring; 6 is elasticity power-assisted assembly (being torsion spring herein), and 601 and 602 is two curved pawls of torsion spring 6; 7 is bounding means; 701 is the installation basic part of bounding means 7, it is a relatively static part relevant with work of the present utility model that basic part 701 is installed, bounding means 7 is packed in to be installed on the basic part 701, in driving stroke, driving component of the present utility model and passive component are all with respect to basic part 701 motions are installed.

Among Fig. 2,10 is friction element, and friction element 10 is used for producing frictional force between driving component and shift fork 4 between upper cover plate 8 and shift fork 4; This frictional force is caused by axial pressure.In backhaul, the friction torque that this frictional force produces is the source of effective torque.The moment of torsion (Operating torque that is called elasticity power-assisted assembly) that this friction torque produces when working less than torsion spring 6.Friction element 10 can be wave washer or block rubber or other elastic type part, also this friction element can be made the part of the part that is shift fork or driving component, such as convex closure class formation etc.

Fig. 3 be E-E of Fig. 1 to partial schematic sectional view, reflected the position relationship between rolling element, small pressure spring, out star wheel, the shift fork.

Among Fig. 3,2 is small pressure spring, and 4 is shift fork, and 101 is the interior dog of out star wheel, and 1011 is the fan platform of interior dog, fan platform 1011 form a space, with prevent small pressure spring 2 when the work by excess compression; Small pressure spring 2 is between the interior dog 101 of the rolling element 301 of organizing clockwise and the rolling element 302 of organizing counterclockwise and out star wheel.When static, gapped between the fan platform 1011 of the interior dog of the rolling element 301 of group and the rolling element 302 of organizing counterclockwise and out star wheel clockwise.

Fig. 4 is that the F of Fig. 2 is to partial schematic diagram.

Among Fig. 4,8 is upper cover plate, and via hole 81 is arranged on the upper cover plate 8; 402 is the export-oriented pawl of shift fork; The export-oriented pawl 402 of shift fork is positioned at via hole 81 and the gap of circumferencial direction is arranged, that is upper cover plate 8 does not interfere with the export-oriented pawl 402 of shift fork.

Fig. 5 of the present embodiment, Fig. 6, Fig. 7, Fig. 8 have described the driving component of the present embodiment one by a complete work cycle that is driven into clockwise counterclockwise backhaul.

In this Fig. 5 and follow-up description, the hollow arrow of circumferencial direction represents the moving direction of driving component.

In the process that the present embodiment one is moved to state shown in Figure 5 by state shown in Figure 1, under the effect of external force, out star wheel 1 clockwise rotates an angle; When out star wheel 1 clockwise rotates, the rolling element 302 of group is in separated state (being non-engagement state) counterclockwise, because the pressure of small pressure spring 2, make three clockwise the rolling elements 301 of group all be positioned at the small end of wedge shape space, out star wheel 1, the rolling element 301, interior ring 5 threes that organize clockwise are in engagement, thereby ring 5 clockwise rotates in driving.When out star wheel 1 clockwise rotates, because friction element has circular gap (referring to Fig. 1) having produced between driving component and the shift fork between the export-oriented pawl 402 of frictional force (referring to the description of Fig. 2) and shift fork and the curved pawl 601 of torsion spring, make the export-oriented pawl 402 of shift fork and interior to pawl 401 along with out star wheel 1 rotates together, until shift fork extroversion pawl 402 contacts with the curved pawl 601 of torsion spring.At this moment since the friction torque that friction element produces less than the Operating torque of torsion spring 6, that is the Operating torque of torsion spring 6 has applied a resistance opposite with driving direction to shift fork, this resistance causes shift fork than angle of out star wheel 1 hysteresis to the export-oriented pawl 402 of shift fork and interior to motion blockage effect of pawl 401 generations.Out star wheel 1 continues to clockwise rotate, and rolling element 302 rotations that drive small pressure spring 2 and organize counterclockwise, when contacting to pawl 401 in counterclockwise group rolling element 302 and the shift fork, under the drag effect of the curved pawl 601 of torsion spring, counterclockwise the rolling element 302 of group also can be in company with producing hysteresis effects (continue lag behind than out star wheel 1 angle) to pawl 401 in the shift fork, and the part small pressure spring 2 that contacts with the rolling element 302 of organizing counterclockwise of compression.Until the gap of the fan platform of the interior dog of out star wheel 1 and rolling element 302 disappears, out star wheel 1 drives the counterclockwise rolling element 302 of group by the fan platform of dog in it, the resistance, the interior of shift fork that overcome the curved pawl 601 of torsion spring clockwise rotate to pawl 401 and export-oriented pawl 402; Until drive the terminal point of stroke, as shown in Figure 5.In this process, shift fork interior than out star wheel 1 angle that lags behind, that is to say that the rotation angle of shift fork is less than the rotation angle of out star wheel 1 to pawl 401 and export-oriented pawl 402; And the twisting force of the curved pawl 601 of torsion spring is in the export-oriented pawl 402 of shift fork and interior to pawl 401, make counterclockwise group rolling element 302 be positioned at wedge shape space large extreme direction, and keep separated state with ring 5 and out star wheel 1.The curved pawl 602 of torsion spring and bounding means 7 keep motionless.

The present embodiment one by state shown in Figure 5 in the process of state shown in Figure 6 motion, the curved pawl of interior ring 5, bounding means 7 and torsion spring 602 is motionless; Out star wheel 1 is turning anticlockwise under external force, the export-oriented pawl 402 of curved pawl 601 shift forks of torsion spring and interior to pawl 401 also turning anticlockwise, the torsion direction of the curved pawl 601 of the torsion spring that shift fork is subject to is identical with the backhaul direction, obviously, the torsion of the curved pawl 601 of the torsion spring that shift fork is subject to that be subject to greater than shift fork with the resistance backhaul opposite direction, make shift fork revolution; This moment, the rolling element 301 of group was in separation (removing engagement) state clockwise, and counterclockwise the rolling element 302 of group is positioned at the large extreme direction of wedge shape space under the effect of pawl 401, also is in separated state in shift fork, small pressure spring 2, rolling element 301 and 302 all in company with in out star wheel 1 and the shift fork to pawl 401 turning anticlockwises, until as shown in Figure 6, a side contacts of the curved pawl of torsion spring 601 and bounding means 7,601 limited of curved pawls of torsion spring 7 are spacing, and the curved pawl 601 of torsion spring stops rotation motion.At this moment, a side of the export-oriented pawl 402 of shift fork contacts with the curved pawl 601 of torsion spring, and opposite side and the curved pawl 602 of torsion spring of the export-oriented pawl 402 of shift fork have circular gap, that is to say, shift fork does not also arrive intermediate point; And out star wheel 1(driving component) do not get back to initial position yet.

In the process that the present embodiment one is moved to state shown in Figure 7 by state shown in Figure 6, interior ring 5, bounding means 7, the curved pawl 601 of torsion spring and 602 keep motionless; Out star wheel 1 continues revolution, and rolling element 301 and 302 still is in separated state.As previously mentioned, because friction element has produced frictional force between driving component and shift fork, namely driving component has applied frictional force by friction element to shift fork, and the direction of the moment that this frictional force causes is consistent with the moving direction of driving component; Simultaneously be subject to the elastic resistance that surface friction drag and small pressure spring 2 from interior ring 5 apply by rolling element 302 to pawl 401 in the shift fork, these resistances can cause resisting moment, and the direction of resisting moment is opposite with the moving direction of driving component.As long as the resisting moment sum opposite with gyratory directions that the friction torque identical with gyratory directions that driving component applies shift fork by friction element is subject to greater than shift fork, then just continue along with out star wheel 1 revolution to pawl 401 in the export-oriented pawl 402 of shift fork and the shift fork, until as shown in Figure 7, shift fork gets back to intermediate point.That is to say, in the process before shift fork is got back to intermediate point, the moment identical with the backhaul direction that shift fork is subject to that be subject to greater than shift fork with the moment backhaul opposite direction, make shift fork get back to intermediate point.When shift fork is positioned at intermediate point.The export-oriented pawl 402 of shift fork and bounding means 7 centerings, the export-oriented pawl 402 of shift fork is in its residing bounding means 7 and the curved pawl 601 of torsion spring, the 602 circumferential working spaces that form in other words, and two side clearances are even.As seen from Figure 7, when shift fork was back to intermediate point, out star wheel 1 was not back to initial position yet fully.

In Fig. 8, interior ring 5, bounding means 7, the curved pawl 601 of torsion spring and 602 keep motionless, owing to out star wheel 1 rotates counterclockwise, therefore the rolling element 301 of group is in separated state clockwise.When shift fork was positioned at intermediate point, driving component was consistent with the moving direction of driving component by the direction of the friction torque that friction element applies shift fork, and this moment is effective torque; Simultaneously shift fork is subject to the elastic resistance that surface friction drag and small pressure spring 2 from interior ring 5 apply by rolling element 302, and these resistances can cause resisting moment, the direction of resisting moment and backhaul opposite direction.As long as effective torque is greater than that this moment, shift fork was subject to and the resisting moment sum backhaul opposite direction, then in the shift fork to pawl 401 and export-oriented pawl 402 along with out star wheel 1 along counterclockwise revolution; The interior of shift fork forces counterclockwise group rolling element 302 to keep released state to pawl 401, out star wheel 1, continue turning anticlockwise to pawl 401 and export-oriented pawl 402 in the shift fork, until as shown in Figure 8, one side of the export-oriented pawl 402 of shift fork contacts with the curved pawl 602 of torsion spring, because friction element is in the friction torque that produces between driving component and the shift fork (after shift fork is crossed intermediate point in backhaul, this moment also is effective torque) less than the Operating torque (referring to the description to Fig. 2) of torsion spring 6, shift fork is stopped operating, to pawl 401 and export-oriented pawl 402 along counterclockwise backhaul direction depart from an intermediate point angle in the shift fork this moment, and out star wheel 1 is got back to initial position fully simultaneously.

By foregoing description, the present embodiment one has been finished driving component by a complete work cycle that is driven into clockwise in returning counterclockwise.In like manner, can know that driving component has the same working principle therewith by the working procedure that is driven into counterclockwise in returning clockwise.Repeat no more herein.

In Fig. 9,11 are extension spring, and 12 is bounding means (being position-limitting pin herein), and 13 is connecting plate, and 14 is the export-oriented pawl of shift fork, and remaining parts is same as in figure 1.Extension spring 11 and connecting plate 13 have consisted of elasticity power-assisted assembly, one client link of extension spring 11 connecting plate 13, the other end of extension spring 11 and position-limitting pin 12 be fixed on and be on the relatively static part relevant with work of the present utility model (with the installation basic part 701 of Fig. 2 in like manner, carefully do not state herein); 13 position-limiting actions of 12 pairs of connecting plates of position-limitting pin; Among Fig. 9 as seen, elasticity power-assisted assembly (two extension springs 11 and two connecting plates 13) forms a circumferential working space that is not less than 180 ° with bounding means (four position-limitting pins 12), and the export-oriented pawl 14 of shift fork is positioned at this circumferential working space and circular gap is arranged; That is to say that the export-oriented pawl 14 of shift fork is positioned at the circumferential working space of bounding means and the formation of elasticity power-assisted assembly, and the circumferential width of the export-oriented pawl 14 of shift fork is less than the circumferential inner width of this circumferential working space.

Figure 10 is the improved schematic diagram to Fig. 2 of embodiment one.

In Figure 10,1 is out star wheel, and 4 is shift fork, and 15 is friction element, and the frictional force of this friction element 15 is caused by radial pressure.15 can be the rubber-like part, also can be spring-like or shell fragment class part.9 is lower cover plate, is provided with lower hard packing 16 between lower cover plate 9 and interior ring 5.All the other are the same with Fig. 2.

In Figure 11,1 is out star wheel, and 8 is upper cover plate, the 801st, and the convex closure of upper cover plate 8; The 4th, shift fork.Convex closure 801 is friction elements, and convex closure 801 can be the part of upper cover plate 8, also can be the elastic component that is embedded on the upper cover plate 8.Between upper cover plate 8 and interior ring 5, be provided with hard packing 17.All the other are the same with Fig. 2.

Combine it, the present embodiment one provides the structure that makes its drive end can get back to the swing type double rolling key clutch of initial position fully in backhaul, be characterized in: in driving stroke, driving component puts on the friction torque of shift fork less than the Operating torque of elasticity power-assisted assembly by friction element, make shift fork than angle of driving component hysteresis, that is the resistance opposite with driving direction that shift fork is subject to make shift fork than angle of driving component hysteresis; In backhaul, before shift fork is got back to intermediate point, the moment identical with the backhaul direction that shift fork is subject to that be subject to greater than shift fork with the moment backhaul opposite direction, make shift fork produce rotation motion; When shift fork returned back to intermediate point, the effective torque consistent with the backhaul direction that shift fork is subject to greater than that this moment, shift fork was subject to and the resisting moment sum backhaul opposite direction, thereby guaranteed to continue when shift fork is back to intermediate point to move along the backhaul direction.Obviously, after shift fork is crossed intermediate point, can make shift fork continue to turn round along the backhaul direction because of inertia, the effective torque consistent with the backhaul direction that also can continue shift fork is subject to that be subject to greater than shift fork with the resisting moment sum backhaul opposite direction, thereby shift fork can be rotated further along the backhaul direction.

The source of the effective torque of the present embodiment one is the frictional force that driving component puts on shift fork directly or indirectly, and this frictional force can be caused by axial pressure, also can be caused by radial pressure; This frictional force comes from the friction element that arranges between driving component and described shift fork, this friction element can be the part of the structure of driving component or shift fork; Perhaps this frictional force comes from driving component and shift fork axially or/and the relation of interference fit radially.In embodiment one, this friction torque is less than the Operating torque of torsion spring 6; Also can this friction torque be set to the maximum working torque less than torsion spring 6, its mechanism of action is the same.Because effective torque is caused by frictional force, so effective torque does not exist only in when shift fork is repositioned to intermediate point in the backhaul, also shift fork is crossed intermediate point until the stroke end of shift fork exists always in backhaul.In fact embodiment one the frictional force that puts on directly or indirectly shift fork by driving component all exists at whole driving stroke and backhaul, but the utility model be defined as in backhaul effective torque when shift fork is positioned at intermediate point and cross intermediate point after, the moment consistent with the backhaul direction that is subject to of shift fork.

In addition, the present embodiment one also comprises bounding means and elasticity power-assisted assembly, shift fork also comprises export-oriented pawl, when shift fork is still in intermediate point, the export-oriented pawl of shift fork is positioned at the circumferential working space that bounding means and elasticity power-assisted assembly form, and (this circumferential space can be less than 180 °, also can be to be not less than 180 °), and circular gap is arranged, this circular gap generally is not less than 0.5mm; Clearly, in embodiment one backhaul, when shift fork returns back to intermediate point, the space that shift fork continued fine rotation during this circular gap provided and made back.

And, the utility model by embodiment one provide make swing type double rolling key clutch drive end can get back to fully when the backhaul initial position method, its control step is: in backhaul, shift fork and driving component are all turned round, and before driving component is got back to initial position, make shift fork get back to intermediate point; Then be positioned at intermediate point and driving component when also not arriving initial position at shift fork, make shift fork cross intermediate point and continue along the backhaul direction to rotate, driving component continues revolution simultaneously; Last shift fork departs from angle of intermediate point along described backhaul direction, and driving component is turned back to initial position.

In order to realize making shift fork get back to intermediate point in the backhaul before driving component is got back to initial position, in the driving stroke of the present embodiment one, shift fork is subject to the resistance opposite with driving direction makes shift fork than angle of driving component hysteresis.

In order to realize being positioned at intermediate point and driving component when also not arriving initial position, making shift fork cross intermediate point to continue to rotate along the backhaul direction at shift fork, the present embodiment one is subject to shift fork at least when being positioned at intermediate point the effective torque consistent with the backhaul direction that be subject to greater than shift fork with the resisting moment sum backhaul opposite direction, make shift fork cross intermediate point and continue to rotate along the backhaul direction.

(embodiment two).

In Figure 12, part 20 is out star wheel, and part 25 is interior ring, comprises paired wedge shape space in the cavity that out star wheel 20 and interior ring 25 form.Part 211 is the rolling element of organizing clockwise, and part 212 is the rolling element of organizing counterclockwise.2211 and 2212 is the interior to pawl of shift fork, wherein in the shift fork to pawl 2211 be positioned at wedge shape space small end, be called small end to pawl, in the shift fork to pawl 2212 be positioned at wedge shape space large end, be called large end to pawl; In pawl 2211 and large the end, consist of groove shape structure to pawl 2212 in the small end of shift fork, that is to say that rolling element 211 and 212 is positioned at small end to pawl 2211 and the large groove that forms to pawl 2212 of holding.Be positioned at the state of rest that initial position, shift fork are positioned at the intermediate point position at driving component shown in Figure 12, in the small end to pawl 2211 and large end is interior can be different to pawl 2212 and the circular gap of rolling element.222 is the export-oriented pawl of shift fork, the interior part that all belongs to shift fork to pawl 2211 and 2212 of the export-oriented pawl 222 of shift fork and shift fork.Part 23 is elasticity power-assisted assembly, is torsion spring herein, and 231 and 232 is the curved pawl of torsion spring 23, and part 24 is bounding means.

In Figure 12, out star wheel 20 belongs to driving component, and interior ring 25 belongs to passive component, and clearly out star wheel 20 is positioned at the outer ring part of total, and interior ring 25 is positioned at the inner round portion of total.Three clockwise the rolling elements 211 of group and three counterclockwise group rolling element 212, and the interior of shift fork all be positioned at the cavity that out star wheel 20 and ring 25 form to pawl 2211 and 2212.The export-oriented pawl 222 of torsion spring 23, bounding means 24 and shift fork is positioned at outside the cavity of out star wheel 20 and ring 25 formation.Two curved pawls 231 of torsion spring and 232 are installed on the both sides of bounding means 24, and the three forms one less than 180 ° circumferential working space, and the export-oriented pawl 222 of shift fork is positioned at this circumferential working space and circular gap is arranged.

Figure 13 is the B--B cross-sectional schematic of Figure 12.

In Figure 13, upper cover plate 27 is fixed together with out star wheel 20, consists of driving component.The bottom outlet Spielpassung of interior ring 25 and out star wheel 20; Part 212 is the rolling element of organizing counterclockwise; Part 22 is shift fork, 2211 be in the small end of shift fork to pawl, 222 is the export-oriented pawl of shift fork; Part 23 is elasticity power-assisted assembly, is torsion spring herein, and 231 and 232 is the curved pawl of torsion spring 23; Part 24 is bounding means; Part 26 is elastic plectrum, between out star wheel 20 and shift fork 22.

In Figure 14, part 20 is that out star wheel, 201 is the internal tooth of out star wheel 20, and part 25 is interior ring, and 22 is shift fork, and part 26 is elastic plectrum.Internal tooth 201 and elastic plectrum 26 are called the peripheral force element.Elastic plectrum 26 1 ends are installed on the shift fork 22, and the other end is positioned at the between cog of the internal tooth 201 of out star wheel.When out star wheel 20 rotates, act on elastic plectrum 26 by internal tooth 201, make elastic plectrum 26 produce distortion, thereby shift fork 22 is produced peripheral force, the effective torque when this peripheral force provides backhaul to shift fork.

In Figure 15, two parts that circumferentially distribute 235 consist of elasticity power-assisted assembly, and part 235 is compression class elastic parts, can be Compress Spring or rubber-like part; Part 237 is bounding means, and part 238 is the export-oriented pawl of shift fork; Part 236 is little springs, and little spring 236 is between the export-oriented pawl 238 and elasticity power-assisted assembly 235 of shift fork.The export-oriented pawl 238 of shift fork is positioned at the circumferential working space of bounding means 237 and 235 formation of elasticity power-assisted assembly, because part 236 is little springs, so the export-oriented pawl 238 of shift fork has a circular gap with respect to this circumferential space, this circular gap generally is not less than 1 °.

The technological scheme that the present embodiment two is described is similar to embodiment one technological scheme, its main difference is: embodiment two effective torque is the moment that is caused by the peripheral force between driving component and the shift fork, and this peripheral force comes from the peripheral force element between driving component and shift fork; And embodiment two shift fork comprises in the small end in pawl and the large end to pawl, and to pawl and large end inward claw grooving shape structure, rolling element is positioned at groove in the small end.

Embodiment two working principle and embodiment one are similar, and any mechanical appointees understand at an easy rate, do not do herein and give unnecessary details.

(embodiment three).

In Figure 16,31 is outer shroud, and 32 star-wheels have chimb 321 and outer shroud 31 Spielpassung on the star-wheel 32.331 is the rolling element of organizing clockwise, and 332 is the rolling element of organizing counterclockwise; 341 is the interior to pawl of shift fork, and 342 is the export-oriented pawl of shift fork, the interior part that all belongs to shift fork to pawl 341 and export-oriented pawl 342 of shift fork; 35 is small pressure spring; 36 is elasticity power-assisted assembly, is torsion spring herein, and 361 and 362 is two curved pawls of torsion spring 36; 37 is bounding means, and bounding means 37 is a plate herein, and 37 play the effect that the curved pawl 361 of torsion spring and 362 are installed.

In Figure 16, star-wheel 32 belongs to driving component, and outer shroud 31 belongs to passive component, and clearly driving component is positioned at inner round portion, and passive component is positioned at the outer ring part.Comprise paired wedge shape space in the cavity that star-wheel 32 and outer shroud 31 form.Six small pressure springs 35, three clockwise the rolling elements 331 of group and three counterclockwise group rolling element 332, and the interior of shift fork all be positioned at the cavity that star-wheel 32 and outer shroud 31 form to pawl 341.The export-oriented pawl 342 of torsion spring 36, bounding means 37 and shift fork is positioned at outside the cavity of star-wheel 32 and outer shroud 31 formation.Two curved pawls 361 of torsion spring 36 and 362 are installed on the both sides of bounding means 37, the curved pawl 361 of torsion spring and 362 and bounding means 37 form one less than 180 ° circumferential working space, the export-oriented pawl 342 of shift fork is positioned at this circumferential working space and does not have circular gap; That is to say that the export-oriented pawl 342 of shift fork is positioned at the circumferential working space of bounding means 37 and 36 formation of elasticity power-assisted assembly, and do not have circular gap, namely the circumferential width of the export-oriented pawl 342 of shift fork equals the circumferential inner width of this circumferential working space.

Figure 17 is the D--D cross-sectional schematic of Figure 16.

Among Figure 17,31 is outer shroud, 32 star-wheels, and 381 is lower cover plate, 382 is upper cover plate.Upper cover plate 382 is fixed together, has consisted of driving component with the method for the riveted joint of star-wheel 32 usefulness or spiral marking connection; Lower cover plate 381 is fixed together, has consisted of passive component with the method for the riveted joint of outer shroud 31 usefulness or spiral marking connection; Porose and load connection on the lower cover plate 381.34 is shift fork, and 341 is the interior to pawl of shift fork, and 342 is the export-oriented pawl of shift fork; 36 is elasticity power-assisted assembly, is torsion spring herein, and 361 and 362 is the curved pawl of torsion spring; 37 is bounding means.The curved pawl 361 of torsion spring and 362 is installed on the bounding means 37.

Among Figure 17,39 is friction element, friction element 39 is between star-wheel 32 and shift fork 34, be used between driving component and shift fork, producing frictional force, the friction torque that this frictional force causes is the source of effective torque, minimum Operating torque after the value of this friction torque is installed on the bounding means 37 greater than torsion spring 36, and produce during less than torsion spring 36 work maximum working torque.Friction element 39 can be wave washer or block rubber or other elastic type part, also this friction element can be made the part of the part that is shift fork or driving component.

The technological scheme that the present embodiment three is described and the main difference of embodiment one technological scheme are that the circumferential width of the shift fork extroversion pawl of the present embodiment three and bounding means is identical, so in backhaul, the value of the effective torque that friction element 39 causes (friction torque) is greater than the minimum Operating torque of torsion spring 36 and less than the maximum working torque of torsion spring 36.Embodiment three working procedure and embodiment one are similar, now are summarized as follows.

Drive clockwise stroke: when the external force clockwise direction drives driving component, star-wheel 32 clockwise rotates, the rolling element 332 of group is in released state counterclockwise, the rolling element 331 of group enters engagement clockwise, thereby lower cover plate 381 rotations that drive outer shroud 31 and be fixed together with outer shroud, thereby drive load; Because the friction torque that friction element 39 provides is greater than the minimum Operating torque of torsion spring 36, so that the export-oriented pawl 342 of shift fork is pushed the curved pawl 362 of torsion spring open; At this moment the export-oriented pawl 342 of shift fork and interior curved pawl 362 to pawl 341, torsion spring, rolling element are all along with star-wheel 32 rotates.Because the friction torque that friction element 39 provides is less than the maximum working torque of torsion spring 36, so that before moving to the terminal point that drives stroke, under the drag effect that the curved pawl 362 of torsion spring produces, make shift fork export-oriented pawl 342 and interior to pawl 341 with respect to star-wheel 32 angle that lags behind, cause promoting the counterclockwise rolling element 332 of group to pawl 341 in the shift fork, and then the small pressure spring 35 that contacts with rolling element 332 of compression, make counterclockwise group rolling element 332 be positioned at the large end of wedge shape space.Afterwards under the promotion of the chimb 321 of star-wheel, the export-oriented pawl 342 of shift fork and interior to pawl 341 and the curved pawl 362 of torsion spring all along with star-wheel 32 rotates together, finish until drive clockwise stroke, in this process, shift fork is with respect to star-wheel 32 angle that lags behind.

Counterclockwise backhaul: after entering counterclockwise backhaul, it is motionless that passive component (outer shroud 31 and lower cover plate 381) keeps under the effect of load, and the rolling element 331 of group is in released state clockwise; This moment is because the rolling element 332 of organizing counterclockwise is positioned at the large end of wedge shape space under the thrust of pawl 341 in shift fork, star-wheel 32, outer shroud 31, rolling element 332 threes of group also are in released state counterclockwise, so that driving component can carry out returning movement under staff or other power effect, rolling element, shift fork is all along with the driving component revolution, because shift fork is than angle of driving component hysteresis in driving stroke, so shift fork 34 keeps than the super previous angle of driving component in backhaul, makes shift fork 34 get back to first intermediate point before driving component is got back to initial position thereby cause; At this moment, be positioned at intermediate point and driving component when also not arriving initial position at shift fork 34, because the friction torque (effective torque) that friction element 39 causes is greater than the minimum Operating torque of torsion spring 36, so that pushing the curved pawl 361 of torsion spring open, the export-oriented pawl 342 of shift fork continues to rotate an angle along counterclockwise backhaul direction, make star-wheel 32, outer shroud 31, rolling element 332 threes of group keep released state counterclockwise, until star-wheel 32 continues under external force revolution and gets back to initial position fully, backhaul finishes, and at this moment shift fork departs from angle of intermediate point along the backhaul direction.

Owing to comprising paired wedge shape space and paired rolling element in the cavity that driving component and passive component form, and rolling element comprises clockwise group rolling element and the rolling element of organizing counterclockwise, can in like manner analyze obviously, driving counterclockwise stroke and clockwise backhaul thereof, also can realize driving and in backhaul, making drive end get back to initial position fully.

Combine it, technological scheme when the present embodiment three provides the export-oriented pawl 342 of shift fork identical with bounding means 37 width, the present embodiment three also comprises bounding means and elasticity power-assisted assembly, shift fork also comprises export-oriented pawl, when shift fork is still in intermediate point, the export-oriented pawl of shift fork is positioned at the circumferential working space of bounding means and the formation of elasticity power-assisted assembly, and without circular gap; In backhaul, when shift fork is positioned at intermediate point, shift fork be subject to the effective torque consistent with the backhaul direction, greater than the minimum Operating torque of elasticity power-assisted assembly, continue to rotate along the backhaul direction thereby make shift fork cross intermediate point.

Although the organization plan of the present embodiment three and embodiment's one is incomplete same, but a common ground is arranged, namely in backhaul, when shift fork is positioned at intermediate point, the effective torque consistent with the backhaul direction that shift fork is subject to that be subject to greater than shift fork with the resisting moment sum backhaul opposite direction, make the backhaul terminal point of shift fork cross the intermediate point of shift fork.

The present embodiment three adopts, and to make driving component get back to the control step of initial position fully identical with embodiment one.

Aforementionedly pass through three embodiments and described organization plan of the present utility model, multiple different organization plan can also be arranged, as use magnet to replace elasticity power-assisted assembly, or make shift fork and driving component produce effective torque with magnetic material, perhaps the export-oriented pawl with shift fork makes elastic part, can also make many improvement to bounding means and elasticity power-assisted assembly, etc.Do not do carefully to state one by one herein.

Claims

1. swing type double rolling key clutch, it comprises driving component, passive component, shift fork, rolling element, described shift fork comprises interior to pawl, describedly interiorly be positioned at the cavity that described driving component and described passive component form to pawl and described rolling element, it is characterized in that: in backhaul, at least when described shift fork is positioned at intermediate point, the effective torque consistent with the backhaul direction that be subject to of described shift fork is that be subject to greater than described shift fork and the resisting moment sum backhaul opposite direction, makes the backhaul terminal point of described shift fork cross the intermediate point of described shift fork.

2. swing type double rolling key clutch according to claim 1 is characterized in that: described effective torque is directly or indirectly to put on the friction torque that the frictional force of described shift fork causes by described driving component.

3. swing type double rolling key clutch according to claim 1, it is characterized in that: described effective torque is the moment that is caused by the peripheral force between described driving component and the described shift fork, and described peripheral force comes from the peripheral force element between described driving component and described shift fork.

4. swing type double rolling key clutch according to claim 1, it is characterized in that: it also comprises bounding means and elasticity power-assisted assembly, described shift fork also comprises export-oriented pawl, when described shift fork is still in intermediate point, described export-oriented pawl is positioned at the circumferential working space of described bounding means and the formation of described elasticity power-assisted assembly, and circular gap is arranged.

5. swing type double rolling key clutch according to claim 1, it is characterized in that: it also comprises bounding means and elasticity power-assisted assembly, described shift fork also comprises export-oriented pawl, when described shift fork is still in intermediate point, described export-oriented pawl is positioned at the circumferential working space of described bounding means and the formation of described elasticity power-assisted assembly, and without circular gap; In backhaul, when described shift fork is positioned at intermediate point, described shift fork be subject to the effective torque consistent with the backhaul direction, greater than the minimum Operating torque of described elasticity power-assisted assembly.

6. swing type double rolling key clutch according to claim 1 is characterized in that: in driving stroke, described shift fork is subject to the resistance opposite with driving direction, makes described shift fork than the described driving component angle that lags behind.