CN2753925Y - Uninterrupted power gear speed variator for automobile - Google Patents

Abstract

The uninterrupted power gear transmission is provided with a gear box body, at least two shafts are arranged on a bearing, the shafts are provided with gears to form a gear mechanism, the gear mechanism comprises at least two circular gear mechanisms and a non-circular gear mechanism as a transition gear, and the two circular gear mechanisms are correspondingly configured with one non-circular gear mechanism; the maximum transmission ratio of the non-circular gear mechanism is larger than that of the corresponding low gear, and the minimum transmission ratio is smaller than that of the high gear; each gear mechanism is provided with a gear which is connected with the shaft or the shaft and the shaft through an overrunning clutch, and the overrunning clutch is also provided with an operating mechanism; the control mechanism consists of a shifting claw, a control pin, a sliding ring and a shifting rod, and an elastic piece for returning the sliding ring is arranged in a transmission chain between the control pin and the shifting rod; and a linkage mechanism is arranged between the shift levers. The variable transmission ratio is utilized to continuously transition the initial gear to the target gear, and synchronous automatic engagement and disengagement conversion is carried out, so that the speed change efficiency is high, the energy consumption is low, and the gear shifting is stable.

Description

The automobile gear-shift transmission of uninterruptible power

Technical field: the present invention relates to the many grades of gear-shift transmissions that a kind of automobile is used, particularly just can gear shift in the time need not cutting off power change the gear-shift transmission of velocity ratio.

Background technique: existing automobile gear-shift transmission, mostly be the step type speed changer greatly, can be divided into by structure: three kinds of carrier wheel formula, constant mesh gear formula and planetary gear types.The axle that relative transferring power is all arranged, be driving shaft and driven shaft, the circular gear mechanism (refering in particular to forward gears) that has at least two grades of normal engagements between driving shaft and the driven shaft, for can conversion between two grades of circular gear mechanisms of different velocity ratios, must when conversion, gear-shift transmission and power section be cut off.Generally all be between gear-shift transmission and power mechanism, to be provided with controlled clutch (as friction disk clutch), when speed-change and gearshift with the clutch separation between gear-shift transmission and the power mechanism, removing transmission of power just can speed-change and gearshift, the gear-shift transmission of automatic transmission, intermeshing planetary gears, clutch operation by air pressure or hydraulic control system, turn to two grades of clutches of output to move simultaneously together by linking mechanism control, the clutch separation of another grade of clutch of shelves forms gear shift.Two clutches of gearshift procedure or gearshift procedure have and separate temporary transient the time or the jointing state of semi-linkage simultaneously.Fluid coupling and torque converter transmission efficiency in certain speed range of adding in this system are extremely low, the manufacture cost height.Speed changer had both been handled complexity like this, had reduced transmission efficiency again, wasted energy.Existing unidirectional delivery is fed back controlled driving mechanism and steel belt clutch, be to the Transmitted chains of gearbox one shaftgear the unidirectional delivery torque mechanism to be set at the clutch plate assembly, the unidirectional delivery torque mechanism comprises ratchet mechanism, one way engagement mechanism and steel belt clutch and other free wheel devicees etc., can be referred to as free wheel device or unidirectional delivery torque mechanism.This driving mechanism as long as reduce the transmission of power or reduce speed drive shaft, just can make the driving link of unidirectional delivery torque mechanism separate with driven member is unidirectional when shifted, disconnects power transmission, thereby just can carry out shifted.But this mechanism yet will disconnect the transmission of power for a long time at speed-change process.

Summary of the invention:

The present invention will solve the gear-shift transmission of automobile will be interrupted the problem of transmission of power at speed-change process, the conversion between a kind of gear is provided but must not be interrupted the automobile gear speed changer of power.

The automobile gear speed changer of uninterruptible power of the present invention, gear housing is arranged, gear housing is being provided with by bearing and is comprising input shaft, output shaft at least two interior axles, axle has normal meshed gears and constitutes gear mechanism, contain with at least two grades of circular gear mechanisms that turn to output at the Transmitted chains of input shaft to output shaft, it is characterized in that: also contain non-circular gear mechanism at input shaft to the Transmitted chains of output shaft, and be with adjacent two grades of circular gear mechanisms that turn to output and a same corresponding configuration of non-circular gear mechanism that turns to output as the transition shelves; The maximum transmission ratio of non-circular gear mechanism is greater than the velocity ratio of bottom gear in adjacent two shelves circular gear mechanisms of corresponding configuration with it, and the fastest ratio of non-circular gear mechanism is less than the velocity ratio of adjacent two shelves circular gear mechanism high speed shelves of corresponding configuration with it; In two adjacent two grades circular gear mechanisms and the non-circular gear mechanism of corresponding configuration as the transition shelves, each gear mechanism all respectively have a gear with the axle or the axle with spool between connect by roller-type overrunning clutch or Wedge type over running clutch, roller-type overrunning clutch or Wedge type over running clutch also have clutch operation; Clutch operation contains the pusher dog that acts on roller-type overrunning clutch or the Wedge type over running clutch joint element, control pusher dog and makes the driving lever that the control pin of circumferentially swing or control pusher dog are made the control pin of circumferentially swing, are in axial sliding the slip ring of socket, are slidingly connected with slip ring with star-wheel or the ring that has a concave circular arc with respect to the ring that has concave circular arc of Wedge type over running clutch with respect to the star-wheel of roller-type overrunning clutch, slip ring connects with control pin, has the elastic component that makes the slip ring return in Transmitted chains between the driving lever is sold in control; Have linking mechanism between the driving lever of clutch operation.Reach by operating mechanism and make free wheel device be in separated state, free wheel device just can not normally engage automatically, is referred to as to be in off working state.Can recover the working state that free wheel device is in automatic combination, separates automatically by operating mechanism on the contrary.For the present invention is described legibly, below all be a pair of gear with gear mechanism earlier or be equivalent to the gear mechanism that a pair of gear constitutes and describe.Like this maximum transmission ratio of non-circular gear mechanism greater than with the circular gear mechanism of its corresponding configuration in the velocity ratio of relative bottom gear, the fastest ratio of non-circular gear mechanism less than with the circular gear mechanism of its corresponding configuration in the velocity ratio of relative top gear, for gear mechanism all is a pair of gear, be exactly the Pitch radius of non-circular gear mechanism driving gear pitch curve minimum radius less than bottom gear driving gear in two grades of circular gear mechanisms of corresponding configuration with it, the maximum radius vector of non-circular gear mechanism driving gear pitch curve is greater than the Pitch radius of two grades of circular gear mechanism high speed shelves driving gears of corresponding configuration with it.When the stable transferring power of speed changer, wherein the free wheel device of one grade circular gear mechanism engages and keeps this grade transferring power, the free wheel device of other gear mechanisms to separate (surmounting) automatically or be in separated state under clutch operation control.To adjacent other grades gear graduation, just between the circular gear mechanism of two grades of normal engagements, carry out gear shift from this grade.As from this grade to adjacent top gear gear shift, just bottom gear is to adjacent top gear gear shift, starts clutch operation and the non-circular gear mechanism clutch operation corresponding with it that linking mechanism drives these adjacent two grades of circular gear mechanisms.In the time of near corresponding non-circular gear mechanism driving wheel is engaged to pitch curve minimum radius (following abbreviate the pitch curve radius vector as radius), the free wheel device of non-circular gear mechanism is realized surmounting and the control pin is left, and makes this free wheel device return to working state.The engagement radius of this non-circular gear mechanism driving wheel is increased to and is greater than bottom gear driving gear Pitch radius (hereinafter to be referred as radius), the free wheel device of non-circular gear mechanism just engages speedup (angular velocity) transferring power automatically, and the free wheel device of bottom gear is separated.In the corresponding non-circular gear mechanism speedup transferring power later stage, its driving gear is engaged near the maximum radius, and the free wheel device of top gear is realized surmounting and the control pin is left, and makes this free wheel device return to working state.The engagement radius of non-circular gear mechanism driving gear is reduced to and is equaled and be less than top gear driving gear radius, the free wheel device of top gear just engages transferring power automatically, and the free wheel device of non-circular gear mechanism is separated, the gear shift that realization can uninterruptible power.Pass through the locking mechanism elasticity self-return of the clutch operation of noncircular gear after gear shift, the control pin is returned to the position of restriction pusher dog swing, makes the free wheel device maintenance separated state of non-circular gear mechanism.To the bottom gear speed change, process is opposite from top gear.Behind the action linking mechanism, stir top gear circular gear mechanism slip ring earlier, make the control pin of top gear circular gear mechanism free wheel device will get back to the control position; After stir the slip ring of non-circular gear mechanism, make the control pin of non-circular gear mechanism free wheel device will leave the control position.Non-circular gear mechanism driving gear radius is engaged near the most of position in addition of maximum radius, non-circular gear mechanism driving gear engagement radius is less than top gear driving gear radius, its free wheel device will surmount and control sells the control position that speeds away, and makes the in running order state to be joined of free wheel device.Near position non-circular gear mechanism driving gear radius is engaged to maximum radius, because the driving gear maximum radius of non-circular gear mechanism will be greater than top gear driving gear radius, just can make the noncircular gear free wheel device be in jointing state automatically and begin transferring power, and the free wheel device of top gear driving gear is surmounted automatically, conversion very steady.After the free wheel device of top gear driving gear surmounted automatically, the effect of its operating mechanism elastic component made the control pin be in restriction pusher dog swing position, keeps the separated state of free wheel device.Equally, in the time of near the driving gear engagement radius of non-circular gear mechanism forwards near least radius, because the free wheel device of bottom gear is in the state to be joined that surmounts always, non-circular gear mechanism driving gear radius is engaged to and equals and be less than bottom gear driving gear radius, the free wheel device of bottom gear automatically engages and makes the free wheel device of non-circular gear mechanism not only but also surmounts automatically, forms gearshift procedure stably.Utilize the locking mechanism elastic recoil characteristic of the clutch operation of non-circular gear mechanism, surmount under the separated state control pin at the free wheel device of non-circular gear mechanism and get back to the position of restriction pusher dog swing, thereby keeping separated state.Like this, utilize non-circular gear mechanism to have the characteristic of non-isogonism speed transmission and the characteristic of free wheel device automatic clutch, the transmittance process that non-circular gear mechanism angular velocity increases comes transitional face to answer between two grades of circular gears from low to high speed change, the transmittance process that reduces with non-circular gear mechanism angular velocity comes between two grades of circular gears of transition speed change from high to low, the transmission that makes speed-change process keep power has also just realized the speed-change and gearshift of automobile gear speed changer uninterruptible power.When not needing free wheel device participation work, just can remove the working state of the joint element of free wheel device by clutch operation, just be forced to free wheel device and be in separated state.In gearshift procedure, when the free wheel device of corresponding target shelves gear and the noncircular gear that matches need participate in work, just can pass through the working state of the joint element of clutch operation real-time recovery free wheel device, and remove the working state of the joint element of free wheel device subsequently in real time.

Many grades of speed change circular gear speed changers more than two grades adjacent two grades of speed changing structures arbitrarily adopt structure of the present invention, and speed-change process is with above-mentioned similar.Still all be arranged on driving shaft with free wheel device earlier below and the present invention be described with corresponding gear.Free wheel device is arranged between driven gear and driven shaft or axle and the axle, and the speed-change process of formation and result are identical, and just the working procedure of free wheel device is between driven shaft and driven gear or axle and spool carry out.The relation of each gear mechanism tooth radius of narrating below all is the relation between the radius of driving wheel, and the radius relationship between the driven gear is just in time opposite with the radius relationship between the driving gear.

Clutch operation is the mechanism that the clutch of clutch is carried out artificial manipulation or control, make clutch according to people's needs be in from or the state that closes, so clutch operation also claims control structure.Clutch operation can be selected different operating mechanisms for use according to different free wheel devicees, for existing free wheel device, as ratchet free wheel device, turn key free wheel device, ball or roller or voussoir free wheel device, can select existing corresponding operating mechanism for use.Operating mechanism also claims control structure, as stir the bar of ratchet, stage clip, the mechanism that the control turn key rotates, the pusher dog mechanism of control ball or roller or voussoir etc., can select for use the unidirectional delivery of the applicant's application in the past to feed back the operating mechanism of overrunning clutch (free wheel device) in the controlled driving mechanism and the operating mechanism of steel band overrunning clutch, also can design new on-off control mechanism.People's controlled clutch operating mechanism, can directly move clutch operation with hand, can also control by mechanical linkage which controls, also can pass through hydraulic power pack, the control of air pressure actuator linkage, can also use linking mechanisms such as electric control motor, electromagnet.Also can electronic, hydraulic parts, pneumatic be set, the corresponding clutch operation that forms with these actuators at operating mechanism.

In the solution of the present invention, be associated with mechanical linkage which controls or electromagnetism linking mechanism or hydraulic power pack or air pressure linking mechanism between the clutch operation.As the gear of the circular gear mechanism of former transferring power being called initial shelves, the gear of the circular gear mechanism that will change to is called the purpose shelves, and the noncircular gear that will match with two circular gear mechanisms of two grades is called the transition shelves.The control program of linking mechanism is like this: initial shelves free wheel device is in state to be separated → transition shelves free wheel device and is in state to be joined → purpose shelves free wheel device and is in state to be joined.Can between the operating mechanism of adjacent two grades of circular gear mechanisms and corresponding transition shelves non-circular gear mechanism, linking mechanism be set separately, also can be connected into whole linking mechanism to each linking mechanism.Equally in order to control the free wheel device of non-circular gear mechanism exactly, just can guarantee that by simple linking mechanism non-circular gear mechanism once finishes transition work.Between the slip ring of the clutch operation of non-circular gear mechanism and the star-wheel of roller-type overrunning clutch, or the slip ring of the clutch operation of non-circular gear mechanism and Wedge type over running clutch have between the ring of concave circular arc, the locking mechanism that also has the axial return of restriction slip ring, locking mechanism have with the pusher dog control end makes the release mechanism that circumferential position changes interlock.

Slip ring as noncircular gear free wheel device operating mechanism is provided with a lever, lever has return spring, between one end of lever and the control pin back segment ball is set, control pin back segment has and the ball corresponding groove, the other end of lever is corresponding with the deck of star-wheel or corresponding with the deck of the ring that has concave circular arc, has constituted locking mechanism and release mechanism.On the pusher dog outer rim of noncircular gear free wheel device operating mechanism a flume structure is arranged in addition for another example, star-wheel or the endless belt that has a concave circular arc have dome, star-wheel or the ring that has a concave circular arc are by dome and slip ring slip socket, dome has the feather key that pins slip ring, feather key is corresponding with flume structure to link, and flume structure has constituted the release mechanism that changes interlock with the circumferential pendulum angle of pusher dog.

So-called non-circular gear mechanism, be exactly the eccentricity gear and the gears such as elliptic gear, square gear of engagement relatively, in the transmission process of a circle, driving gear do that isogonism speed is rotated and the rotation of driven gear to be non-isogonism speed rotate, angular velocity diminish gradually not only become greatly gradually or become gradually diminish gradually greatly not only or several become greatly gradually but also gradually the process of diminishing be loop cycle.At the rotation process of a circle two or more processes that diminish gradually again greatly that become are gradually arranged, diminishing gradually through an angular velocity becomes greatly not only or becomes gradually the process that diminishes greatly but also gradually gradually and just can finish once the uninterruptedly smooth transition speed-change process of transferring power, and both gear shift once.The noncircular gear of indication mainly is continuous rotating noncircular gear among the present invention.Discontinuous rotating noncircular gear can only carry out a gear shift, also will ajust the position of discontinuous rotating noncircular gear when needing gear shift more again, just can carry out.

For free wheel device, the also title unidirectional delivery torque mechanism that has.For the speed changer that is unidirectional delivery power, free wheel device just can be realized purpose of the present invention as long as be mono-directional overrun clutch.If the speed changer of bi-directional power, free wheel device then is a double rolling key clutch.Double rolling key clutch can be the joint of the opposite mono-directional overrun clutch of both direction, also can single design double rolling key clutch.At this moment double rolling key clutch two-way all needs to have operating mechanism, by the control operating mechanism, guarantees that a direction is in the normal working that stable separation realizes the overdrive clutch of other direction.Be used for automotive transmission for the present invention,, utilize engine braking, also will often adopt double rolling key clutch in order to prevent automobile sideslip tuning when ice ways face is exercised.

The present invention preferably friction overdrive clutch of usefulness mainly is ball type free wheel device or roller-type overrunning clutch or voussoir free wheel device, and friction overdrive clutch is band pusher dog friction overdrive clutch, and the clutch operation of band pusher dog friction overdrive clutch is the control mechanism of pusher dog and control pusher dog swing position.The control mechanism of control pusher dog swing position is the operation mechanism that pusher dog is in or is not in restriction ball, roller or voussoir working state.So-called pusher dog is exactly the pusher dog of the roller-type overrunning clutch of existing band pusher dog, and perhaps the shift fork of voussoir double rolling key clutch (also have claim pusher dog) is similar as pusher dog and shift fork, can unitedly call pusher dog.The pawl of pusher dog is arranged in the wedge groove at roller place or in the annular groove of voussoir place, is positioned at the outside of roller or voussoir, and perhaps the pawl of pusher dog is positioned at the opening of roller or voussoir end face, perhaps is enclosed within the projection of roller or voussoir section.When free wheel device is roller-type overrunning clutch, the pawl of pusher dog is arranged on the wedge groove at roller place, the control end of pusher dog is pegged graft with the star-wheel control chamber that has the wedge groove, the corresponding control pin that can insert or transfer to that is provided with the space between the control chamber of control end, the control pin can connect with slip ring by spring.Also can control pin and directly connect with slip ring, elastic element is the elasticity driving lever, or driving lever has return spring.Work more accurately and effectively in order to guarantee the control pin, control pin front end has the projection corresponding with the pusher dog control end, just to guarantee guaranteeing that after the swing of the pusher dog control end control pin leaves or return.Equally, pusher dog and control pin front end projection corresponding position, just the control end position is preferably with the inclination angle; Star-wheel or the position that has a relative pusher dog of ring of concave circular arc have control chamber.For make noncircular gear when not participating in work not the axle with transferring power rotate, the present invention preferably the noncircular gear place axle and circular gear place spool between be provided with controlled clutch.Can be provided with controlled clutch between the shaft part with the shaft part at single non-circular gear mechanism place and circular gear place, preferably all non-circular gear mechanisms are concentrated on a pair of (two) axle, circular gear mechanism concentrates and is arranged on another to axle, another of a pair of (two) at non-circular gear mechanism place axle and circular gear mechanism place is corresponding drive connection connection to (two in addition) axle, and connects by controlled clutch.The shaft part at noncircular gear place or axle and the shaft part at circular gear place or axle can distribute by coaxial line, as the abutment shaft that connects by controlled clutch, can use the mutual socket that connects by controlled clutch spool; Distribution also can parallel to the axis, two shaft parts or the axle at two shaft parts at noncircular gear place or axle and circular gear place all are that the corresponding driving mechanism by identical drive connections such as gears connects, another root shaft part that the corresponding connection shaft part at shaft part at noncircular gear place or axle and circular gear place or shaft drive is concerned be equal to the noncircular gear place or spool connect shaft part with circular gear place corresponding or shaft drive concerns.This just another of a pair of (two) axle and circular gear mechanism place at non-circular gear mechanism place be corresponding drive connection connection to (two in addition) axle, just corresponding shaft can be a Synchronous Transmission, be the equal of coaxial, perhaps corresponding shaft is to turn to relative transmission joint with velocity ratio, and a pair of (two) the shaft drive relation at non-circular gear mechanism place is identical with another drive connection to (two in addition) axle at circular gear mechanism place.

Compared with the prior art the present invention has automobile in the uninterrupted transferring power of speed-change process, makes driven shaft earlier after the speed transition change that will become, again by the circular gear mechanism transferring power of purpose shelves; Mechanical wear and loss reduce greatly, have improved the efficient of speed changer, have reduced the energy loss of speed-change process, and make transferring power more steady.

Description of drawings: accompanying drawing has been represented the automobile gear speed changer structure schematic representation and the part-structure schematic representation of uninterruptible power of the present invention.Wherein, Fig. 1 is a kind of automobile gear speed changer transmission system sketch of three shelves uninterruptible powers, Fig. 2 is the change curve of this car transmissions gearshift procedure velocity ratio, Fig. 3 is a linking mechanism in the automobile gear speed changer of this three shelves uninterruptible powers, each clutch operation, driven shaft, the part-structure schematic representation of each driven gear and free wheel device, Fig. 4 is the ssembly drawing of each grade driven gear and free wheel device and part clutch control parts, Fig. 5 is the exploded view of each grade driven gear and free wheel device and part clutch control parts, Fig. 6 is the ssembly drawing that can turn round non-circular gear mechanism driven gear and free wheel device and part clutch control parts continuously, Fig. 7 is the exploded view that can turn round non-circular gear mechanism driven gear and free wheel device and part clutch control parts continuously, and the gear-shift transmission of this three shelves uninterruptible powers of Fig. 8-12 is at the schematic representation of gearshift procedure linking mechanism and each clutch operation change procedure; Figure 13,14, three kinds of state principle schematic of 15 band pusher dog double rolling key clutchs; Figure 16,17,18,19, the 20th, the gear-shift transmission of three shelves uninterruptible powers of another kind of linkage pull rod formula is at the schematic representation of gearshift procedure linking mechanism and each clutch operation change procedure; Figure 21 is the automobile gear speed changer principle schematic of four shelves speed change uninterruptible powers, and Figure 22 .1,22.2, the 22.3rd has the wedge block type double rolling key clutch of pusher dog and the sectional view of three kinds of states of part operating mechanism; Figure 23 is roller type double rolling key clutch and the operating mechanism main station portion sectional view that has pusher dog, Figure 24 has the roller type double rolling key clutch of pusher dog and operating mechanism B-B to sectional view, Figure 25 has the roller type double rolling key clutch of pusher dog and operating mechanism A to partial sectional view, Figure 23 .1 is used roller type double rolling key clutch and the operating mechanism partial cutaway plan view that has pusher dog of non-circular gear mechanism, and Figure 23 .2 is used roller type double rolling key clutch and the operating mechanism partial cutaway plan view that has pusher dog of this non-circular gear mechanism; Figure 26 is the schematic representation of controlled clutch separated state between noncircular gear axle and the round tooth wheel shaft in the gear-shift transmission of three shelves uninterruptible powers, and Figure 27 is the schematic representation by the controlled clutch jointing state between noncircular gear axle and the round tooth wheel shaft in the gear-shift transmission of three shelves uninterruptible powers.The example that engages accompanying drawing below further specifies the present invention.

Specific embodiment:

Embodiment one, a kind of automobile gear-shift transmission of uninterruptible power, gear housing is arranged, gear housing is being provided with two axles at least by bearing, and two axles have the circular gear that engagement is being set and the noncircular gear of engagement, and reverse gear shaft and reverse gear carrier gear also are being set.Have the normal circular gear mechanism of meshing of three shelves between I, two II in relative rotation, every adjacent two grades of circular gear mechanisms of these three shelves circular gear mechanisms also dispose a non-circular gear mechanism, and non-circular gear mechanism also is I, two II in relative rotation of being arranged on of normal engagement.Driving gear 4a ', 4b ' in circular gear mechanism, the non-circular gear mechanism, 4d ', 5a ', 5b ' are fixedly connected with one, and driven gear 4a, the 4b in circular gear mechanism, the non-circular gear mechanism, 4d, 5a, 5b connect by roller-type overrunning clutch with two II.Free wheel device also has the operating mechanism that pusher dog and control pin thereof etc. constitute.In the non-circular gear mechanism of adjacent two grades of circular gear mechanisms and configuration, less than the driving gear 4a ' of bottom gear in adjacent two grades of circular gear mechanisms, the radius of 4b ', its maximum radius is respectively greater than the driving gear 4b ' of adjacent two grades of circular gear mechanism high speed shelves, the radius of 4d ' respectively for the least radius of driving gear 5a ', 5b '.In the non-circular gear mechanism of adjacent two grades of circular gear mechanisms and corresponding configuration, the least radius of driven gear 5a, the 5b of non-circular gear mechanism is less than the radius of the top gear driven gear of the adjacent two grades of circular gear mechanisms of correspondence, and its maximum radius is greater than the radius of the bottom gear driven gear of the adjacent two grades of gear mechanisms of correspondence.The control pin of control pusher dog swing position is the critical piece that pusher dog is in or is not in the operating mechanism of restriction ball, roller or voussoir working state.The pusher dog control mechanism of noncircular gear free wheel device operating mechanism is in state to be separated when making free wheel device be in jointing state, and promptly constitutes the linking mechanism of stablizing separated state after entering separated state.Having linking mechanism between the pusher dog control mechanism of each roller-type overrunning clutch.Like this, have the linking mechanism according to control program control between the free wheel device operating mechanism of the non-circular gear mechanism transition wheel of the initial shelves of every adjacent two grades of circular gear mechanisms, purpose shelves and configuration, control program is that initial shelves free wheel device is in state to be separated → transition wheel free wheel device and is in state to be joined → purpose shelves free wheel device and is in state to be joined.Transition wheel be noncircular gear in the present invention as a kind of abbreviation of the gear of transition shelves,

The gearshift mechanism general structure of A, speed changer and operating mechanism

Fig. 1 is the transmission system sketch of speed changer.One is input shaft I, and two is output shaft II.Gear 4a-4a ' is the gear train of one grade of circular gear mechanism, and velocity ratio is i ₁Gear 4b-4b ' is the gear train of second gear circular gear mechanism, and velocity ratio is i ₂(be i ₁＞i ₂).Gear 4c-4c ' is the gear train of third gear circular gear mechanism, and velocity ratio is i ₃(be i ₁＞i ₂＞i ₃); Gear 5a-5a ', 5b-5b ' are respectively two groups of noncircular gears that are used for realizing the non-circular gear mechanism of gear shift.The velocity ratio of two groups of noncircular gears is respectively i ₄And i ₅I wherein ₄At i _4minAnd i _4maxBetween the consecutive periods variation, and i _4minBe slightly less than i ₂, and i _4maxBe slightly larger than i ₁i ₅At i _5minAnd i _5maxBetween the consecutive periods variation, and i _5minBe slightly less than i ₃, and i _5maxBe slightly larger than i ₂, as shown in figure 12.Gear 4a ', 4b ', 4c ', 5a ', 5b ' connect firmly together with input shaft, and gear 4a, 4b, 4c, 5a, 5b link by free wheel device and the output shaft II by change pulley and the control of each operating mechanism.

Gearshift mechanism can be made of linking mechanism, operating mechanism, roller-type overrunning clutch (being called for short clutch in this embodiment).As shown in Figure 3, the figure middle gear is reduced representation, the gearshift mechanism general structure mainly comprises gear shift control wheel 57 and catch means (not shown) thereof, shift shaft 58, shift fork and shift fork spring (in the shift fork rotating shaft, not shown), the circular gear clutch pack of each grade (seeing Fig. 4, Fig. 5), can continuous rotating noncircular gear clutch pack (seeing Fig. 6, Fig. 7), line shaft 56 (output shaft) etc.4a, 4b, 4c are respectively one, two in addition, the third gear circular gear, and 5a is one, the transition wheel of second gear correspondence, and 5b is two, the transition wheel of third gear correspondence.Transition wheel is can the another kind of address of continuous rotating noncircular gear.Among the figure each gear all with input shaft on fixing respective gears keep the normal engaged relation (see Fig. 1, among Fig. 3 input shaft and on gear all do not draw in the drawings).

Gear shift control wheel 57 is rotated by selector device (can be manual operating handle or automatic controller) control, and drives shift shaft 58 rotations.On the shift shaft 58 with on the out of phase of reverse shift fork relevant position protruding structure is being arranged, stirring shift fork in order to machine in due course.Shift fork (3a, 3b, 3c, 3d, 3e) drives slip ring (the similar fork shift ring of the stirring) action of corresponding operating mechanism when being struck, and recovers maybe will recover to engage automatically the working state of separating automatically again to control corresponding free wheel device.And be not subjected to the shift fork of protruding partial action on the shift shaft, and all under the effect of shift fork spring, be in and make slip ring to the position that gear is close to, make corresponding free wheel device be controlled in stable separated state.Gear shift control wheel 57, shift shaft 58 and protruding structure have constituted linking mechanism.

B, have the formation of the controllable overrunning clutch of operating mechanism

A) supporting controllable overrunning clutch group (hereinafter to be referred as the conventional wheel clutch pack) the conventional wheel clutch pack of each grade circular gear is made up of critical pieces such as line shaft (not drawing among the figure), circular gear 51, pusher dog control unit and roller 52, slip ring 53, limit shelves 54, Fig. 4 is an assembly structure, and Fig. 5 is each part disassembled form.

Line shaft 56 connects with the roller-type overrunning clutch main part of circular gear by band pusher dog control unit, forms the main body of controllable overrunning clutch.Line shaft is the circular section axle, and the overcoat of free wheel device is to be that the gear of star wheel structure constitutes by the inboard, is furnished with roller and alternate pawl between line shaft and the star wheel structure, and the outer end of pawl is the ring that fuses, and endless belt has the fork as control end.So just constitute the friction overdrive clutch with out star wheel structure, free wheel device has in check pusher dog.The pawl of pusher dog contacts with the line shaft cylindrical, can keep movement tendency in the same way by friction mode and line shaft 56.By to protruding the control of position control end on the pusher dog outer rim, whether in running order to reach solenoidoperated cluthes, can realize the transmission of power from the circular gear to the line shaft.

The slip ring sky is enclosed within on the periphery of the gear wheel hub that has star wheel structure, and circular gear is in axial sliding relatively only.Its sliding stroke is limited by the end face and the limit shelves of gear.The projection that above the slip ring gear one side is had the buckle of two symmetric arrangement constitutes the control pin, in order to the position of the relative star wheel structure of control pusher dog.Control pin (and can contain spring between the slip ring), slip ring and driving lever have constituted control mechanism, and pusher dog, control pin (can contain spring between control pin and the slip ring), slip ring, driving lever (can be the elasticity driving lever) have constituted operating mechanism.

B) the supporting controllable overrunning clutch group (hereinafter to be referred as the transition wheel clutch pack) of noncircular gear

The transition wheel clutch pack is made up of critical pieces such as line shaft 56 (this axle does not draw among Fig. 6,7), noncircular gear 71, roller pusher dog control unit 72, feather key 73, slip ring 74, limit shelves 75, and Fig. 6 is an assembling condition, and Fig. 7 is its each part disassembled form.

Be equally slip ring sleeve on the periphery of circular gear wheel hub, circular gear is done and is endwisely slipped relatively.Its sliding stroke is subjected to the restriction of end face, feather key and the limit shelves of gear; Relative gear one side has the buckle projection of two symmetric arrangement above the slip ring, constitutes the control pin, in order to the position of the relative star wheel structure of control pusher dog, is limited in order to the position to pusher dog.Line shaft connects by roller, pusher dog control unit with noncircular gear, forms the main body of controllable overrunning clutch.Line shaft is the circular section axle, the noncircular gear inboard is a star wheel structure, be furnished with roller and alternate pawl between line shaft and the star wheel structure, the outer end of pawl is the ring that is connected as a single entity and as the fork of control end, has constituted the friction overdrive clutch that the band pusher dog has the out star wheel structure.Keep the trend of rotating in the same way by the contact friction mode between pusher dog and line shaft simultaneously.Can whether the control pin by the slip ring end face be to protruding the control of control end on the pusher dog outer rim, in running order to reach solenoidoperated cluthes, transmission of power that from the noncircular gear to the line shaft.

One flume structure is arranged on the pusher dog outer rim in addition, link with the feather key of gear wheel hub, the locking mechanism and the relative star-wheel with the pusher dog control end that have constituted the axial return of restriction slip ring make circumferentially to change the release mechanism that links.After driving slip ring and leave pusher dog by linking mechanism and shift fork, when pusher dog is in when making gear and line shaft separated state, feather key protrudes to side direction and is in a high position, limits the close of slip ring return and pusher dog; And be in when making gear and line shaft jointing state when pusher dog, flume structure is with the pusher dog backswing, and feather key is dialled back by flume structure and is in low level in the keyway, does not limit the close of slip ring and pusher dog.After slip ring and control pin and pusher dog are close, when making gear and line shaft realize automatic separated state, gap between the cavity sides of pusher dog control end and star-wheel increases, and the space of control pin insertion pusher dog fork is in pusher dog and makes gear and line shaft maintenance separated state.This has quite increased locking mechanism and the release mechanism that is made of flume structure, feather key on above-mentioned circular gear mechanism free wheel device pusher dog control mechanism basis, formation is in state to be separated when making free wheel device be in jointing state, and constitutes the mechanism that stablizes separated state immediately after entering separated state.The flume structure of pusher dog, feather key, limit shelves, slip ring and buckle projection have constituted the control mechanism of noncircular gear free wheel device operating mechanism pusher dog.

C, gearshift procedure explanation

Suppose that this automobile gear speed changer at first is in one grade of work, line shaft 56 is in the minimum operating speed (see figure 8).At this moment, the shift fork 3a corresponding with gear 4a is subjected to the projection effect on the shift shaft, and slip ring on the 4a and control pin leave the control position, break away from the effect to pusher dog and roller, and this clutch is in the stable engagement state.All the other each shift forks are in and are subjected to shift fork spring state of a control, and the corresponding melon of dialling of its corresponding slip ring control makes each clutch keep separating, so all the other clutches are in stable separated state.

Shift shaft is turned in the rotation process of second gear home position by one grade of home position, and at first shift fork 3a loses the control of shift shaft, under the effect of spring, rotates and the slip ring on the gear 4a wheel hub is pressed to pusher dog.Because the free wheel device principal and subordinate moving part relative movement of gear 4a does not change, the position of pusher dog does not also change, control pin on the slip ring can't all enter control gap, the state of this moment is a state to be separated, in case the relative oscillating quantity of pusher dog allows the control pin to enter, and then can make this free wheel device enter stable separated state.

Shift shaft is rotated further, and then can make the slip ring of transition wheel 5a and control pin that the trend of pulling out be arranged to shift fork 3d effect.In case the control pin is transferred to transition wheel 5a then can be in state to be joined, the condition achievement will engage automatically takes over gear 4a realization transmission of power function.(see figure 9)

Because what paired transition wheel 5a realized is the gear ratio transmission, its velocity ratio maximum value is greater than one grade velocity ratio, and its minimum value is less than the velocity ratio of second gear.If the angular velocity of noncircular gear 5a is lower than the angular velocity of line shaft at this moment, the friction torque of axle makes the relative star-wheel swing of pusher dog, and opening increases, control pin and pusher dog on the slip ring projection are thrown off, slip ring promptly is drawn out, and the clutch on the 5a will enter jointing state, and is in state to be separated.If the angular velocity of transition wheel 5a is higher than the angular velocity of line shaft, friction torque makes pusher dog hook the hook of projection on the slip ring, and slip ring temporarily can not be pulled out, and when only reaching aforesaid state, slip ring just can be drawn out.

After slip ring was drawn out, when the velocity ratio of transition wheel was reduced to identical with one grade of velocity ratio and is greater than, transition wheel was taken over the control to line shaft, and the rotating speed of line shaft can improve thereupon.This moment, friction torque can make swing relative with star-wheel of pusher dog of 4a gear, and opening increases, and the clutch of 4a gear separates automatically, and the buckle projection of slip ring is pressed on the 4a, makes the separation of clutch enter stable separated state.After this rotating speed of line shaft can change with the speed of transition wheel.

Because shift shaft does not stop in this position, so shift fork 3d loses the control of shift shaft immediately, is pushed back by the shift fork spring, the clutch of transition wheel 5a promptly enters state to be separated.Be not lockable again through jointing state for fear of this clutch, the slide key of being controlled by the skewed slot of pusher dog is promptly ejected after shift fork 3d turns an angle at once.Limited the return of shift fork.Have only when pusher dog certain corner really takes place, positive stop key is just pushed back by skewed slot, and shift fork and slip ring are pushed back by shift fork spring or the return spring 71 that sets up, guarantee that the clutch of 5a is in state to be separated in good time.

(see figure 10) was by gear shift wheel positioning device locking when shift shaft was rotated further to the second gear working position, and this moment, shift fork 3b was open, and made the slip ring on the gear 4b that the trend of being drawn back be arranged.Equally and since this moment gear 4b rotating speed be higher than the rotating speed of line shaft 56, friction torque makes hooking that control is sold on pusher dog and the slip ring on it, slip ring can't be drawn out immediately.Raise gradually by the rotating speed of the line shaft 56 of transition wheel control, when the speed of line shaft is higher than the rotating speed of gear 4b, friction torque makes that pusher dog is relative with star-wheel to be swung, opening increases, the hook and the pusher dog of control pin on the slip ring are thrown off, slip ring is outwards removed under the shift fork spring action, pusher dog is in unrestricted state (being state to be joined) immediately, when the speed of transition wheel drive line shaft 56 drops to less than the rotating speed of gear 4b, the clutch of 4b changes jointing state over to, and the speed of line shaft 56 changes by gear 4b to be controlled; In this simultaneously, the clutch of gear 5a separates automatically, and friction torque makes that the pusher dog on the 5a is relative with star-wheel to be swung, the opening increase, and the slip ring on the 5a is pressed into the gap of pusher dog and star-wheel, and makes the clutch of 5a be in stable separated state.More than realized gearshift procedure from one grade to second gear.

Opposite from the gearshift procedure of second gear to a grade with one grade of gearshift procedure to second gear.

Gearshift procedure between second gear, third gear (seeing Figure 11,12) is similar to one grade, the gearshift procedure of second gear, and institute's difference is that initial shelves are different with the purpose shelves, and transition wheel 5b replaces 5a participation gearshift procedure.

Velocity ratio variation relation between actual input shaft of gearshift procedure and output shaft has been realized the gearshift procedure of uninterruptible power as shown in phantom in Figure 2.

D, other explanations

Above-mentioned discussion is to carry out under the prerequisite that the power direction of input shaft and output shaft relation remains unchanged basically, can be that realize on the basis with band pusher dog roller-type overrunning clutch.But in some actual practical field, the power direction of diaxon relation may take a turn for the worse at any time, and the clutch that is adopted in the structure this moment should be band pusher dog double rolling key clutch, and the structure of the more above-mentioned clutch of realization of concrete structure is complicated a little.When adopting band pusher dog roller type double rolling key clutch (seeing Figure 13,14,15) or band pusher dog wedge block type double rolling key clutch (seeing Figure 28) in each grade of gear-shift transmission of automobile and the transition shelves gear mechanism, this speed change gear can utilize engine braking and realize the continuous increase and decrease shelves of uninterrupted braking force, as travelling of long abrupt slope and ice and snow road under the heavy-duty vehicle, all can satisfy job requirement.

Embodiment two, a kind of automobile gear-shift transmission of uninterruptible power, there is the bearing of gear housing, gear housing that two rotatingshaft I, II are being set, have the circular gear of three pairs of different drive ratios in relative rotation between the axle, constituted three shelves circular gear mechanisms.The corresponding noncircular gear in pairs that also is being provided with between the axle in relative rotation of every adjacent two grades of circular gear mechanisms constitutes non-circular gear mechanism.Driving gear in circular gear mechanism, the non-circular gear mechanism and active rotation axle are fixedly connected, driven moving gear 4a in circular gear mechanism, the non-circular gear mechanism, 4b, 4d, 5a, 5b connect by roller-type overrunning clutch (seeing Figure 23,24,25,23.1,23.2) with driven rotatingshaft II, have formed five normal meshed gears mechanisms between two rotatingshaft I, II.Also have the operating mechanism that translation shift fork, slip ring and control pin thereof constitute at free wheel device.In the non-circular gear mechanism of each adjacent circular gear mechanism and configuration, the least radius of driving gear 5a ', 5b ' is less than the radius of bottom gear driving gear in the adjacent circular gear mechanism, and its maximum radius is greater than the radius of adjacent circular gear mechanism high speed shelves driving gear.In the non-circular gear mechanism of adjacent circular gear mechanism and configuration, the least radius of driven gear 5a, 5b is less than the radius of adjacent circular gear mechanism high speed shelves driven gear, and its maximum radius is greater than the radius of bottom gear driven gear in the adjacent circular gear mechanism.We can say that also free wheel device is a band pusher dog roller-type overrunning clutch, operating mechanism is the control mechanism of pusher dog and control pusher dog swing position.The mechanism of the circumferential swing position of control pusher dog is the control mechanism that pusher dog is in or is not in restriction roller working state, sees Figure 23.The control mechanism of noncircular gear free wheel device is in state to be separated when making free wheel device be in jointing state, and promptly constitutes the mechanism that stablizes separated state, Figure 23 .1,23.2 after entering separated state; Just make pusher dog not be in restriction ball, roller or voussoir working state earlier, when after free wheel device enters jointing state, entering separated state again, make pusher dog be in the interlock control mechanism of restriction ball, roller or voussoir working state, make free wheel device be in stable separated state at last.The free wheel device operating mechanism of this noncircular gear is to have increased locking mechanism and release mechanism on the operating mechanism basis of circular gear, is to control the corresponding position of pin side by side at two a lever is set, and lever has return spring; One end of lever is corresponding with side by side control pin back segment, and respectively and between the two control pin back segments ball is set, and two control pin back segments have groove; The other end of lever is corresponding with the spring clip of axle or axle sleeve.These parts have constituted the control mechanism of noncircular gear free wheel device pusher dog with the control pin of slip ring, band spring, formed with pusher dog and to be in state to be separated when making free wheel device be in jointing state, and after entering separated state, promptly constituted the mechanism that stablizes separated state.Spring clip, ball, groove, lever and return spring have constituted the locking mechanism of the axial return of restriction slip ring between slip ring and the star-wheel and have changed the releasing lockable mechanism that links with the pusher dog swing position., having linking mechanism between the pusher dog control mechanism that Figure 23 .1, the locking mechanism shown in 23.2 and release mechanism also are applicable to each roller-type overrunning clutch of Wedge type over running clutch.Like this, have the linking mechanism according to control program control between the free wheel device operating mechanism of the non-circular gear mechanism transition wheel of the initial shelves of every adjacent two grades of circular gear mechanisms, purpose shelves and configuration, control program is that initial shelves free wheel device is in state to be separated → transition wheel free wheel device and is in state to be joined → purpose shelves free wheel device and is in state to be joined.

This automobile can constitute (the figure middle gear is simplified) as shown in figure 16 by linking mechanism, each operating mechanism, each roller-type overrunning clutch (following can be called for short clutch) with the gearshift structure of uninterruptible power gear-shift transmission.The linking mechanism that mainly comprises gear shift control pull rod 71 and slip taper pin device 72 thereof and slip shift fork 73 and parallel slide-bar 74 formations; The engagement sleeve group 75 that also comprises each grade can continuous rotating noncircular gear clutch pack 76, line shaft 77 (output shaft) etc.1a, 1b, 1c are respectively one, two in addition, the third gear circular gear, and 2a is transition wheel between a second gear (transition wheel be can the another kind of address of continuous rotating noncircular gear).2b is a transition wheel between two third gear.Among the figure each gear all with input shaft on fixing respective gears keep the normal engaged relation.

Gear shift control pull rod 71 is moved by selector device (can be manual or automatic) control, and the corresponding slip taper pin that drives slip taper pin device 72 moves down or return, make corresponding slip shift fork 73 move or return along parallel slide-bar 74, drive slip ring (slip ring) action on the respective clutch, maybe will recover automatically to engage the working state of separating automatically again to control the corresponding free wheel device state of resuming work, and perhaps control corresponding free wheel device and get back to and keep the state that separates.When the needs gear shift, pull bar 71 is stirred shift fork 73, drives the slip ring action on the respective clutch, maybe will move to control corresponding free wheel device operating mechanism action; And be not subjected to the shift fork of pull bar and the effect of slip taper pin, and all under the effect of shift fork spring, be in and make slip ring to the position that gear is close to, make corresponding free wheel device be controlled in stable separated state, the elementary process of Here it is linking mechanism.Gear shift control pull rod 71, slip taper pin device 72, slip shift fork 73, parallel slide-bar 74 and slip ring have constituted linking mechanism.

Linking mechanism carries out according to Figure 16-Figure 20 process from the course of action that second gear is changed to the third gear process changing to second gear from one grade again, and has just finished the gear shift of corresponding uninterruptible power.The operating mechanism of each adjacent gear is the same with embodiment two process with the conversion process of free wheel device.

The free wheel device of gear 4a, 4b, 4d, by and the shell 14 that is fixedly connected of gear, and the star-wheel 13 that is connected as a single entity of axle II, the roller 16 that is arranged between star-wheel and the shell constitute.Also have pusher dog 15 between star-wheel and the shell, the pawl of pusher dog is distributed between each roller.The control end of pusher dog inserts the control chamber 11,12 of star-wheel.Star-wheel also is with in axial sliding slip ring (structure and fork shift cover, gear shift circle similar) 17, and slip ring is being provided with the control pin corresponding with control chamber 18,19 by spring.Control pin 18,19 is corresponding with control chamber 12,11 respectively.Spring, slip ring, control pin, control chamber, pusher dog have constituted operating mechanism.Spring, slip ring, control pin have constituted the control mechanism of the relative star-wheel control chamber of pusher dog swing position.This roller type double rolling key clutch of each free wheel device is the axle bi-directional power that is used to rotate.If be unidirectional delivery power, only need to use the parts of a direction.Also can adopt mono-directional overrun clutch, also just be equivalent to the control chamber one side cavity 11 or the 12 usefulness fixtures of above-mentioned double rolling key clutch are blocked the wherein situation at a place.

The maximum radius of eccentricity gear 5a, 5b (dactylus curve radius vector) is respectively greater than the radius (dactylus circle radius) of gear 4a, 4b, the least radius of eccentricity gear 5a, 5b is respectively less than the radius of gear 4b, 4d, the AO of eccentricity gear 5a, 5b, BO radius equal the radius of gear 4b, 4d respectively, and the CO of eccentricity gear 5a, 5b, DO radius equal the radius of gear 4a, 4b.The structure of gear 4a, 4b, 4d free wheel device operating mechanism is referring to Figure 23,24,25, and their structures are the same.When design control space 11,12 width and control pin 19,18 thickness and front end anti-retreating hook thereof, reach after control pin 19,18 enters space 11,12 entirely, pusher dog 15 only swings to or will just can withdraw from control space 12 near 18 of control pin 19 time controls cotters; Otherwise pusher dog 15 only swings to or will closely control pin 18 o'clock, and 19 of control pins just can withdraw from controls space 11; Otherwise 19,18 1 control spaces of also can not moving back separately of control pin.After one of them control pin withdrawed from, pusher dog 15 pendulum angles just can more help withdrawing from another control pin greater than above-mentioned angle.The free wheel device of non-circular gear mechanism and operating mechanism are big to the same with gear 4a, 4b, 4d free wheel device and operating mechanism, just increase a locking mechanism and release mechanism (seeing Figure 23 .1,23.2) on circular gear free wheel device and operating mechanism basis.When transforming to top gear circular gear mechanism 3,6 transferring power, will utilize the non-circular gear mechanism rotational angular velocity to become big process gradually from the circular gear mechanism transferring power of bottom gear.The direction of transmission of power is to be transmitted to axle II by axle I.At this moment the free wheel device of gear 4a is in jointing state, and the free wheel device of gear 4b, 5a all is in separated state.Each operating mechanism of handsetting gear 4a, 4b, 5a free wheel device successively all moves the slip ring of gear 4b, 5a to the direction that deviates from part 13, the slip ring that can also make gear 4a moves towards the direction of part 13.Make 4b gear control pin 19 and 18 withdraw from the control space 11 and 12 of free wheel device.The radius of gear 4b is greater than the radius of gear 4a, so at this time the rotating speed of gear 4b is lower than an II rotating speed, so control pin 18 temporarily moves back not between clearancen 12, just spring is compressed to await a favorable opportunity and withdraws from automatically, and at this time 19 of control pins withdraw from control space 11.The free wheel device of gear 4a is in jointing state, and the control pin 19 in the gear 4a free wheel device enters space 11, and control pin 18 does not temporarily enter space 12, and just spring is compressed to await a favorable opportunity and enters automatically.The free wheel device of gear 5a is in separated state, and the free wheel device control mechanism of gear 5a will be controlled the control space 11,12 that pin 19 and 18 withdraws from free wheel device.Because at this time gear 5a and gear 2 engagements are rotated, forward this section interval of C to by D, because the engagement radius of gear 5a is less than the radius of gear 4a, so at this time the rotating speed of gear 5a (angular velocity) is to be higher than an II rotating speed (angular velocity), so control pin 19 temporarily move back not between clearancen 11 just spring be compressed to await a favorable opportunity and withdraw from automatically, 18 of control pins withdraw from control space 12.When 2 engagements of gear 5a and gear forward this section interval that is forwarded to A by C to, the engagement radius of gear 5a changes from small to big gradually, angular velocity also is less than an II angular velocity gradually from large to small and at the very start, at this moment gear 5a just takes over the power (task) of transferring power from gear 4a, and gear 4a free wheel device is surmounted automatically.The control pin 18 of the operating mechanism of gear 4a free wheel device enters space 12 automatically under the effect of spring simultaneously, and the free wheel device of gear 4a is in separated state.When gear 5a engagement is rotated, engagement is forwarded to this section interval of B by A, the engagement radius of gear 5a is the radius greater than gear 4b, at this time the rotating speed of gear 4b is higher than an II rotating speed, thus the control pin 18 of the operating mechanism of gear 4b free wheel device spring do with under withdraw from space 12 automatically.The free wheel device operating mechanism of steerage gear 5a all moves the slip ring of gear 5a towards the direction of part 13 simultaneously, makes control pin 19 enter space 11, and control pin 18 does not temporarily enter space 12, and just spring is compressed to await a favorable opportunity and enters automatically.When gear 5a and gear 2 engagement rotations, forward this section interval of D to by B, the engagement radius of gear 5a is less than the radius of gear 4b at the beginning, at this time the rotating speed of gear 4b is less than an II rotating speed, and gear 4b free wheel device is in jointing state and the free wheel device of gear 5a is surmounted automatically.At this moment gear 4b just takes over the power (task) of transferring power fully from gear 5a.Forward this section interval of D to by B, the engagement radius of gear 5a is the radius less than gear 4b, at this time the rotating speed of gear 5a is to be higher than an II rotating speed, makes control pin 18 enter space 12 automatically under doing of spring used, make the free wheel device of gear 5a be in separated state.Circular gear mechanism transferring power from bottom gear transforms to top gear circular gear mechanism like this, and the task of transferring power has just been finished under the prerequisite of uninterruptible power.The steering program that lowers category is opposite, handles the operating mechanism of each free wheel device respectively, just can be under the prerequisite of uninterruptible power, and the noncircular gear from initial shelves to transition is again to the purpose shelves, and just two of each free wheel device control pin sequence of movement are opposite.The upshift operation program of back transfer power is the same with forward transferring power upshift operation program, and also just two of each free wheel device control pin sequence of movement are opposite.More than the controlling of operating mechanism of adjacent two grades of circular gear mechanisms and corresponding each free wheel device of non-circular gear mechanism, once finish with linking mechanism (Figure 16-20, referring to 8-12), the operating mechanism of non-circular gear mechanism free wheel device at this moment adopts as Figure 23 .1,23.2 structure, also can adopt as Fig. 6,7 structure.

As Figure 23 .1,23.2 structure, the operating mechanism of non-circular gear mechanism free wheel device is that the slip ring at said gear 5a operating mechanism is provided with a lever, and lever has return spring; One end of lever is corresponding with side by side control pin back segment groove, and ball is set respectively between the two; The other end of lever is corresponding with the spring clip of axle or axle sleeve.These parts have formed a locking mechanism and release mechanism, and have constituted the control mechanism of noncircular gear 5a free wheel device pusher dog with the slip ring of gear 5a, the control pin of band spring.

When changing to bottom gear circular gear mechanism transferring power, mainly utilize the eccentricity gear mechanism rotational angular velocity process that diminishes gradually from the circular gear mechanism transferring power of top gear.The free wheel device of gear 4a is in jointing state, and in relative rotation the axle I, II between transferring power.The free wheel device of gear 5a, 4b is in separated state.The linking mechanism of handsetting gear 4a, 5a, 4b free wheel device moves the gear shift circle of gear 5a free wheel device, withdraw from the control pin of free wheel device.To surmount the state probability bigger because gear 5a free wheel device is in, and the control pin withdraws from soon, and the control pin 18 or 19 in the free wheel device withdraws from space 11 or 12.Here it is rotates when gear 5a engagement, forward C to by A and forward D to and forward B again to or forward D to and forward C to and forward A again to by B, the free wheel device of gear 5a always through n to surmounting state, control pin 18 or 19 is easy to withdraw from space 12 or 11.The while linking mechanism also moves the gear shift circle of gear 4b free wheel device, insert the control pin of free wheel device.Then when gear 5a engagement rotation, forward A to or forward B to by B by A, its engagement radius by OB to OA or OA to OB, the engagement radius of gyration is greater than gear 4b radius, the free wheel device of gear 5a is engaged, by eccentricity gear mechanism transferring power, reach with regard to the free wheel device that makes gear 4b simultaneously and surmount state, and make the control pin insertion of gear 4b free wheel device surmount the control chamber space 11 or 12 that motion moves out, two control pins all insert control chamber space 11 and 12, make gear 4b keep separated state.Soon, driven shaft 8 angular velocity are reduced gradually after the eccentricity gear mechanism transferring power.Simultaneously the control pin of the operating mechanism of gear 5a all withdraws from control chamber, and it is close as the release mechanisms of Figure 23 .1,23.2 expressions slip ring to be begun to part 13 returns, and one of control pin enters control chamber, another will enter control chamber.When gear 5a is forwarded to C or forwarded to D by B by A, its engagement radius by OA to OC or OB to OD, the engagement radius of gyration reduces gradually, the free wheel device of gear 4a is in n to surmounting always, if the control pin of this free wheel device does not withdraw from control chamber, will under the control pin spring force effect that linking mechanism has produced, withdraw from the space of corresponding control chamber.When gear 5a is forwarded to D or forwarded to C by D by C, its engagement radius by OC to OD or OD to OC, the engagement radius is less than gear 4a radius, make the free wheel device of gear 4a engage transferring power at the very start, the transferring power of gear 4a makes gear 5a formation surmount again conversely, the double-action mechanism of gear 5a operating mechanism makes the control pin insert the control chamber of gear 5a free wheel device, makes gear 5a keep the separated state of bidirectional overtaking, finally realizes the continual speed-change process of transmission of power.

Claims (10)

1, a kind of automobile gear-shift transmission of uninterruptible power, gear housing is arranged, gear housing is being provided with by bearing and is comprising input shaft, output shaft at least two interior axles, axle has normal meshed gears and constitutes gear mechanism, Transmitted chains from the input shaft to the output shaft contains with two grades of circular gear mechanisms that turn to output at least, it is characterized in that: the Transmitted chains from the input shaft to the output shaft also contains the non-circular gear mechanism as the transition shelves, and is with adjacent two grades of circular gear mechanisms that turn to output and a corresponding configuration of non-circular gear mechanism that turns to output together; The maximum transmission ratio of non-circular gear mechanism greater than with adjacent two shelves circular gear mechanisms of its corresponding configuration in the velocity ratio of relative bottom gear, the fastest ratio of non-circular gear mechanism less than with adjacent two shelves circular gear mechanisms of its corresponding configuration in the velocity ratio of relative top gear; In two adjacent two grades circular gear mechanisms and the non-circular gear mechanism of corresponding configuration as the transition shelves, each gear mechanism all respectively have a gear with the axle or the axle with spool between connect by roller-type overrunning clutch or Wedge type over running clutch, roller-type overrunning clutch or Wedge type over running clutch also have clutch operation; Clutch operation contain the pusher dog that acts on roller-type overrunning clutch or the Wedge type over running clutch joint element, control pusher dog with respect to the star-wheel of roller-type overrunning clutch circumferentially the control pin of swing or control pusher dog with respect to the ring that has concave circular arc of Wedge type over running clutch circumferentially the control pin, the driving lever that only endwisely slips the slip ring of suit, is slidingly connected with slip ring with star-wheel or the ring that has a concave circular arc of swing, slip ring connects with control pin, has the elastic component that makes the slip ring return in Transmitted chains between the driving lever is sold in control; Have linking mechanism between the driving lever of clutch operation.

2, as the gear-shift transmission of the said uninterruptible power of claim 1, it is characterized in that: between the slip ring of the clutch operation of noncircular gear free wheel device and the star-wheel or slip ring and have the locking mechanism that also has the axial return of restriction slip ring between the ring of concave circular arc, locking mechanism has and pusher dog is made the release mechanism that circumferentially swing changes interlock.

3, as the gear-shift transmission of the said uninterruptible power of claim 2, it is characterized in that: the slip ring of noncircular gear free wheel device operating mechanism is provided with a lever, lever has return spring, between one end of lever and the control pin back segment ball is set, control pin back segment has and the ball corresponding groove, the other end of lever is corresponding with the deck of star-wheel or corresponding with the deck of the ring that has concave circular arc, has constituted locking mechanism and release mechanism.

4, as the gear-shift transmission of the said uninterruptible power of claim 2, it is characterized in that: on the pusher dog outer rim of noncircular gear free wheel device operating mechanism a flume structure is arranged in addition, star-wheel or the endless belt that has a concave circular arc have dome, star-wheel or the ring that has a concave circular arc are by dome and slip ring slip socket, dome has the feather key that pins slip ring, feather key is corresponding with flume structure to link, and flume structure has constituted with pusher dog makes the release mechanism that circumferentially swing changes interlock.

5, as the gear-shift transmission of claim 1 or 2 or 3 or 4 said uninterruptible powers, it is characterized in that: control pin front end has the projection corresponding with the pusher dog control end.

6, as the gear-shift transmission of the said uninterruptible power of claim 5, it is characterized in that: pusher dog has the inclination angle with control pin front end projection corresponding position.

7, as the gear-shift transmission of the said uninterruptible power of claim 6, it is characterized in that: star-wheel or the position that has a relative pusher dog of ring of concave circular arc have control chamber.

8, as the gear-shift transmission of claim 2 or 3 or 4 said uninterruptible powers, it is characterized in that: be associated with mechanical linkage which controls or electromagnetism linking mechanism or hydraulic power pack or air pressure linking mechanism between the clutch operation.

9, as the gear-shift transmission of claim 1 or 2 or 3 or 4 said uninterruptible powers, it is characterized in that: be provided with controlled clutch between the axle at noncircular gear place and the axle at circular gear place.

10, as the gear-shift transmission of the said uninterruptible power of claim 9, it is characterized in that: the axle at non-circular gear mechanism place is what parallel to the axis or be coaxially set with the axle at circular gear mechanism place, the axle at non-circular gear mechanism place is the connection of corresponding drive connection with the axle at circular gear mechanism place, and connects by controlled clutch.

Images