CN1651808A

CN1651808A - Uninterrupted power gear speed changer

Info

Publication number: CN1651808A
Application number: CN 200410079999
Authority: CN
Inventors: 杨斌彬
Original assignee: Individual
Current assignee: Individual
Priority date: 2004-02-02
Filing date: 2004-09-18
Publication date: 2005-08-10
Anticipated expiration: 2024-09-18
Also published as: CN100400940C

Abstract

The invention has a base or a gear box body, the base or the gear box body is provided with at least two shafts through a bearing, the shafts are connected through a gear to form a gear mechanism, the gear mechanism comprises at least two gears of circular gear mechanisms from an input shaft to an output shaft, and the gear mechanism also comprises a non-circular gear mechanism, wherein the two gears of circular gear mechanisms output in the same direction and the non-circular gear mechanism output in the same direction are correspondingly configured; two circular gear mechanisms of two gears and a corresponding non-circular gear mechanism, wherein each gear mechanism is provided with a gear which is connected with a rotating shaft or a shaft which is connected with the shaft through an overrunning clutch; the overrunning clutch is provided with an operating mechanism. The process of increasing or decreasing the angular speed of the non-circular gear is used for shifting two gears from low to high or from high to low, and the gear shifting of uninterrupted power is realized by automatically combining and separating. The maximum transmission ratio of the non-circular gear mechanism is larger than the transmission ratio of the low gear, and when the minimum transmission ratio is smaller than the transmission ratio of the high gear, the gear speed change is more reliable and stable.

Description

The gear-shift transmission of uninterruptible power

Technical field: the present invention relates to a kind of multi-stage gear speed changer, particularly just can gear shift change the gear-shift transmission of velocity ratio need not cutting off power.

Background technique: existing gear-shift transmission, the axle that relative transferring power is all arranged, be called for short transmission shaft, be driving shaft and driven shaft, have two-stage driving gear set at least between driving shaft and the driven shaft, for can conversion between the two-stage driving gear set 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 have clutch (as friction disk clutch), when speed-change and gearshift,, remove transmission of power the clutch separation between gear-shift transmission and the power mechanism.So both handled complexity, 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 the rotating speed of reduction power, just can make the driving link of unidirectional delivery torque mechanism separate because of speed discrepancy with driven member when shifted, just surmounts state.Disconnect transmission of power, 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 gear-shift transmission will be interrupted the problem of transmission of power at speed-change process, and a kind of gear-shift transmission of uninterruptible power is provided.

The gear-shift transmission of uninterruptible power of the present invention has at least two transmission shafts of bearing setting of pedestal or gear housing, pedestal or gear housing, has two-stage driving gear set (i.e. at least two grades circular gear mechanism) at least between the transmission shaft relatively.Feature of the present invention is: also be provided with noncircular gear group (i.e. the non-circular gear mechanism of transition shelves) between the corresponding transmission shaft of every adjacent two-stage driving gear set; A gear in driving gear set, the noncircular gear group is connected by free wheel device with transmission shaft, be meant two groups of gears of two-stage driving gear set and one group of noncircular gear group of corresponding configuration, have a gear to connect by free wheel device with the axle of corresponding transferring power in every group of gear, just driven gear of the driving gear of every group of two groups of driving gear set, one group of noncircular gear group or every group or every group have spool being connected by free wheel device of a gear and transferring power; Free wheel device also has clutch operation (following can be called for short operating mechanism).Clutch operation is the connected member of control free wheel device, and by the effect of operating mechanism to the connected member of free wheel device, whether the control free wheel device is in running order.Work functions and process that free wheel device separates automatically, engages automatically are referred to as working state.Make free wheel device be in separated state by operating mechanism, free wheel device just can not normally engage automatically, and we claim it to be in off working state.It is in running order to recover free wheel device by operating mechanism on the contrary.In two groups of driving gear set of adjacent two-stage, the shelves that velocity ratio is big claim bottom gear relatively, the shelves title top gear that velocity ratio is little relatively.The noncircular gear group of the corresponding configuration of adjacent two-stage driving gear set is meant, relatively between the transmission shaft, as between input shaft and output shaft, to turn to the adjacent two-stage driving gear set of output together, correspondence is disposing a transition shelves noncircular gear group that turns to output with this two-stage driving gear set together, the gear range of noncircular gear group is preferably between the velocity ratio of two groups of driving gear set of two-stage or cross over the velocity ratio of two groups of driving gear set of two-stage, also can be the maximum transmission ratio of noncircular gear group be less than or equal to or greater than with the driving gear set of its corresponding configuration in the velocity ratio of relative bottom gear driving gear set, the fastest ratio of noncircular gear group be less than or equal to or greater than with the driving gear set of its corresponding configuration in relative high speed gear group velocity ratio.Also can be described as in the adjacent two-stage driving gear set maximum transmission ratio that the velocity ratio of bottom gear relatively is less than or equal to or is slightly larger than the noncircular gear group of corresponding configuration with it, in the adjacent two-stage driving gear set velocity ratio of relative top gear more than or equal to or be slightly less than the fastest ratio of the noncircular gear group of corresponding configuration with it.All be by a pair of gear or be equivalent under the situation that a pair of gear constitutes for the noncircular gear group of adjacent two-stage driving gear set and corresponding configuration, the driving gear pitch curve minimum radius of noncircular gear group is less than or equal to or is slightly larger than the Pitch radius of bootom gear group driving gear in the adjacent two-stage driving gear set, the maximum radius vector of the driving gear pitch curve of noncircular gear group more than or equal to or be slightly less than the Pitch radius of adjacent two-stage driving gear set high speed shelves gear train driving gear.The noncircular gear group of the corresponding configuration of adjacent two-stage driving gear set, a kind of corresponding relation that is meant, they can be set up in parallel together, other gear train setting of also can being separated by, can also and other the operative gear of gear train mix to be provided with, exist as long as guarantee between input shaft and output shaft, to contain corresponding gear mechanism.The axle that the said relative transmission shaft of the present invention is exactly relative transferring power mainly is by the mutual transferring power of gear, gear-shift transmission the axle generally be rotating shaft, also contain mandrel in the gear-shift transmission that has.So relatively have driving gear set between the transmission shaft or correspondence is provided with the noncircular gear group, just at the relative Transmitted chains of transferring power axle, particularly at the Transmitted chains of input shaft to output shaft, constituted fixed gear mechanism than transmission or indefinite, also can claim circular gear mechanism or non-circular gear mechanism than drive gear mechanism.Gear train and gear mechanism that the present invention is alleged are equal to, and driving gear set and circular gear mechanism are equal to, and noncircular gear group and non-circular gear mechanism are equal to.

Alleged level of the present invention is the meaning of shelves, is meant the gear of gear, also claims shelves sometimes.Easy for what narrate below, the radius of alleged circular gear is meant Pitch radius, and the radius that relates to noncircular gear is meant the pitch curve radius vector.The radius relationship of each gear of narrating below all is the relation between the radius of driving gear, and the radius relationship between the driven gear is just in time opposite with the radius relationship between the driving gear.Following elder generation is an example with the non-circular gear mechanism that has two grades of circular gear mechanisms and a configuration between two axles, and is be described (referring to the accompanying drawing 1,2) of a pair of gear structure with gear mechanism.By bearing be provided with more than two the axle, many grades of circular gear mechanism speed changers more than the two grades arbitrarily speed change between adjacent two grades adopt basic structure of the present invention, gear mechanism is that two above gear engagement constitute, the speed-change process of these multiple situations or the combination of these situations is all similar, can analogize.Simultaneously easy for what describe, all be arranged on driving shaft (input shaft) and describe between the driving gear accordingly with the free wheel device of every grade of gear mechanism.The free wheel device of every grade of gear mechanism all is arranged between driven shaft (output shaft) and the driven gear, perhaps have be arranged between driving shaft and the driving gear, have be arranged between driven shaft and the driven gear, have be arranged on the axle with spool between, the speed-change process and the result that form are identical, and the working procedure of the free wheel device that just has is being carried out between driven shaft and the driven gear or between axle and the axle.Each gear mechanism preferably has only a gear to connect by free wheel device with rotating shaft, generally is fixedly connected between another gear of every group of gear mechanism and the axle.At gear-shift transmission stably during transferring power, wherein the free wheel device of one-level driving gear set engages, keep this one-level gear train transferring power, the free wheel device of other gear trains separates (promptly surmounting) automatically or be in separated state under clutch operation control, and the gear of these gear trains is meshing with each other and rotates but transferring power not.To adjacent other grades gear train speed change, just between the two-stage driving gear set, carry out gear shift from this one-level, as from the bootom gear group to adjacent high speed gear's group gear shift.When the corresponding noncircular gear group driving gear of bottom gear and top gear two-stage gear train configuration is engaged near the least radius, just can make noncircular gear group free wheel device in running order by operating mechanism.The least radius of this noncircular gear group driving gear is greater than bottom gear driving gear radius, or its engagement radius is increased to and is greater than bottom gear driving gear radius, the free wheel device of noncircular gear group just engages the speedup transferring power automatically, and the free wheel device of bootom gear group is separated.In this noncircular gear group speedup transferring power later stage, when the driving gear in the noncircular gear group was engaged near the maximum radius, the operating mechanism by high speed gear's group made the free wheel device of high speed gear's group in running order.The maximum radius of noncircular gear group driving gear is reduced to less than top gear driving gear radius or its engagement radius and is less than top gear driving gear radius, the free wheel device of high speed gear's group just engages transferring power automatically, and the free wheel device of noncircular gear group is separated, the gear shift that realization can uninterruptible power.If noncircular gear group driving gear maximum radius greater than the radius of top gear driving gear, can be controlled its free wheel device by the operating mechanism of noncircular gear group and be in separated state after gear shift, to keep high speed gear's group continous-stable transferring power.To adjacent bottom gear gear shift, process is just in time opposite from top gear, and just the driving gear least radius of the noncircular gear group of this two-stage driving gear configuration set is preferably less than the radius of bottom gear driving gear, the maximum radius radius greater than the top gear driving gear.Like this, utilize the noncircular gear group to have the characteristic of non-isogonism speed transmission and the characteristic of free wheel device automatic clutch, the speed change that the transmittance process that increases with driven noncircular gear angular velocity comes between the transition two-stage driving gear from low to high, the transmittance process that reduces with driven noncircular gear angular velocity comes between the transition two-stage driving gear speed change from high to low, the transmission that makes speed-change process keep power has also just realized the gear graduation of uninterruptible power.Also we can say the characteristic of utilizing noncircular gear group driving gear engagement radius to reduce gradually or increase gradually, come the gear shift of transition from the top gear to the bottom gear or from the bottom gear to the top gear.In gearshift procedure, the free wheel device of the noncircular gear group of corresponding target shelves gear train and correspondence need participate in work, just can be by the working state of clutch operation real-time recovery free wheel device and connected member thereof, and remove the working state of noncircular gear group, initial shelves gear train free wheel device and connected member thereof subsequently as required in real time, and form the steady state after the gear shift.Each free wheel device can be under the control of its clutch operation, the several states that are achieved as follows: (1) " state to be joined ", and promptly free wheel device is in normal separated state, allows clutch to enter jointing state automatically when treating the condition achievement; (2) " jointing state ", promptly free wheel device makes axle and the stable connection of corresponding gear; (3) " state to be separated " is just can form separated state automatically when separation condition is achieved under jointing state, and can forms stable separated state under the control of clutch operation; (4) " maintenance separated state ", promptly to make free wheel device both make the condition achievement of joint also be to be in separated state to clutch operation, axle and corresponding gear keep stable separated state.

To the bottom gear speed-change and gearshift, process is opposite from top gear.Just the driving gear maximum radius of noncircular gear group is slightly less than or equals top gear driving gear radius, make noncircular gear group free wheel device be in state to be joined, when noncircular gear group driving gear radius is engaged to maximum radius, utilize the operating mechanism of top gear to make the free wheel device separation of top gear and be in separated state.Since the driving gear maximum radius of noncircular gear group near or equal top gear driving gear radius, the free wheel device of top gear separates just can make the noncircular gear free wheel device be in the jointing state transferring power that reduces speed now, but not as the driving gear maximum radius of noncircular gear group greater than top gear driving gear radius steadily and smoothly.Equally, when the driving gear least radius of noncircular gear group is slightly larger than or equals bottom gear driving gear radius, make bootom gear group free wheel device be in state to be joined earlier, when noncircular gear group driving gear radius is engaged to least radius, utilize the operating mechanism of noncircular gear group to make the free wheel device separation of noncircular gear group and be in separated state.Since the driving gear least radius of noncircular gear group near or equal bottom gear driving gear radius, the free wheel device of noncircular gear group separates just can make bootom gear group free wheel device be in jointing state, but not as the driving gear least radius of noncircular gear group less than bottom gear driving gear radius steadily and smoothly.

Angular velocity from the driven gear of noncircular gear group, by top gear to the bottom gear speed change, make the in running order state to be joined of free wheel device of noncircular gear group earlier, noncircular gear group driven gear angular velocity is elevated to identical with the top gear driven gear and when being greater than, the free wheel device of noncircular gear group engages also the free wheel device of high speed gear's group is separated automatically, makes free wheel device keep separated state with the operating mechanism of high speed gear's group; Reduce the later stage at noncircular gear group driven gear angular velocity, noncircular gear group driven gear angular velocity is reduced to identical with the bottom gear driven gear and when being less than, the free wheel device of bootom gear group is in jointing state automatically, and the free wheel device of noncircular gear group is separated automatically, make the free wheel device maintenance separated state of noncircular gear group with the operating mechanism of noncircular gear group.When the driving wheel least radius of the noncircular gear that matches less than the driving gear radius of bottom gear, maximum radius during greater than the driving gear radius of top gear, the free wheel device of noncircular gear can engage automatically or separate and the free wheel device of top gear, bootom gear group is separated automatically in the speed change transfer process.After the free wheel device of noncircular gear group, high speed gear's group separates automatically, can make the free wheel device of automatic separation keep separated state by clutch operation, the stationarity after the maintenance gear shift.Thus, in the noncircular gear group of adjacent two-stage driving gear set and configuration, preferably less than the radius of bootom gear group driving gear in the adjacent two-stage driving gear set, the driving gear maximum radius of noncircular gear group is more preferably greater than the radius of adjacent two-stage driving gear set high speed shelves gear train driving gear for the driving gear least radius of noncircular gear group.That is to say, in the noncircular gear group of adjacent two-stage driving gear set and configuration, preferably less than the Pitch radius of bootom gear group driving gear in the adjacent two-stage driving gear set, the maximum radius vector of the driving gear pitch curve of noncircular gear group is more preferably greater than the Pitch radius of adjacent two-stage driving gear set high speed shelves gear train driving gear for the driving gear pitch curve minimum radius of noncircular gear group.Relatively the velocity ratio of bootom gear group is preferably less than the maximum transmission ratio of the noncircular gear group of corresponding configuration with it in two groups of driving gear set of adjacent two-stage of the present invention that Here it is, and the velocity ratio of relative high speed gear group is more preferably greater than the fastest ratio of the noncircular gear group of corresponding configuration with it in two groups of drive gear mechanisms of adjacent two-stage.Make the power-converting between the gear be more prone to eliminate the impact of gear shift like this with steady.

Every grade of driving gear set, cooperate between the gear of noncircular gear group and all keeping engagement, utilization can engage automatically, separate automatically and transforming gear that the free wheel device that can control keeps uninterruptible power to transmit, guaranteed that effectively gear-shift transmission is in speed-change process transferring power stably.Wherein the free wheel device of one-level driving gear set is in jointing state, transferring power between two relative axles.Can make the free wheel device of other grade driving gear set and noncircular gear group be in separated state by the operated clutch operating mechanism, the gear of these gear trains be meshing with each other and rotates but transferring power not.Between the two-stage driving gear set of relative transmission shaft during conversion, the free wheel device of handling the noncircular gear group earlier makes it change state to be joined over to by separated state, Deng the angular velocity varies of noncircular gear group engagement rotation to identical with initial grade of gear rotational angular velocity of transferring power and desire greater than the time, its free wheel device engage transferring power automatically and the rotational angular velocity of driven shaft is increased gradually or increase slightly after reduce gradually again, just make simultaneously the free wheel device of the initial shelves driving gear set of former transferring power surmount automatic separation, and can keep separated state by operating mechanism, between transmission shaft, keeping transferring power by the noncircular gear group.Increase and reduce or reduce gradually the later stage gradually at rotational angular velocity, the angular velocity varies of noncircular gear group engagement rotation to identical with the purpose shelves gear rotational angular velocity of wanting transferring power and desire less than the time, make adjacent one-level want the top gear of transferring power or bottom gear purpose shelves driving gear set free wheel device to engage automatically again, make this purpose shelves driving gear set be in the transferring power state, and the free wheel device of noncircular gear group surmount separation.When so just keeping the transferring power function, finished the purpose (concrete detailed process is seen embodiment) of speed change again always.By at a high speed when bottom gear change, need after surmounting separation, top gear free wheel device, noncircular gear free wheel device make clutch maintenance separated state by corresponding clutch operation.

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.Free wheel device is can engage automatically and the clutch that separates automatically.The present invention has not only utilized free wheel device to engage automatically and the characteristic of separating automatically, has also adopted clutch operation that free wheel device is controlled simultaneously, and the control free wheel device keeps separated state.The manipulation control of clutch operation is in separated state even the condition that can make free wheel device reach automatic joint is also controlled it; Can control free wheel device and be in normal working state, promptly the rotating speed of driven member then is to surmount separation greater than the rotating speed of driving link, the rotating speed of driven member equal or the rotating speed of the little driving link of desire then free wheel device engage transferring power.The present invention can also control free wheel device makes driven member can freely rotate with respect to driving link, is equivalent to always be in separation (surmounting) state.Clutch operation can be selected different operating mechanisms for use according to different free wheel devicees, for existing ratchet ratchet free wheel device, the turn key free wheel device, ball or roller or voussoir free wheel device can be selected existing clutch operation for use, as stir ratchet, the bar of stage clip is (referring to Figure 34,35), control the linkage mechanism of stirring of turn key, the pusher dog mechanism of control ball or roller or voussoir etc., the operating mechanism of the free wheel device (overrunning clutch) in the reverse controlled gear of the unidirectional delivery of the applicant's application in the past and the operating mechanism of steel band overrunning clutch can be selected for use, also new on-off control mechanism can be designed.As existing clutch operation operating process, ratchet type overrunning clutch (also claiming the control type pawl clutch) as the vertical mechanism of ribbon gymnastics is to limit or recover ratchet with bar and double-action mechanism etc. to engage with ratchet, the pivotal position of the turn key manipulating mechanism control turn key of turn key free wheel device (also claiming rotating key clutch), the operating mechanism of steel belt clutch (steel band free wheel device) or the control structure of pressure mechanism are controlled the exerting pressure of steel band end, and whether free wheel device (overrunning clutch) the operating mechanism control in the controlled driving mechanism of unidirectional delivery feedback is in running order.Can also insert or withdraw from the lateral location such as joint element ball, roller, voussoir of friction overdrive clutch with the separator levers end of existing clutch operation, control these joint elements and be in separated state or recover it and engage automatically and the automatic state that separates.Insert or withdraw from the relative star-wheel of pusher dog of friction overdrive clutch with the separation rod end of operating mechanism and (see Figure 23,24,25, the ring of band concave circular arc is also identical, referring to Figure 42,43,44) swing position, control lateral location such as joint element ball, roller, voussoir indirectly, control that these joint elements are in separated state or the state of resuming work.For the use of double rolling key clutch, more need to control the working state (referring to Figure 23,24,25) that realizes certain direction with operating mechanism, the double rolling key clutch of operating mechanism control just keeps certain direction or two-way separated state.The operating mechanism of control free wheel device is realized gear shift, and to control controlled clutch the same with handling speed change lever, just the effect that produces difference to some extent.Existing gear shift is to handle speed change lever, and the action controlled clutch directly makes gear close, separate with relative being coupling with gear shaft or gear shaft.Behind the operating mechanism action free wheel device of the present invention, just make when free wheel device will reach condition between gear and axle or axle and the axle and engage automatically, separate automatically, and be that the free wheel device of taking over the gear mechanism of transferring power mutually engages, separates and carry out synchronously automatically, alternate tooth wheel mechanism velocity ratio is suitable.It is uninterrupted that the present invention can keep transferring power thus, and do not overlap the energy consumption of transmission, saves the power and the energy.

For the use of double rolling key clutch, more to control the working state (referring to Figure 23,24,25) that realizes certain direction with clutch operation.Clutch operation is also controlled free wheel device and is kept unidirectional or two-way separated state.Slow for rotating speed, when the gear-shift transmission structure is bigger, can control free wheel device by the manual driven operating mechanism, as manually stirring ratchet or turn key or pusher dog, make ratchet engage, not engage with ratchet, make turn key with key engagement, do not engage, pusher dog make roller of friction overdrive clutch etc. be in, not in running order.People's controlled clutch operating mechanism, can directly move clutch operation with hand, can also be by mechanical double-action mechanism control, also can pass through hydraulic mechanism, Pneumatic Transmission mechanism controls, can also keep the separated state surmount with mechanism controls free wheel devicees such as electric control motor, electromagnet, perhaps control recovers the original working state of free wheel device.Electronic, hydraulic parts, pneumatic can be set, the clutch operation that forms with these actuators changes states such as ratchet, turn key, ball, roller, contract piece, also can drive clutch operation with these actuators, to realize making free wheel device be in stable separated state, still be in the normal working of free wheel device.Clutch operation can be electromagnetically-operated mechanism or hydraulic control mechanism or pneumatic control mechanism, is associated with between the electromagnetically-operated mechanism to be associated with between program control mechanism or the hydraulic control mechanism between program control mechanism or the pneumatic control mechanism to be associated with program control mechanism.Surmount operating mechanism more in phase by above-mentioned process work for the non-circular gear mechanism that makes adjacent two grades of circular gear mechanisms and configuration, respectively surmounting of the non-circular gear mechanism of adjacent two grades of gear trains and configuration preferably is provided with these linking mechanisms between the operating mechanism, so that according to the priority program behavior.The situation of as similar automobile, need running at high speed, the gear-shift transmission of employed uninterruptible power, as existing gear-shift transmission, be preferably with linking mechanism between the free wheel device operating mechanism of the initial shelves of every adjacent two grades of circular gear mechanisms, purpose shelves and configuration non-circular gear mechanism according to control program control, so that according to the step that configures, drive the state of each free wheel device of control continuously.Like this than manually directly control operating mechanism on time more accurately with more reliable.Between the operating mechanism that can adjacent two grades of circular gear mechanisms and the operating mechanism of corresponding non-circular gear mechanism linking mechanism is set separately, also can be connected into whole linking mechanism to each linking mechanism.

So-called noncircular gear group, be exactly the eccentricity gear and the gears such as elliptic gear, square gear of engagement relatively, in the transmission process of a circle, it is that non-isogonism speed is rotated that the driving gear average rate is rotated the then rotation of driven gear, and angular velocity diminishes gradually not only to become greatly gradually or become gradually and diminishes gradually greatly not only or several process that diminishes greatly but also gradually that becomes gradually.At the rotation process of a circle two or more processes that diminish gradually again greatly that become are gradually arranged, become greatly not only or become 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 as long as diminish gradually through an angular velocity, gear shift once.The noncircular gear of indication mainly is can 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 or the overrunning clutch that have.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 (referring to Figure 34,35).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 (Figure 34,35 two opposite mono-directional overrun clutchs are engaged and just constituted double rolling key clutch) of the opposite mono-directional overrun clutch of both direction, the also double rolling key clutch of design that can be single.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.For the speed changer of the present invention that is used for automobile, in order to prevent automobile sideslip tuning when ice ways face is exercised, utilize engine braking, also to adopt double rolling key clutch.

The preferred friction overdrive clutch of the present invention is as ball type free wheel device or roller-type overrunning clutch or voussoir free wheel device.To friction overdrive clutch control, be band pusher dog friction overdrive clutch, the clutch operation that band pusher dog friction overdrive clutch has is to be arranged on the pusher dog of connected member side and the control mechanism of the relative star-wheel swing position of control pusher dog.The control mechanism of the relative star-wheel swing position of control pusher dog is linking mechanism or the double-action mechanism that pusher dog is in or is not in restriction ball, roller or voussoir working state, is called for short control mechanism.For the friction overdrive clutch of control band pusher dog, be exactly position by the relative star-wheel of control pusher dog, the connected member that limits clutch is the original working state of ball, roller or voussoir.That is to say the angle of oscillation of control pusher dog relative star-wheel, can adopt and insert block or draw key or turn key or sliding pin wait the connected member that limits or lift restrictions.Can be to form clutch operation with have the driving link of the friction overdrive clutch control pusher dog of being with pusher dog such as the control mechanism that motor is controlled the relative star-wheel swing position of pusher dog instead, if pusher dog and motor in the original friction overdrive clutch that has pusher dog are regarded as clutch operation, motor can be stepper motor or motor limited the various control mechanisms of pusher dog swing instead, form new clutch operation.For the free wheel device of the noncircular gear group that makes adjacent two-stage gear train and configuration is undertaken by the program of setting more in phase, be provided with linking mechanism between each free wheel device control pusher dog limting mechanism of the noncircular gear group of adjacent two-stage gear train and configuration.For the ease of coordination, the pusher dog control mechanism of noncircular gear free wheel device preferably makes free wheel device in a single day enter to transfer state to be separated immediately to behind the jointing state and finally is in the linking mechanism of stablizing separated state again; Just make pusher dog not be in restriction ball, roller or voussoir working state earlier, after free wheel device enters jointing state automatically, when this linking mechanism can make free wheel device enter free wheel device such as state to be separated automatically again direction takes place once to relatively rotate again to change, make pusher dog be in the mechanism of restriction ball, roller or voussoir working state (stablizing separated state).The pusher dog control mechanism of the mono-directional overrun clutch of noncircular gear with two-way be the same.Come to this a kind of linking mechanism of program of the pusher dog control mechanism of noncircular gear free wheel device or clutch operation.

And the clutch operation that has of roller-type overrunning clutch or voussoir free wheel device, preferably select pusher dog for use.So-called pusher dog is exactly the pusher dog of the roller clutch of existing band pusher dog, the perhaps shift fork of voussoir double rolling key clutch.Picture pusher dog and shift fork are similar, can unitedly call pusher dog or control pawl.Pusher dog (control pawl) 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, or in the roller, voussoir connected member opening or roller, protruding place, voussoir two.Free wheel device is preferably roller-type overrunning clutch, the clutch operation that has is preferably pusher dog, the pawl of pusher dog is arranged on the wedge groove at roller place, the swinging end of pusher dog is positioned at the control chamber of star-wheel dome, the position that corresponds to control chamber on slip ring is being provided with the control pin that can insert or transfer to control chamber, control pin is connected by spring and slip ring (or be slip ring, its structure and fork shift cover, fork shift ring structure are similar).So just constituted the operating mechanism of roller-type overrunning clutch.Clutch operation can also be another kind of structure, the pawl of pusher dog is arranged on the wedge groove at roller place, pusher dog and have between the rotating component of wedge groove and have control chamber and control corresponding pin, the control pin has return spring, the control pin also is connected with hoodle by spring, hoodle is corresponding with the groove of pull bar, and pull bar is arranged in the rotating component hollow cavity that has the wedge groove movingly, and pull bar is connected with slip ring by the sliding pin that passes chute.For the speed changer of heavy machinery and the speed changer of transmission at a slow speed, can distinguish control clutch operation separately separately.Noncircular gear group collaborative work accurately continuously in order to make two-stage driving gear set and cooperation is preferably with linking mechanism between the clutch operation that each free wheel device has.Can control like this and once just can make the collaborative action according to the order of sequence of each clutch operating mechanism, real-time action under the effect of linking mechanism.

Compared with the prior art the present invention has in the uninterrupted transferring power of speed-change process, and makes driven shaft earlier after the speed transition change that will become, again by the driving gear set transferring power of wanting speed change; Mechanical wear and loss reduce greatly, have improved the efficient of speed change, have reduced the energy loss of speed-change process, and make the transmission that is keeping power in the whole speed-change process.

Description of drawings: accompanying drawing has been represented the gear-shift transmission structural representation and the part-structure schematic representation of uninterruptible power of the present invention.Wherein, Fig. 1 is the gear-shift transmission structural principle schematic representation of two-stage uninterruptible power, and Fig. 2 is the schematic representation of used eccentricity gear and engagement radius specific position; Fig. 3 is the roller type double rolling key clutch main station portion sectional view that has pusher dog, Fig. 4 has the roller type double rolling key clutch B-B of pusher dog to sectional view, Fig. 5 has the roller type double rolling key clutch A of pusher dog to partial sectional view, Fig. 3 .1 is that this roller type double rolling key clutch that has pusher dog has increased the used roller type double rolling key clutch partial sectional view (plan view) of double-action mechanism formation noncircular gear, and Fig. 3 .2 is that this roller type double rolling key clutch that has pusher dog has increased the used roller type double rolling key clutch partial sectional view (plan view) that has pusher dog of noncircular gear that double-action mechanism forms; Fig. 6 is the roller type double rolling key clutch master sectional view that another kind has pusher dog, and Fig. 7 is that this another kind has the roller type double rolling key clutch A-A of pusher dog to sectional view; Fig. 8 is the schematic representation of used elliptic gear and engagement radius specific position; Fig. 9 is the gear-shift transmission structural principle schematic representation of the mutual transferring power two-stage of diaxon uninterruptible power, and Figure 10 is the schematic representation of eccentric noncircular gear group in this speed changer; Figure 11 is a kind of gear-shift transmission transmission system sketch of three grades of uninterruptible powers, Figure 12 is the change curve of this transmission system gearshift procedure velocity ratio, Figure 13 is a linking mechanism in the gear-shift transmission of this three grades of uninterruptible powers, each clutch operation, driven shaft, the part-structure schematic representation of each driven gear and free wheel device, Figure 14 is the ssembly drawing of each grade driven gear and free wheel device and part clutch control parts, Figure 15 is the exploded view of each grade driven gear and free wheel device and part clutch control parts, Figure 16 is the ssembly drawing that can turn round noncircular gear group driven gear and free wheel device and part clutch control parts continuously, Figure 17 is the exploded view that can turn round noncircular gear group driven gear and free wheel device and part clutch control parts continuously, and the gear-shift transmission of this three grades of uninterruptible powers of Figure 18-22 is at the schematic representation of gearshift procedure linking mechanism and each clutch operation change procedure; Figure 23,24, three kinds of view of 25 band pusher dog double rolling key clutchs; Figure 26,27,28,29, the 30th, the gear-shift transmission of three grades of uninterruptible powers of another kind of interlock rod-type is at the schematic representation of gearshift procedure linking mechanism and each clutch operation change procedure; Figure 31,32, the 33rd, the noncircular gear long radius that matches, minor radius equal or are approximately equal to bootom gear, noncircular gear, high speed gear's schematic representation of high speed gear's radius, bootom gear radius respectively; Figure 34 is the structural representation of internal tooth ratchet free wheel device and operating mechanism, and Figure 35 is the structural representation of external tooth ratchet free wheel device and operating mechanism; Figure 36 is the gear-shift transmission principle schematic of four shelves uninterruptible powers; Figure 37 is the gear-shift transmission principle schematic of four shelves uninterruptible powers of a kind of non-coaxial line output and non-circular gear mechanism and the split axle setting of circular gear mechanism; Figure 38 is the gear-shift transmission principle schematic that four shelves uninterruptible powers of noncircular gear mechanism and the split axle setting of circular gear mechanism were exported and be to a kind of coaxial line, the 39th, and the gear-shift transmission principle schematic of the four-speed gear shift uninterruptible power of direct high is exported and had to a kind of coaxial line; Figure 40 is the schematic representation of controlled clutch separated state between the axle at axle and circular gear place at noncircular gear place in the gear-shift transmission of three shelves uninterruptible powers, Figure 41 be the axle at noncircular gear place in the gear-shift transmission of three shelves uninterruptible powers and circular gear place spool between the schematic representation of controlled clutch jointing state; Figure 42,43, the 44th 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 45 for input and output shaft with the parallel gear-shift transmission structural representation that is connecting four shelves uninterruptible powers of jack shaft of identical drive connection, the gear-shift transmission structural representation of Figure 46 four shelves uninterruptible powers that to be input and output shaft be connected with the jack shaft at non-circular gear mechanism place by controlled clutch; Figure 47,48,49,50 is respectively four kinds of form structure schematic representation of gear-shift transmission of three shelves uninterruptible powers that a pair of noncircular gear is combined into two non-circular gear mechanisms respectively with different circular gears and to be input shaft be connected with the driving shaft of non-circular gear mechanism by controlled clutch; Figure 51 is the gear-shift transmission of three shelves uninterruptible powers of coaxial line output that a pair of noncircular gear of a kind of usefulness is combined into two non-circular gear mechanisms respectively with two pairs of circular gears and to be input shaft be connected respectively by the controlled clutch and the driving wheel of two non-circular gear mechanisms.The sketch schematic representation that relates in the above-mentioned accompanying drawing, owing to do not find the current technique of painting of the free wheel device sketch of the vertical mechanism of ribbon gymnastics, expression is provided with the position of the free wheel device of the vertical mechanism of ribbon gymnastics among the figure, has selected for use the sketch signal of certain mono-directional overrun clutch to substitute the free wheel device signal that has operating mechanism.The example that engages accompanying drawing below further specifies the present invention.

Specific embodiment:

The large gear speed changer of embodiment one, a kind of two-stage uninterruptible power of the present invention (referring to Fig. 1,2), two transmission shafts 7,8 that have the bearing 9 of pedestal, pedestal to be provided with, power is delivered to transmission shaft 8 by transmission shaft 7.Have two-stage driving gear set 1,3,4,6 between the transmission shaft 7,8 relatively, also be provided with eccentricity gear group 2,5 between the relative transmission shaft 7,8 of this two-stage driving gear set.Driving gear 4,5,6 in two-stage driving gear set, the eccentricity gear group and transmission shaft 7 are connected by mono-directional overrun clutch.Transmission shaft 7 turn to for n be 3 rev/mins to rotating speed.The ratchet of the ratchet mono-directional overrun clutch of driving gear 5,6 has the driving lever (seeing Figure 34,35) of stirring ratchet.The semi major axis of eccentricity gear 5 is greater than the radius of gear 6, and the short radius of eccentricity gear 5 is less than the radius of gear 4, and eccentricity gear AO, BO radius equal the radius of gear 6, and eccentricity gear CO, DO radius equal the radius of gear 4.The free wheel device of gear 6 is in jointing state, and by driving shaft 7 to axle 8 transferring power.The ratchet of the free wheel device of gear 5 has been dialled by driving lever, breaks away from ratchet, makes free wheel device be in bidirectional overtaking state, i.e. separated state.The free wheel device of gear 4 since have speed discrepancy to be in naturally to surmount state (the said state that surmounts of the present invention is a kind of of free wheel device separated state, be in the free wheel device driven member rotating speed greater than a kind of state of the driving link that rotates in the same way).At this time need be by top gear to the bottom gear speed change, when active eccentricity gear 5 rotated in C to the D interval with gear 2 engagements, the free wheel device ratchet return of handsetting gear 5 contacted with ratchet.Because gear 5 angular velocity at this moment surmounts state greater than the angular velocity of driving shaft 7 so still be in.And then gear 5 rotates with gear 2 engagements, forward the position of B to from D, gear 5 angular velocity at this moment equals the angular velocity of transmission shaft 7, and be less than the angular velocity of driving shaft 7, after this because the effect of free wheel device ratchet and ratchet, then rotate, and give axle 8 transmission of power by gear 5 by driving shaft 7 driven gears 5.Then when gear 5 and gear 2 engagement rotations, by B to A, its the engagement radius by OA to OB, the engagement radius of gyration is greater than gear 6 radiuses, reach with regard to the free wheel device that makes gear 6 and to surmount state, at this time the ratchet by driving lever handsetting gear 6 free wheel devicees lifts, and breaks away from corresponding ratchet, makes gear 6 be in the state of bidirectional overtaking.Eccentricity gear group transferring power, and driven shaft 8 angular velocity are reduced gradually.Forward C when gear 5 meshes to by A, to OD, the engagement radius of gyration reduces its engagement radius gradually, continues to make driven shaft 8 angular velocity to reduce gradually by OB.When gear 5 engagements forward D to by C, its the engagement radius by OD to OC, the engagement radius of gyration is from equaling gear 4 radiuses to being less than the development of gear 4 radiuses, gear 4 angular velocity are developed to the direction less than transmission shaft 7 from equaling driving shaft 7, the free wheel device of gear 4 is engaged, become by gear 4 and give axle 8 transmission of power.Simultaneously at the angular velocity of this interval internal gear 5 greater than transmission shaft 7 angular velocity, the free wheel device of gear 5 is formed surmounts, make no longer transferring power of gear 5 immediately.At this time come the ratchet of handsetting gear 5 free wheel devicees to lift, break away from corresponding ratchet, make gear 5 be in the state of bidirectional overtaking by driving lever.So final realize transmission of power continual by at a high speed to the low speed speed-change process., opposite by low speed with above-mentioned process to the high speed speed-change process.When the gear 5 of noncircular gear group is engaged to position between the C-D, make the free wheel device ratchet return and the ratchet interlock of noncircular gear 5 earlier, the gear 5 of noncircular gear group is engaged to the position beyond the C-D, the free wheel device of gear 5 engages transferring power automatically, and the free wheel device of gear 4 is separated automatically.When the gear 5 of noncircular gear group is engaged to position between the B-A, make the free wheel device ratchet return and the ratchet interlock of gear 6 earlier, the gear 5 of noncircular gear group is engaged to the position beyond the B-A, the free wheel device of gear 6 engages transferring power automatically, and the free wheel device of gear 5 is separated automatically.At this time can come the ratchet of handsetting gear 5 free wheel devicees to lift, break away from corresponding ratchet, make gear 5 be in the separated state of bidirectional overtaking by driving lever, so just realize again transmission of power continual by low speed to the high speed speed-change process.

The gear-shift transmission of embodiment two, a kind of two-stage uninterruptible power of the present invention (seeing Fig. 1,2,3,4,5), two transmission shafts 7,8 that the bearing setting of gear housing, gear housing is arranged, have two-stage driving gear set 1,3,4,6 between the transmission shaft 7,8 relatively, also be provided with the eccentricity gear group between the corresponding transmission shaft 7,8 of this two-stage driving gear set.Each gear 4,5,6 in two-stage driving gear set, the eccentricity gear group connects by roller type double rolling key clutch X, Y, Z with transmission shaft 7.The free wheel device of gear 4,5,6 is owing to shell 14, be rigidity with gear, transmission shaft 7 with star-wheel 13 and be connected.Swinging end 15 star-wheels of pusher dog are installed in the control chamber 11,12 of star-wheel dome, the position that corresponds to control chamber on slip ring 17 (structure and fork shift cover, gear shift circle similar) is provided with the control pin 19,18 that can insert or transfer to control chamber, the control pin is connected with slip ring 17 by spring, has constituted clutch operation.

Each free wheel device is the roller type double rolling key clutch, is used for transmission shaft 7,8 bi-directional power.If just unidirectional delivery power uses the parts of a direction good.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.

Eccentricity gear is identical with embodiment one with two grades driving gear radius relationship.When design control space 11,12 width and control pin 19,18 thickness and front end anti-retreating hook thereof, preferably will 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 operating mechanism of the free wheel device of gear 5 can be big with the operating mechanism of the free wheel device of gear 4,6 to the same, also can on the operating mechanism basis of the free wheel device of gear 4,6, increase a locking mechanism and release mechanism (see Fig. 3 .1,3.2), the control of the operating mechanism of being more convenient for like this.When transforming to top gear circular gear mechanism 3,6 transferring power, will utilize non-circular gear mechanism transition shelves rotational angular velocity to become big process transition gradually from circular gear mechanism 1,4 transferring power of bottom gear.The direction of transmission of power is to be transmitted to axle 8 by axle 7, sense of rotation be N to.At this moment the free wheel device of gear 4 is in jointing state, and the free wheel device of gear 5,6 all is in separated state.With the slip ring (referring to Fig. 5) of each operating mechanism of driving lever, the slip ring that makes gear 4 earlier moves towards the direction of part 13, and slip ring will make control pin 19 and 18 enter the control space 11 and 12 of free wheel device; The slip ring of gear 5,6 is successively all moved to the direction that deviates from part 13, and slip ring will make control pin 19 and 18 withdraw from the control space 11 and 12 of free wheel device.The radius of gear 6 is greater than the radius of gear 4, so at this time the rotating speed of gear 6 is lower than axle 7 rotating speeds, 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 4 is in jointing state, and the control pin 19 in gear 4 free wheel devicees 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, is called the state to be separated that is in.The free wheel device of gear 5 is in separated state, and the free wheel device control mechanism of gear 5 will be controlled the control space 11,12 that pin 19 and 18 withdraws from free wheel device.If at this time gear 5 rotates at D with gear 2 engagements and arrives the interval in addition of C, velocity ratio is less than the velocity ratio of bottom gear, the engagement radius of gear 5 is greater than the radius of gear 4, so at this time the rotating speed of gear 5 (angular velocity) is to be lower than axle 7 rotating speeds (angular velocity), so control pin 18 temporarily move back not between clearancen 12 just spring be compressed to await a favorable opportunity and withdraw from automatically, 19 of control pins withdraw from control space 11; 18 of the interval back control of this section pins that have only gear 5 and gear 2 to be engaged to D-C withdraw from control space 12, and the free wheel device of gear 5 just is in the working state for the treatment of combination, is being engaged to the free wheel device combination of back, C place, and the free wheel device of gear 4 is separated.If at this time gear 5 rotates with gear 2 engagements, forward this section interval of C to by D, because the engagement radius of gear 5 is less than the radius of gear 4, so at this time the rotating speed of gear 5 (angular velocity) is to be higher than axle 7 rotating speeds (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, are called to be in and treat bonding state being in such working state; When gear 5 and gear 2 engagements forward this section interval that is forwarded to A by C to, the engagement radius of gear 5 changes from small to big gradually, angular velocity also is less than axle 7 angular velocity gradually from large to small and at the very start, at this moment the automatic combination of the free wheel device of gear 5, take over the power (task) of transferring power from gear 4, and make the free wheel device of gear 4 surmount separation automatically.The control pin 18 of the operating mechanism of gear 4 free wheel devicees enters space 12 automatically under the effect of spring simultaneously, and the free wheel device of gear 4 is keeping separated state.When gear 5 and gear 2 engagements are rotated, forward this section interval of B to by A, the engagement radius of gear 5 is the radiuses greater than gear 6, at this time the rotating speed of gear 6 is higher than axle 7 rotating speeds, so the control pin 18 of the operating mechanism of gear 6 free wheel devicees spring do with under withdraw from space 12 automatically, the working state of the free wheel device of gear 6 is in treats bonding state.The operating mechanism return of gear 5 moves the slip ring of gear 5 again towards the direction of part 13 simultaneously, make control pin 19 enter space 11, control pin 18 does not temporarily enter space 12, just spring is compressed to await a favorable opportunity and enters automatically, and the working state of the free wheel device of gear 5 is called the state to be separated that is at this moment.When gear 5 and gear 2 engagements are rotated, forward this section interval of D to by B, the engagement radius of gear 5 is less than the radius of gear 6 at the beginning, and at this time the rotating speed of gear 6 is less than axle 7 rotating speeds, and gear 6 free wheel devicees are in jointing state and make the free wheel device of gear 5 surmount separation automatically.At this moment gear 6 is just taken over the power of transferring power fully from gear 5.Forward this section interval of D to by B, the engagement radius of gear 5 is the radiuses less than gear 6, at this time the rotating speed of gear 5 is to be higher than axle 7 rotating speeds, the control that makes pusher dog is to space 11 swings, and control pin 18 enters space 12 automatically, makes the free wheel device of gear 5 keep separated state under the effect of spring.Circular gear mechanism 1,4 transferring power from bottom gear transform to top gear circular gear mechanism 3,6 transferring power like this, have just finished under the situation 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.As long as adopt friction overdrive clutch and above-mentioned operating mechanism, the working procedure of operating mechanism and free wheel device and gear shift all is the same below.As long as operate the free wheel device operating mechanism of initial retaining, transition shelves, purpose shelves respectively according to priority, and make transition shelves operating mechanism return, just can realize the gear shift of uninterruptible power.More than the controlling of operating mechanism of each free wheel device, also available linking mechanism (referring to Figure 18-22,26-30) is once finished, and behind the free wheel device operating mechanism of the noncircular gear that just links, also will make its return.Adopt linking mechanism, the operating mechanism of non-circular gear mechanism free wheel device preferably to adopt as Fig. 3 .1,3.2 structure or as Figure 16,17 structure.

As Fig. 3 .1,3.2 structure, the operating mechanism of non-circular gear mechanism free wheel device is that the slip ring at said gear 5 operating mechanisms 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 5 free wheel device pusher dogs with the control pin of slip ring, band spring.Wedge type over running clutch has increased locking mechanism and release mechanism also is the same, and the control mechanism shown in Fig. 3 .1,3.2 (comprising locking mechanism and release mechanism) also is applicable to the control of the pusher dog of the Wedge type over running clutch of being with pusher dog.Pusher dog and this control mechanism have formed and have been in state to be separated when making free wheel device be in jointing state, and promptly constitute the operating mechanism of stablizing separated state after entering separated state.Can also be provided with connection double-action mechanism (referring to Figure 18-22 or Figure 26-30) like this between the slip ring of each free wheel device operating mechanism, under the effect of linking mechanism, make each control pin insert or withdraw from control chamber in real time, and controlling each roller-type overrunning clutch maintenance separated state or the state of resuming work in real time.

When changing to 1,4 transferring power from circular gear mechanism 3,6 transferring power of top gear by bottom gear circular gear mechanism, mainly utilize eccentricity gear mechanism transition shelves rotational angular velocity gradually the process of diminishing come transition.The free wheel device of gear 6 is in jointing state, and in relative rotation the axle 7,8 between transferring power.The free wheel device of gear 5,4 is in separated state.Stir the linking mechanism of each operating mechanism, the driving lever of linking mechanism makes the slip ring of top gear operating mechanism (referring to Fig. 5) move earlier, and make corresponding control pin will insert control chamber, successively the slip ring of transition shelves, bottom gear operating mechanism (referring to Fig. 5) is moved again, and successively will make corresponding separately control pin will insert separately control chamber.The slip ring that the driving lever of linking mechanism is stirred the transition shelves moves the back slip ring will return, but because as the lever of Fig. 3 .1,3.2 locking mechanisms of representing be stuck in deck, slip ring is remained on leave the position of part 13.To surmount the state probability bigger because gear 5 free wheel devicees are 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 5 and gear 2 engagements, 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 5 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 slip ring of gear 6 free wheel devicees (referring to Fig. 5), control sell the control chamber that inserts free wheel device.Then when gear 5 and gear 2 engagement rotations, 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 6 radiuses, the free wheel device of gear 5 is engaged, by eccentricity gear mechanism transferring power, the while reaches with regard to the free wheel device that makes gear 6 and surmounts state, and makes the control pin insertion of gear 6 free wheel devicees surmount the control chamber space 11 or 12 that motion moves out.Such two control pins all insert control chamber space 11 and 12 respectively, make gear 6 keep the state of bidirectional overtaking.Soon, driven shaft 8 angular velocity are reduced gradually after the eccentricity gear mechanism transferring power.The control pin of the operating mechanism of gear 5 all withdraws from control chamber simultaneously, all be retracted into the groove that control is sold as the locking mechanism of Fig. 3 .1,3.2 expressions and the ball of release mechanism, lever can rotate to lift and leave deck, it is close that slip ring is begun to part 13 returns, and two one of control pins enter control chamber, another will enter control chamber and be stuck.When gear 5 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 4 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 5 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 4 radiuses, make the free wheel device of gear 4 engage transferring power at the very start, the transferring power of gear 4 makes gear 5 formation surmount again conversely, the former control pin that does not enter control chamber of gear 5 operating mechanisms just inserts the control chamber of gear 5 free wheel devicees, makes gear 5 keep the separated state of bidirectional overtaking, finally realizes the continual speed-change process of transmission of power.

The gear-shift transmission of embodiment three, a kind of four shelves uninterruptible powers (is seen Figure 36, and referring to Fig. 8), there is the bearing of gear housing, gear housing disposing input shaft 87 and output shaft 88, these two axles that relatively rotate transferring power have four shelves circular gear mechanisms that just changeing, and also dispose an elliptic gear mechanism that is just changeing side by side in the middle of every two grades of adjacent circular gear mechanisms.The bearing of gear housing, input shaft, output shaft, four pairs of circular gears, three pairs of noncircular gears have constituted the non-circular gear mechanism of four shelves circular gear mechanisms and three transition shelves respectively, and have constituted the level Four speed changer with gear housing.This gear-shift transmission is a unidirectional delivery power, by axle 87 to axle 88 transferring power.From one grade of circular gear mechanism from low to high, constituted with four shelves that turn to output to fourth gear circular gear mechanism transport velocity.One grade of circular gear mechanism, second gear circular gear mechanism are equipped with the elliptic gear mechanism that is provided with, and initiatively the minor axis radius of elliptic gear is less than the radius of one grade of driving gear, and the major diameter radius of elliptic gear is greater than the radius of the driving gear of second gear.Second gear circular gear mechanism, third gear circular gear mechanism are equipped with the elliptic gear mechanism that is provided with, and initiatively the minor axis radius of elliptic gear is less than the radius of second gear driving gear, and initiatively the major diameter radius of elliptic gear is greater than the radius of the driving gear of third gear.Third gear circular gear mechanism, fourth gear circular gear mechanism are equipped with the elliptic gear mechanism that is provided with, and initiatively the minor axis radius of elliptic gear is less than the radius of third speed drive gear, and initiatively the major diameter radius of elliptic gear is greater than the radius of the driving gear of fourth gear.Three driving gears (referring to Fig. 8) of elliptic gear all have two E of place, the G that equates with bottom gear driving gear radius, two H of place, the I that equate with top gear driving gear radius.Between driving gear in four circular gear mechanisms, three the elliptic gear mechanisms and the input shaft 87 free wheel device (referring to Fig. 3,4,5,6,7) is set respectively.The free wheel device of seven driving gears all by the shell 14,36 that is fixedly connected with gear, is fabricated to the star-wheel 13,34 of one with axle, and the roller 16,35 that is arranged between star-wheel and the shell constitutes.Also have pusher dog 15,33 between star-wheel and the shell, the pawl of pusher dog is distributed between each roller, and pusher dog contacts with circle in the shell.The control end of pusher dog inserts the control chamber 11,12 of star-wheel dome, and star-wheel also is with slip ring 17 in axial sliding, and slip ring is being provided with the control pin corresponding with control chamber 18,19 by spring.The back control end that another kind of mode is a pusher dog has control chamber 37,38, star-wheel only also is set with slip ring 31 in axial sliding, and slip ring passes star-wheel by pin 30, Control Shaft 32, hoodle 25,26 and spring 24,27 and controlling the control pin corresponding with control chamber 23,28.Slip ring, pin, Control Shaft, hoodle, spring, control pin, control chamber, pusher dog have constituted operating mechanism.

When changing to adjacent top gear circular gear mechanism by shelves from first grade of circular gear mechanism, the operating mechanism of one grade of circular gear mechanism of control earlier, the operating mechanism of controlling corresponding elliptic gear again makes the free wheel device of elliptic gear recover state to be joined, controls the operating mechanism of second gear circular gear mechanism at last.The driving gear of corresponding elliptic gear mechanism meshes to the major diameter place from minor axis, after the free wheel device of elliptic gear engages, corresponding elliptic gear mechanism begins transferring power, and bottom gear driving gear free wheel device is transformed into from jointing state surmount state.Elliptic gear mechanism makes the angular velocity of transferring power become big gradually.Angular velocity becomes the big later stage gradually makes the free wheel device of second gear driving gear return to state to be joined from separated state, the angular velocity that elliptic gear mechanism changes become gradually begin greatly again to reduce after, the free wheel device of second gear driving gear will engage automatically, carry out the transition to second gear circular gear mechanism transferring power, initiatively the free wheel device of elliptic gear also is in separated state immediately simultaneously, and its operating mechanism keeps this separated state.So just realized that the uninterruptible power transmission is by the conversion of bottom gear to top gear.When will be from the top gear to the bottom gear, will utilize corresponding elliptic gear mechanism engagement rotational angular from large to small process gradually.Earlier, make the free wheel device of top gear be in state to be separated, control the operating mechanism of corresponding elliptic gear mechanism again, the free wheel device of elliptic gear is in treats bonding state by the operating mechanism of control top gear.After the engagement of active elliptic gear is tending towards the H or I place of major diameter radius, initiatively the free wheel device of elliptic gear converts jointing state to by separated state, the free wheel device of top gear driving gear is in surmounts state, and make it keep surmounting separated state by the control operating mechanism.The free wheel device of bottom gear driving gear is in treats bonding state, initiatively elliptic gear is engaged to the E or the G place of minor axis radius, be in jointing state with regard to the free wheel device that makes the bottom gear driving gear, and the free wheel device of elliptic gear be in surmount state.By the free wheel device operating mechanism of control active elliptic gear, making initiatively, the free wheel device of elliptic gear keeps separated state.So just realized that the uninterruptible power transmission is by the conversion of adjacent two grades arbitrarily top gear to the bottom gear uninterruptible power.In speed-change process, if each operating mechanism has linking mechanism, can stir fork shift circle that linking mechanism makes elliptic gear free wheel device initiatively, connect pin, pull bar moves, and makes hoodle enter the respective slot of pull bar, under the effect of spring 22, make the control pin will eject control chamber.Surmount state if free wheel device is in, then control pin ejects control chamber immediately, does not surmount state if free wheel device is not in, then wait to be in surmount state after the control pin eject control chamber immediately.The control pin of then corresponding adjacent two grades of circular gear mechanism free wheel devicees also will be along with inserting and withdraw from the control corresponding chamber.The control pin of the initial shelves driving gear free wheel device of former transferring power that Here it is also will insert control chamber; Also be that linking mechanism successively makes the fork shift circle according to the order of sequence, even pin, pull bar move, and make hoodle leave the groove of pull bar, upwards lift, under the effect of spring 24 or 27, make the control pin will insert control chamber; Surmount state if free wheel device is in, then control pin inserts control chamber immediately and makes its maintenance surmount state; Do not surmount state if free wheel device is not in, then wait to be in and surmount that the control pin inserts control chamber immediately behind the state, make its maintenance surmount state.Corresponding want speed change to the control pin of purpose shelves driving gear free wheel device also eject control chamber at last; Also be that linking mechanism successively makes the fork shift circle of this driving gear free wheel device according to the order of sequence, even pin, pull bar move, the respective slot that makes hoodle enter pull bar under the effect of spring 22, makes the control pin will eject control chamber; Surmount state if free wheel device is in, then the control pin ejects control chamber immediately; Do not surmount state if free wheel device is not in, then wait to be in and surmount that the control pin ejects control chamber immediately behind the state.So just can after active elliptic gear transferring power, the former driving gear free wheel device that is in jointing state be become immediately surmount state, and can keep surmounting state; Can change the driven shaft angular velocity later stage in active elliptic gear transferring power, make the former purpose shelves driving gear free wheel device that surmounts state that is in become jointing state, reach in time reposefully speed change to corresponding circular gear mechanism, and keeping transmitting corresponding power always.

The gear-shift transmission of Figure 37,38,39 represented four shelves uninterruptible powers and above-mentioned structure are basic identical, just non-circular gear mechanism constitutes at the different axle of coaxial line respectively with circular gear mechanism, connect by controlled clutch between the axle of coaxial line, and from the input shaft to the output shaft, contain the reverse gear circular gear mechanism of backward rotation output.Wherein Figure 39 represents the gear-shift transmission of four shelves uninterruptible powers, one of them grade is the shelves of directly exporting, also can regard the shelves of the circular gear mechanism formation of 1:1 as, in the circular gear mechanism of this 1:1, be connected by free wheel device between the rotating shaft of coaxial line and the rotating shaft, make this Transmitted chains contain free wheel device.

Two grades of speed change gears of embodiment four, the mutual transferring power of a kind of diaxon (moment of torsion is positive and negative alternately) are seen Fig. 9.

This device has pedestal, base via shaft to hold two rotating shaft I, II of setting, has two pairs of normal engagement circular gears in relative rotation between the rotating shaft and has constituted two grades of circular gear mechanisms.Rotating shaft I, the II of these two grades of circular gear mechanisms also is provided with a pair of noncircular gear 45,46 and constituted non-circular gear mechanism.Two pairs of circular gears of two grades, a pair of noncircular gear, respectively have a gear 41,45,43 to connect by double rolling key clutch (seeing Figure 23,24,25,42) with rotating shaft I respectively, two-way roller-type overrunning clutch also has operating mechanism (seeing Fig. 3,4,5).Pusher dog and the control mechanism thereof selected for use of the free wheel device operating mechanism of non-circular gear mechanism wherein seen Fig. 3 .1,3.2 structure.The free wheel device operating mechanism of non-circular gear mechanism is to be provided with locking mechanism and circumferentially to swing the release mechanism that changes interlock with pusher dog on the basis of circular gear mechanism double rolling key clutch operating mechanism.These locking mechanisms and release mechanism are at slip ring lever to be set, and an end of lever is sold the corresponding ball that is respectively arranged with between the back segments with two controls, is provided with jump ring between the other end of lever and the spider gear shaft.Like this can be after stirring the control end that slip ring leaves pusher dog, lever is stuck between jump ring and the ball, make the slip ring can not return, after guaranteeing that non-garden gear mechanism free wheel device engages, all withdraw from from control chamber at two control pins, ball all pushes the position-limited lever groove, lever is rotated cross jump ring, make the slip ring return, realize making when surmounting free wheel device to keep separated state again.Such operating mechanism is the same with existing clutch operation, contact with the joint element roller of double rolling key clutch by pusher dog, operation control joint element roller, make double rolling key clutch become two-way separated state, still recover the automatic separation of its a certain direction or the working state of separating automatically.At the non-circular gear mechanism of adjacent two grades of circular gear mechanisms and corresponding configuration, the maximum transmission ratio of non-circular gear mechanism is greater than the velocity ratio of bottom gear circular gear mechanism, and its fastest ratio is less than top gear circular gear transmission ratio.Have linking mechanism and selector gear (referring to Fig. 8,19,20,21,22,26,27,28,29,30) between the operating mechanism of each double rolling key clutch.

Its working principle is as follows:

As shown in Figure 9, the I axle is a driving shaft, and the II axle is an output shaft.Gear 41,42 is an adjacent bottom gear circular gear mechanism, and velocity ratio is i ₁₂Gear 43,44 is an adjacent top gear circular gear mechanism, and velocity ratio is i ₃₄Gear 45,46 can continuous rotating non-circular gear mechanism for what realize gear shift, its end view such as Figure 10.The non-circular gear mechanism velocity ratio is i ₅₆At i _56minAnd i _56maxBetween the consecutive periods variation, and i _56minLess than i ₃₄, and i _56maxGreater than i ₁₂Gear 41,43,45 can link by double rolling key clutch and the driving shaft I by selector gear control.The double rolling key clutch of present embodiment is referring to Figure 23,24,25, and present embodiment is hereinafter to be referred as clutch.

The speed-raising process:

At first by gear 41,42 transmissions, promptly only the clutch on the gear 41 is in the stable engagement state, and all the other all are in stable separated state, are in bottom gear smooth running state.

After the conversion MLP successively touched clutch operation on the gear 41,45,43, the clutch on the gear 41 was in state to be separated, was the gear ratio transmission because gear 45,46 realizes, its velocity ratio i ₅₆Experience equal and the trend less than velocity ratio i ₁₂Relatively rotating direction and will taking place once to change of process I axle and gear 45 just makes the free wheel device of gear 45 become the state to be joined that is in by stablizing separated state; Velocity ratio i ₅₆Experience less than, equal to go to velocity ratio i greater than gear 41,42 ₁₂Process, the direction that relatively rotates of I axle and gear 45 takes place again once to change, clutch on the gear 45 can experience and enter jointing state automatically and be state to be separated, and the clutch of gear 41 is separated automatically, takes over gear 41,42 by 45,46 gears and realizes the transmission of I axles to the II axle.Take over behind gear 41,42 transfer motion powers velocity ratio to greater than i by 45,46 gears ₁₂Change, make the free wheel device of gear 41 keep separated state.What gear 45,46 was then realized is the gear ratio transmission, along with the carrying out of transmission, and its velocity ratio i ₅₆Experience again less than, equal to go to velocity ratio i greater than gear 43,44 ₃₄Process, the relatively rotating direction and will take place once to change of I axle and gear 43, the free wheel device separated state of gear 43 becomes the state to be joined that is in; Velocity ratio i ₅₆Then experience greater than, equal to go to the velocity ratio i that is less than gear 43,44 ₃₄Process, the direction that relatively rotates of I axle and gear 43 takes place again once to change, clutch on the gear 43 can experience and enter jointing state automatically, make the automatic separation of gear 45 free wheel devicees simultaneously and under the operating mechanism effect, keep separated state, also just make gear 43 form the stable engagement state, take over gear 45,46 by 43,44 gears and realize of the transmission of I axle to the II axle.

The reduction of speed process:

Realize the transmission of I axles to the II axle by gear 43,44 during beginning, promptly only the clutch on 43 gears is in the stable engagement state of work, and all the other all are in separated state, and system is in top gear, and is in the smooth running state.

After the conversion MLP sends shift-down action, make the clutch on the gear 43 be in state to be separated, and the clutch on the gear 41,45 successively is in state to be joined; When the relation that relatively rotates of I axle and II axle did not change, the clutch on the gear 43 can not separate, and similarly, the clutch on the gear 41,45 can successively not enter jointing state yet.

Because what gear 45,46 was realized is the gear ratio transmission, along with the carrying out of transmission, its velocity ratio i ₅₆Can experience equal to go to the velocity ratio i that is greater than gear 43,44 ₃₄Process, the relatively rotating direction and will take place once to change of I axle and gear 45.In this process, clutch on the gear 45 can experience and enter jointing state automatically and directly change state to be separated over to, and make the clutch of gear 43 surmount separation automatically, take over gear 43,44 by 45,46 gears and realize the transmission of I axle to the II axle, the operating mechanism of gear 43 makes its free wheel device keep separated state.This is because after gear 45,46 is taken over transmission process, the rotating speed of II axle reduces gradually, from the drive connection angle analysis, gear 44 is fixedly connected with the II axle, and the rotating speed of gear 43 is higher than the rotating speed of I axle, and gear 43 becomes follower by driving gear, clutch on it is through withdrawing from jointing state automatically, and then insert control chamber by the control pin of operating mechanism, and make clutch change separated state over to, surrender the transmission control.

Along with proceeding of transmission, the velocity ratio i of gear 45,46 ₅₆Can experience again greater than, equal to go to the velocity ratio i that is less than gear 41,42 ₁₂Process, the relatively rotating direction and also will take place once to change of I axle and gear 1.In this process, the clutch on the gear 41 can experience and enter jointing state automatically, takes over 45,46 gears by 41,42 gears and realizes the transmission of I axle to the II axle.

After gear 41,42 is taken over transmission process, the rotating speed of II axle will maintain a new level, and the clutch of gear 45 separates through withdrawing from jointing state automatically, enter control chamber at operating mechanism and release mechanism drive control pin, keep separated state, surrendering the transmission control.

Speed-change process between adjacent two grades more than has been discussed.To the working method of multi-speed transmission similarly, so do not add narration.At the gear ratio allocative decision of two kinds of automotive transmissions, the circular gear mechanism of four gear gearboxes that provide and the multiple matching scheme of noncircular gear transmission thereof are seen Figure 36,37,38,39.

Embodiment five, a kind of automobile are with the gear-shift transmission (seeing Figure 11) of uninterruptible power, gear housing is arranged, gear housing is being provided with two axle I, II at least by bearing, two axles also can be provided with reverse gear circular gear and reverse gear shaft and reverse gear carrier gear by three pairs of normal circular gear and two pairs of noncircular gear transmission joint that mesh.The circular gear of three shelves and the non-circular gear mechanism of two transition shelves have so just been constituted respectively, and contain the circular gear mechanism of three forward gearss and the circular gear mechanism of two transition shelves from I to two II, every adjacent two grades of circular gear mechanisms of these three shelves circular gear mechanisms also corresponding the advance non-circular gear mechanism of transition shelves of conduct.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 etc. constitute.In the non-circular gear mechanism of adjacent two grades of circular gear mechanisms configuration, the least radius of driving gear 5a ', 5b ' is respectively less than the radius of corresponding bottom gear driving gear 4a ', 4b ', and its maximum radius is respectively greater than the radius of corresponding top gear driving gear 4b ', 4d '.In the non-circular gear mechanism of adjacent two grades of circular gear mechanisms and configuration, the least radius of driven gear 5a, 5b is less than the radius of top gear driven gear, and maximum radius is greater than the radius of bottom gear driven gear.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 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 → non-circular gear mechanism free wheel device and is in state to be joined → purpose shelves free wheel device and is in state to be joined.

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

Figure 11 is the transmission system sketch of speed changer.One is input shaft, and two is output shaft.Gear 4a-4a ' is one grade of circular gear mechanism, and velocity ratio is i ₁Gear 4b-4b ' is a second gear circular gear mechanism, and velocity ratio is i ₂(be i ₁＞i ₂); Gear 4c-4c ' is a third gear circular gear mechanism, and velocity ratio is i ₃(be i ₁＞i ₂＞i ₃).The circular gear mechanism of these three shelves all is with the gear that turns to output.Gear 5a-5a ', 5b-5b ' be used for realizing gear shift, can continuous rotating non-circular gear mechanism, also be that circular gear mechanism with above-mentioned three shelves is with turning to output.Velocity ratio 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 ' are fixedly connected with input shaft I, and gear 4a, 4b, 4c, 5a, 5b are by being linked by the free wheel device and the output shaft II of 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 13, the figure middle gear is simplified, the gearshift mechanism general structure mainly comprises gear shift control wheel 57 and catch means (not shown) thereof, shift shaft 58, driving lever and driving lever spring (in the driving lever rotating shaft, not shown), the circular gear clutch pack of each grade (seeing Figure 14, Figure 15), can continuous rotating noncircular gear clutch pack (seeing Figure 16, Figure 17), line shaft 56 (output shaft) etc.4a, 4b, 4c are respectively one, two in addition, the circular gear of third gear, and 5a is a transition gear between a second gear, and 5b is a transition gear between two third gear.Transition gear 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 Figure 11, among Figure 13 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 shift lever relevant position protruding structure is being arranged, stirring driving lever in order to machine in due course.When driving lever (3a, 3b, 3c, 3d, 3e) when being struck, drive slip ring (fork shift ring) action on the respective clutch, recover 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 driving lever of protruding partial action on the shift shaft, and all under the effect of driving lever 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) the supporting controllable overrunning clutch group (hereinafter to be referred as the conventional wheel clutch pack) of each grade circular gear

The conventional wheel clutch pack 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, and Figure 14 is an assembly structure, and Figure 15 is each part disassembled form.

The line shaft 56 of output 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 constituting the inboard, is furnished with roller and alternate pawl between line shaft and the star wheel structure, the ring that the outer end of pawl becomes to be connected as a single entity, 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 fork on the pusher dog outer rim, can realize transmission of power from the circular gear to the line shaft to reach solenoidoperated cluthes.

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

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

The noncircular gear clutch pack is made up of critical pieces such as line shaft 56 (not drawing among Figure 16,17), noncircular gear 71, roller pusher dog control unit 72, feather key 73, slip ring 74, limit shelves 75, and Figure 16 is an assembling condition, and Figure 17 is its each part disassembled form.

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.Simultaneously between pusher dog and line shaft by contacting, rotate trend in the same way with the friction mode maintenance.Can whether the control pin by the slip ring end face be to protruding the control at fork position on the pusher dog outer rim, in running order to reach solenoidoperated cluthes, transmission of power that from the circular gear to the line shaft.

One flume structure 76 is arranged on the pusher dog outer rim in addition, link with the feather key 72 of gear wheel hub.After driving slip ring and leave pusher dog by linking mechanism and driving lever, when pusher dog is in when making gear and line shaft separated state, feather key is in a high position to radially protruding, limit the close of slip ring and pusher dog; And be in when making gear and line shaft jointing state when pusher dog, 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.Slip ring and control pin and pusher dog near after, when making gear and line shaft realize automatic separated state, the space that the control pin inserts the 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 feather key and flume structure 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.

Slip ring sleeve is on the periphery of circular gear wheel hub, and circular gear is done and 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 circumferential swing of the relative star wheel structure of control pusher dog, the position of pusher dog is limited.The flume structure of pusher dog, feather key, limit shelves, driving lever, slip ring and buckle projection have constituted the control mechanism of noncircular gear free wheel device operating mechanism pusher dog.Driving lever has return spring 77 in the Transmitted chains of driving lever, slip ring and buckle projection.

C, gearshift procedure explanation

This speed control system of car at first is in one grade of work, and line shaft 56 is in minimum operating speed (seeing Figure 18).At this moment, the driving lever 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 driving levers are in and are subjected to driving lever spring state of a control, and its corresponding slip ring is controlled corresponding pusher dog and made each clutch separation, so all the other clutches are in stable separated state.

Shift shaft is put by a gear in the rotation process that turns to the second gear position, and at first driving lever 3a loses the control of shift shaft, under the effect of driving lever spring, rotates and the slip ring on the gear 4a wheel hub is pressed to pusher dog.Because the relative movement of gear 4a free wheel device principal and subordinate moving part 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 gear 5a and control pin that the trend of pulling out be arranged to driving lever 3d effect.In case the control pin is transferred to transition gear 5a then can be in state to be joined, the condition achievement will engage automatically takes over gear 4a realization transmission of power function.(seeing Figure 19)

Because what transition gear was 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, friction torque 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 gear 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.

Slip ring is drawn out, and after transition gear was taken over control to line shaft, 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 noncircular gear.

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

(seeing Figure 20) took turns the positioning device locking by gear shift when shift shaft was rotated further to the second gear working position, and this moment, driving lever 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 noncircular gear 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 driving lever spring action, pusher dog is in unrestricted state (being state to be joined) immediately, when the speed of noncircular gear 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 4b to be controlled; In this simultaneously, the clutch of 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 21,22) 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 gear 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 12.

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 free wheel device.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 double rolling key clutch (seeing Figure 23,24,25), this speed change gear can be used as the speed variator system of movable machinery (as automobile etc.).To utilizing engine braking and realizing that the continuous increase and decrease grade (as under the heavy-duty vehicle during long abrupt slope) of uninterrupted braking force all can satisfy job requirement.

The large-size ball mill gear-shift transmission of embodiment six, a kind of two grades of uninterruptible powers of the present invention (seeing Fig. 1,31,32,33), 7,8, two axles of two axles that are provided with by the bearing 9 of pedestal, pedestal are being provided with constant mesh gear and are constituting.Power is delivered to output shaft 8 from input shaft 7.The cylindrical gears 1,3,4,6 by two pairs of different drive ratios has constituted two grades of circular gear mechanisms between the axle 7,8 in relative rotation.The size of these gears is all bigger, and radius is all more than one meter.The axle 7,8 at these two grades of circular gear mechanism places also is provided with elliptic gear 2,5, has constituted the elliptic gear mechanism of transition shelves.Driving gear 4,5,6 in two grades of circular gear mechanisms, the elliptic gear mechanism connects by ratchet type overrunning clutch (seeing Figure 34,35) with rotating shaft 7.About 10 rev/mins of the n of rotating shaft 7 to rotating speed.The ratchet of the ratchet type overrunning clutch of driving gear 5,6 has the driving lever of stirring ratchet, has constituted the ratchet-type controlled clutch.The semi major axis of elliptic gear 5 equals several millimeters of the radius of gear 6 or positive minus tolerances, and the short radius of elliptic gear 5 equals the radius or positive several millimeters of the negative errors (referring to Figure 31,32,33) of gear 4.The ratchet of the free wheel device of gear 5,6 has been dialled by driving lever, breaks away from ratchet, makes free wheel device be in separated state, and the free wheel device of gear 4 is in jointing state.Need be when the high speed speed change, when active elliptic gear 5 minor radius were in engagement, the free wheel device ratchet return of handsetting gear 5 contacted with ratchet.Since gear 5 at this moment rotational angular velocity less than the angular velocity of rotating shaft 7, so just transit directly to and be in jointing state from surmounting state.And then just by gear 5 and gear 2 transfer motion powers.The engagement of noncircular gear 5 forwards the position of maximum radius to from least radius, and gear 5 makes the rotating speed of driven shaft improve.At this moment by the ratchet return of driving lever handsetting gear 6 free wheel devicees, contact with corresponding ratchet, gear 6 will carry out the transition to jointing state, becomes by gear 6 transferring power.The transferring power of gear 6 makes the angular velocity of gear 5 greater than rotating shaft 7 angular velocity again, and the free wheel device formation of gear 5 is surmounted, and makes no longer transferring power of gear 5 immediately.If many grades with regard to one grade one grade to the top gear speed change, the work that keeps high-speed smooth in the most at a high speed shelves stable operation at last.Shut down the work back.Begin one grade one grade to the top gear speed change from lowest gear again when needing start work.The driving lever of ratchet can drive (seeing Figure 34,35) by cylinder or hydraulic cylinder mechanism, also can be driven by existing mechanical clutch operating mechanism, and driving lever is as the release lever of mechanical clutch operating mechanism.

Embodiment seven, a kind of automobile gear-shift transmission of uninterruptible power, there is the bearing of gear housing, gear housing that two rotating shaft I, II are being set, two rotating shafts connect the different shelves of formation circular gear mechanism by the circular gear of engagement in pairs respectively, connect the non-circular gear mechanism that constitutes different transition shelves by the noncircular gear that meshes in pairs respectively.Rotating shaft in relative rotation contains the circular gear mechanism of three shelves, and the axle in relative rotation of every adjacent two grades of circular gear mechanisms also contains a non-circular gear mechanism.Driving gear and active rotating shaft in circular gear mechanism, the non-circular gear mechanism are fixedly connected, driven gear 4a, 4b in circular gear mechanism, the non-circular gear mechanism, 4d, 5a, 5b connect by roller-type overrunning clutch (seeing Figure 23,24,25) with driven spindle II, have formed the gear mechanism of combination in real time with five parallel arranged of separating between two rotating shaft I, II.Free wheel device also has the operating mechanism of translation driving lever, slip ring, control pin, pusher dog formation.In the non-circular gear mechanism of adjacent two grades of circular gear mechanisms and corresponding configuration, the least radius of driving gear 5a ', 5b ' is less than the radius of bottom gear driving gear, and maximum radius is greater than the radius of top gear driving gear.In the non-circular gear mechanism of adjacent two grades of gear mechanisms configuration, the least radius of driven gear 5a, 5b is less than the radius of top gear driven gear, and maximum radius is greater than the radius of bottom gear driven gear.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 control pusher dog swing position is the control mechanism that pusher dog is in or is not in restriction roller working state, sees Fig. 3,4,5.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 after entering separated state, sees Fig. 3 .1,3.2; 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 on the operating mechanism basis of circular gear, controls 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 release mechanism that links with the pusher dog swing position.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 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 → non-circular gear mechanism 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 26 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 driving lever 73 and parallel slide-bar 74 formations; The engagement sleeve group 75 that also comprises each grade can continuous rotating noncircular gear (transition 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 gear between a second gear (transition gear be can the another kind of address of continuous rotating noncircular gear).2b is a transition gear between two third gear.Among the figure each gear all with input shaft on fixing respective gears keep the normal engaged relation (among Fig. 3 input shaft and on gear all do not draw in the drawings).

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 driving lever 73 move or return along parallel slide-bar 74, drive the 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 driving lever 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 driving lever of pull bar and the effect of slip taper pin, and all under the effect of driving lever 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 driving lever 73, parallel slide-bar 74 and slip ring have constituted linking mechanism.

Linking mechanism carries out according to Figure 26-Figure 30 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.

Embodiment eight, a kind of input and output shaft are with parallel four the shelves gear-shift transmissions (seeing Figure 45) that connecting the uninterruptible power of jack shaft of identical drive connection, there is the bearing of gear housing, gear housing that five rotating shaft I, II, III, IV, V are being set, contains non-circular gear mechanism from input shaft I to output shaft II side by side with four forward gears circular gear mechanisms that turn to output and corresponding three transition shelves; Non-circular gear mechanism of the corresponding configuration of every two grades of adjacent circular gear mechanisms, the velocity ratio of bottom gear is less than the maximum transmission ratio of the non-circular gear mechanism of correspondence relatively in adjacent two grades of circular gear mechanisms, and the velocity ratio of relative top gear is greater than the fastest ratio of the non-circular gear mechanism of correspondence in adjacent two grades of circular gear mechanisms; The idler and the active driven gear that also pass through axle VI between input shaft, the output shaft constitute reverse gear circular gear mechanism.Be provided with castellated controlled clutch between rotating shaft II and rotating shaft V and the reverse gear.The gear mechanism of forward gears and reverse gear just can connect with output shaft respectively by controlled clutch like this.Driving gear in four circular gear mechanisms, three non-circular gear mechanisms respectively with active rotating shaft I, III, be fixedly connected, driven gear in circular gear mechanism, the non-circular gear mechanism connects by roller-type overrunning clutch (referring to Figure 23,24,25) with driven spindle V, IV respectively, has formed seven groups of normal meshed gears mechanisms between principal and subordinate's rotating shaft.Connect by a pair of gear drive that meshes between two active rotating shaft I, the III, two driven spindle V, IV connect identical gear drive by another that meshes, and two pairs of gear drives make two rotating shafts that be arranged in parallel form identical drive connection.Rotating shaft I, the V of transferring power concentrate four circular gear mechanisms are being set relatively, and rotating shaft III, the IV of transferring power concentrate three non-circular gear mechanisms are being set relatively.So just can form with the gear drive that turns to output disalignment distance.Can connect by controlled clutch between the driving shaft, also can connect (seeing Figure 46) between the driven shaft, just can when not needing non-circular gear mechanism work, separate controlled clutch by controlled clutch.

Three shelves uninterruptible power gear-shift transmissions (seeing Figure 47,48,49,50,51) that embodiment nine, a kind of input shaft are connected with two non-circular gear mechanisms respectively by controlled clutch, have the bearing of gear housing, gear housing that many axles that comprise input shaft, output shaft are being set, these axles have constituted three shelves circular gear mechanisms and two transition shelves non-circular gear mechanisms by the pitch wheel group is set from the input shaft to the output shaft.Every adjacent two grades of circular gear mechanisms corresponding configuration one transition shelves non-circular gear mechanism.Three shelves circular gear mechanisms, two non-circular gear mechanisms, each gear mechanism all have a gear to connect by roller-type overrunning clutch or Wedge type over running clutch (referring to Figure 23,24,25,42,43,44) with rotating shaft.Free wheel device has operating mechanism (referring to Fig. 3,4,5).Other gears are fixedly connected with corresponding axle or connect with corresponding by controlled clutch.Five groups of normal meshed gears mechanisms have been formed at input shaft, output shaft.Wherein the driving gear of each non-circular gear mechanism all connects with corresponding input shaft by controlled clutch, and the free wheel device of non-circular gear mechanism is arranged between last driven gear and the corresponding axle.Two shared a pair of noncircular gears of non-circular gear mechanism.Wherein this to noncircular gear and one group of cylindrical gears constitute with one together, the corresponding non-circular gear mechanism of second gear circular gear mechanism, the maximum transmission ratio of this non-circular gear mechanism is greater than one grade of circular gear transmission ratio, and the fastest ratio of non-circular gear mechanism is less than second gear circular gear transmission ratio; This noncircular gear and another group cylindrical gears is constituted again together and two, the corresponding non-circular gear mechanism of third gear circular gear mechanism, the maximum transmission ratio of non-circular gear mechanism is greater than second gear circular gear transmission ratio, and the fastest ratio of non-circular gear mechanism is less than third gear circular gear transmission ratio.Three above uninterruptible power gear-shift transmissions of shelves, if the shared a pair of noncircular gear of plural non-circular gear mechanism, can form by that analogy and contain the less a plurality of non-circular gear mechanisms of the number of gears.Be example with three shelves uninterruptible power gear-shift transmissions shown in Figure 47 below, this uninterruptible power gear-shift transmission and working procedure are described.This three shelves uninterruptible power gear-shift transmissions, there is the bearing of gear housing, gear housing that four rotating shaft I, II, III, the IV that comprises input and output shaft is being set, these rotating shafts are by being provided with the pitch wheel group, three shelves circular gear mechanisms and two corresponding transition shelves non-circular gear mechanisms from the input shaft to the output shaft, have been constituted, every adjacent two grades of circular gear mechanisms corresponding configuration one transition shelves non-circular gear mechanism.The driving gear of three shelves circular gear mechanisms all is fixedly connected with input shaft I, the driving gear of two grades of non-circular gear mechanisms and auxiliary axis III are fixedly connected, circular gear mechanism, non-circular gear mechanism all are that driven gear connects by roller-type overrunning clutch or Wedge type over running clutch (referring to Figure 23,24,25,42,43,44) with output revolving shaft II, have formed five groups of normal meshed gears mechanisms between the input output rotating shaft.Rotating shaft I, the II of transferring power concentrate circular gear are being set relatively, constituted the circular gear mechanism of three shelves, rotating shaft I, II, III, the IV of transferring power are being provided with the gear that comprises a pair of noncircular gear relatively, have constituted the non-circular gear mechanism of two transition shelves.The controlled clutch that passes through two pairs of circular gears and cooperation between input rotating shaft I and the auxiliary rotating shaft III respectively connects.Between wherein a pair of circular gear and rotating shaft II, the IV this to a pair of circular driving gear between noncircular gear and rotating shaft III, the IV constitute with one together, the corresponding non-circular gear mechanism of second gear circular gear mechanism, the maximum transmission ratio of non-circular gear mechanism is greater than one grade of circular gear transmission ratio, and the fastest ratio of non-circular gear mechanism is less than second gear circular gear transmission ratio; Another between circular gear and rotating shaft II, the IV this constituted again together to a pair of circular driving gear between noncircular gear and rotating shaft III, the IV and two, the corresponding non-circular gear mechanism of third gear circular gear mechanism, the maximum transmission ratio of non-circular gear mechanism is greater than second gear circular gear transmission ratio, and the fastest ratio of non-circular gear mechanism is less than third gear circular gear transmission ratio.The roller-type overrunning clutch of non-circular gear mechanism can also be arranged between the gear and corresponding rotating shaft between input rotating shaft I and the auxiliary rotating shaft III like this.By one grade to the second gear speed change, the controlled clutch of the non-circular gear mechanism that make with earlier, second gear is corresponding engages, make the operating mechanism action of a retaining make one grade free wheel device be in state to be separated again, next the operating mechanism with this non-circular gear mechanism makes its free wheel device be in state to be joined.This non-circular gear mechanism driven gear angular velocity is increased to identical with first speed driven gear and when being greater than, the free wheel device of non-circular gear mechanism engages also one grade free wheel device is separated automatically from minimum.Move the second gear operating mechanism at last, this non-circular gear mechanism driven gear angular velocity be increased to maximum near the time, the operating mechanism recovery free wheel device of second gear is in state to be joined.This non-circular gear mechanism driven gear angular velocity is reduced to identical with the second gear driven gear and when being less than, the free wheel device of second gear engages automatically, and the free wheel device of non-circular gear mechanism is separated automatically, make its free wheel device keep separated state with the operating mechanism of non-circular gear mechanism.The driving gear of this non-circular gear mechanism is separated with controlled clutch between the input shaft, make non-circular gear mechanism no longer with other mechanisms' idle running.To three class gear shift, the controlled clutch of the non-circular gear mechanism that make with two earlier, third gear is corresponding engages, and successively makes the free wheel device of second gear, non-circular gear mechanism, third gear in running order again by second gear; Non-circular gear mechanism driven gear angular velocity is increased to identical with the second gear driven gear and when being greater than, the free wheel device of non-circular gear mechanism engages also the free wheel device of second gear is separated automatically from minimum; In the time of near non-circular gear mechanism driven gear angular velocity is increased to maximum, the third gear operating mechanism makes free wheel device be in state to be joined, non-circular gear mechanism driven gear angular velocity is reduced to identical with the third gear driven gear and when being less than, the free wheel device of third gear engages automatically, and the free wheel device of non-circular gear mechanism is separated automatically, make its free wheel device keep separated state with the operating mechanism of non-circular gear mechanism.The driving gear of this non-circular gear mechanism is separated with controlled clutch between the input shaft, make non-circular gear mechanism no longer with other mechanisms' idle running.By opposite to the low speed speed-change process at a high speed.By third gear to the second gear speed change, with two, the controlled clutch of the non-circular gear mechanism of third gear correspondence engages, and successively make the free wheel device of third gear, non-circular gear mechanism, second gear in running order with operating mechanism separately.The driven gear angular velocity of this non-circular gear mechanism is increased to identical with the third gear driven gear and when being greater than, the free wheel device of non-circular gear mechanism engages and the free wheel device of third gear is separated automatically, and the operating mechanism of third gear makes its free wheel device keep separated state; After non-circular gear mechanism driven gear angular velocity is increased to maximum and begins to reduce, non-circular gear mechanism driven gear angular velocity is reduced to identical with the second gear driven gear and when being less than, the free wheel device of second gear is in jointing state automatically, and the free wheel device of non-circular gear mechanism is separated automatically, the operating mechanism return of non-circular gear mechanism makes free wheel device keep separated state; The controlled clutch of control non-circular gear mechanism separates, and non-circular gear mechanism is no longer dallied.To one grade of speed change, the controlled clutch of the non-circular gear mechanism that make with earlier, second gear is corresponding engages by second gear, successively makes second gear, this non-circular gear mechanism, one grade free wheel device in running order again; Non-circular gear mechanism driven gear angular velocity is increased to identical with the second gear driven gear and when being greater than, the free wheel device of non-circular gear mechanism engages also the free wheel device of second gear is separated automatically from low; When non-circular gear mechanism driven gear angular velocity is reduced to identical with first speed driven gear again and is less than, one grade free wheel device is in jointing state automatically, and the free wheel device of non-circular gear mechanism is separated automatically, the operating mechanism return of non-circular gear mechanism makes its free wheel device keep separated state.The controlled clutch of control non-circular gear mechanism separates, and non-circular gear mechanism is no longer dallied.

Claims

1, a kind of gear-shift transmission of uninterruptible power, there is the bearing of pedestal or gear housing, pedestal or gear housing that at least two transmission shafts are being set, have two-stage driving gear set at least between the transmission shaft relatively, it is characterized in that: also be provided with the noncircular gear group between the relative transmission shaft of every adjacent two-stage driving gear set, a gear in driving gear set, the noncircular gear group is connected by free wheel device with transmission shaft, and free wheel device also has clutch operation.

2, as the gear-shift transmission of the said uninterruptible power of claim 1, it is characterized in that: a gear in driving gear set, the noncircular gear group is connected by free wheel device with transmission shaft, be meant two groups of driving gear set of adjacent two-stage and one group of noncircular gear group of corresponding configuration, driven gear of every group driving gear or every group or every group have a gear and carry out spool being connected by free wheel device of transfer motion power.

3, as the gear-shift transmission of the said uninterruptible power of claim 2, it is characterized in that: the velocity ratio of bootom gear group is less than the maximum transmission ratio of the noncircular gear group of corresponding configuration with it relatively in two groups of driving gear set of adjacent two-stage, and the velocity ratio of relative high speed gear group is greater than the fastest ratio of the noncircular gear group of corresponding configuration with it in two groups of drive gear mechanisms of adjacent two-stage.

4, as the gear-shift transmission of the said uninterruptible power of claim 3, it is characterized in that: have linking mechanism between the clutch operation that free wheel device has.

5, as the gear-shift transmission of the said uninterruptible power of claim 3, it is characterized in that: free wheel device is a Wedge type over running clutch, the clutch operation that Wedge type over running clutch has is the control mechanism of the relative ring swing position with concave circular arc with the control pusher dog of the pusher dog that is arranged on voussoir side or voussoir end face opening, perhaps for the goods of furniture for display rather than for use that is enclosed within voussoir end face projection and control goods of furniture for display rather than for use relatively with the control mechanism of the ring swing position of concave circular arc.

6, as the gear-shift transmission of the said uninterruptible power of claim 3, it is characterized in that: free wheel device is a roller-type overrunning clutch, the clutch operation that roller-type overrunning clutch has is to be arranged on the pusher dog of roller side or roller end face opening and the control mechanism of the relative star-wheel swing position of control pusher dog, perhaps is goods of furniture for display rather than for use that is enclosed within roller end face projection and the control mechanism of controlling the relative star-wheel swing position of goods of furniture for display rather than for use.

7, as the gear-shift transmission of the said uninterruptible power of claim 3, it is characterized in that: free wheel device is a roller-type overrunning clutch, the clutch operation that has is a pusher dog, the pawl of pusher dog is arranged on the wedge groove or the roller end face opening at roller place, the swinging end of pusher dog is arranged in the control chamber of star-wheel, space corresponding position between swinging end and the control chamber is provided with the control pin that can insert or transfer to control chamber, the control pin is connected the socket in axial sliding of slip ring and star-wheel with slip ring by spring.

8, as the gear-shift transmission of claim 4 or 5 or 6 said uninterruptible powers, it is characterized in that: the slip ring and the star-wheel of noncircular gear free wheel device operating mechanism or have and also have the axial return locking mechanism of restriction slip ring between the ring of concave circular arc, locking mechanism has the releasing lockable mechanism with the pusher dog interlock.

9, as the gear-shift transmission of the said uninterruptible power of claim 8, it is characterized in that: each is with between the pusher dog of pusher dog friction overdrive clutch operating mechanism or the goods of furniture for display rather than for use control mechanism linking mechanism being set.

10, as the gear-shift transmission of the said uninterruptible power of claim 3, it is characterized in that: clutch operation is electromagnetically-operated mechanism or hydraulic control mechanism or pneumatic control mechanism, is associated with between the electromagnetically-operated mechanism to be associated with between program control mechanism or the hydraulic control mechanism between program control mechanism or the pneumatic control mechanism to be associated with program control mechanism.