CN1568406B

CN1568406B - Infinitely variable adjustable gearbox

Info

Publication number: CN1568406B
Application number: CN038011875A
Authority: CN
Inventors: 乌尔里克·罗斯; W·布兰维特; C·德雷格尔
Original assignee: Individual
Current assignee: Individual
Priority date: 2002-09-30
Filing date: 2003-09-29
Publication date: 2011-10-05
Anticipated expiration: 2023-09-29
Also published as: DE10393308A5; DE10393308D2; CN1568406A

Abstract

A gearbox comprising an infinitely variable adjustable partial gear mechanism, consisting of two parallel mounted gear trains. The infinitely adjustable partial gear mechanism is provided in a first gear train of said two gear trains.

Description

Infinitely variable speed transmission

Technical field

The present invention relates to a kind of transmission device that has stepless adjustable branch's driving mechanism.Such transmission device itself is known, for example just has been disclosed in EP0878641A1 and EP0980993A2.Although only described conical friction ring transmission device in these documents, the present invention also can be used in combination with other infinitely variable speed transmission (CVT).

Background technique

Such infinitely variable speed transmission is very favourable under many running condition, especially at driving comfort or make full use of aspect the moment of torsion that is provided by drive unit.On the other hand, such transmission device is disadvantageous under some running condition especially.The latter for example may be slowly travel, under the state of reversing or constant continuous loading.

Summary of the invention

Task of the present invention provides a kind of transmission device that has stepless adjustable branch's driving mechanism, has wherein reduced the problem under special running condition.

As solution, the present invention proposes a kind of transmission device that has stepless adjustable branch's driving mechanism, the characteristics of this transmission device are the drive path that two parallel connections are arranged, and wherein, stepless adjustable branch's driving mechanism is arranged in first drive path in two drive path.

Such layout makes realizes that by second drive path special running condition or load condition becomes possibility, and first drive path can be brought the advantage of infinitely variable speed transmission.In this article, term " two drive path parallel connection " is meant, for example main differential mechanism of similar means such as the live axle of motor or clutch disk and common output terminal transmission part such as automobile of a common input end transmission part is arranged between these two drive path.Between common input end transmission part and output terminal transmission part, these two drive path can be alternately, add up ground and/or differential work, so that satisfy various requirement.

Thus, it may be favourable a reverse gear, one first grade and/or an overdirve gear being set in second drive path in these two drive path.For this situation, can only be conditionally and the suitable highland of cost use infinitely variable speed transmission, perhaps this infinitely variable speed transmission has very big loss, especially when overdirve gear, promptly under the situation of high rotating speed, low moment of torsion.

If between these two drive path, at least one freewheel is set, then can complicated gear shift or the gear shift regulation technology that need not to take a lot of trouble concentrate this two drive path.

In addition or as an alternative mode, in a transmission device that comprises stepless adjustable branch's driving mechanism, this branch's driving mechanism be arranged between two power dividers as differential drive portion or planetary pinion based part between, wherein, at least one input end of this stepless adjustable branch's driving mechanism effectively is connected with at least one output terminal of an input end power divider, and at least one output terminal of this stepless adjustable branch's driving mechanism effectively is connected with at least one input end of an output terminal power divider.By such layout, can expand the regulation range that realizes the moment of torsion transmission or expand stepless adjustable branch's driving mechanism, wherein, according to existing understanding, this is to finish under the situation of wasted power, because these two power dividers generally cause loss certainly.On the other hand, such layout can obviously be widened the application area of continuously variable transmittion.In addition, thus one, must can reduce by the moment of torsion of stepless adjustable branch's driving mechanism transmission, the result, in suitable form of implementation, can make loss limited, because the moment of torsion that reduces causes littler loss in infinitely variable speed transmission (an especially conical friction ring transmission device), this loss can correspondingly reduce the loss in power divider.

In addition or as an alternative mode, one also with exist a stepless speed variator irrespectively to comprise in the transmission device of at least one forward gears and at least one reverse gear to be provided with a differential mechanism, it has realized this forward gears and this reverse gear, and wherein at least one parts of this differential drive portion selectively are fixed together with another parts of shell and/or differential drive portion.So, can realize a transmission device that has a forward gears and a reverse gear very compactly, wherein for example a differential component of a differential drive portion is used as input end.So, when the central module of this differential mechanism is connected with second differential component, just can realizes one and turn to.And if second differential component of differential mechanism or central module are connected with shell when also being fixed thus, then another loose at that time parts change turns to, and the result just can realize above-mentioned gear shift.So, can realize a transmission device that comprises a forward gears and a reverse gear very compactly.

And, in addition or as an alternative a transmission device is proposed to mode, it comprises at least two speed change gears, these speed change gears selectively are access in the drive path by a transmission components, and wherein the first speed change gear in these two speed change gears has stepless adjustable branch's driving mechanism.As if such structure is harmful to system at least, because be provided with a stepless speed variator, so that can abandon any type of gear shift.But, such layout allows only just to adopt a stepless speed variator when its advantage is actually very important.For example, often occur when starting than higher moment of torsion, this moment of torsion has obviously increased the weight of the load of stepless speed variator or has required oversize ground design stepless speed variator.Thus, for example realize one first grade and only just to insert stepless adjustable branch's driving mechanism after starting be favourable separately.In this case, especially can determine the size of stepless adjustable branch's driving mechanism like this, promptly before changing to the gearshift procedure of another speed change gear from one of these two speed change gears, realize the coupling of the rotating speed of the rotating speed of the second speed change gear and the first speed change gear by this infinitely variable speed transmission, thereby transition from the first speed change gear to the second speed change gear or the transition from the second speed change gear to the first speed change gear can steplessly be carried out.So, the advantage of stepless adjustable branch's driving mechanism can obtain optimum utilization, and needn't tolerate the shortcoming as occurring when the starting.

This also is applicable to the basicly stable constant or basicly stable constant situation of its moment of torsion of its power, wherein not necessarily will use stepless adjustable branch's driving mechanism, because can realize velocity variations by changing engine speed.Under such operating mode, stepless adjustable branch's driving mechanism general (for example by the decision ground that skids) has big loss, this loss can be avoided by the speed change gear of an access, here, also can on the operation point, realize gear shift, wherein the passenger note less than or be to notice such transforming gear not obviously.Infinitely variable speed transmission is entered in the suitable operating mode.For example, what also can expect is, inserts or disconnects such speed change gear by a freewheel.

In addition, the speed change gear that also can insert except the speed change gear that comprises stepless adjustable branch's driving mechanism can comprise a differential drive portion, and it for example is used to carry out gear shift and be used for start gear between forward gears and reverse gear.Especially concerning such form of implementation, the fixing of parts of the required differential drive portion of gear shift realizes it being favourable by friction clutch between forward gears and reverse gear, and the result can realize cautious and consistent as far as possible gear shift.

Having two at one can selectively be access in by a transmission components in the transmission device of the speed change gear in the drive path, the first speed change gear in two speed change gears comprises stepless adjustable branch's driving mechanism, transmission components can link up this stepless adjustable branch's driving mechanism with a pump impeller of one three wheeled fluid torque converter or another parts that directly link to each other with an engine output shaft, and the motor output member that turbine or another of the second speed change gear and this three wheeled fluid torque converter can insert is linked up.So, engine power and especially under nominal situation, be directly passed to stepless adjustable branch's driving mechanism, especially in starting process, high moment of torsion passed to the second speed change gear, thereby make this stepless adjustable branch's driving mechanism unloading therewith relatively.This is particularly suited for uniting use with the turbine of one three wheeled fluid torque converter, wherein Lock-in the moment of torsion increase, otherwise, this increases significantly load can for stepless adjustable branch's driving mechanism.

Especially when uniting use with a motor, stepless adjustable branch's driving mechanism that has input end that coaxial line arranges and an output terminal irrespectively is favourable with all the other features of transmission device of the present invention also, because in such layout, can reduce to act on the moment of torsion of shell very compactly.Be preferably in the output terminal that coaxial line arranges and be provided with a differential drive portion, it is driven by an output terminal of infinitely variable speed transmission again.This structure is very compact, because the output terminal of infinitely variable speed transmission affacts on the differential mechanism with need not intergrade, and this differential mechanism especially just must have in automobile originally.In addition, anyway generally need gear or other driving component to form the input end and the output terminal of coaxial line, therefore, the parts that do not need to add because differential drive portion is arranged.Above-mentioned configuration structure is particularly suited for uniting use with a Vidacare corp, wherein, a motor is linked to each other with an infinitely variable speed transmission itself look like to system harmful because the rotating speed of motor is original just almost can regulated at will.On the other hand, this infinitely variable speed transmission allows motor to turn round under such rotating speed, and promptly it has favourable moment of torsion/electric current [strength ratio under this rotating speed.Like this, especially under slow-revving situation, the total efficiency in corresponding driving path has improved or required magnitude of current has reduced.

A transmission device of the present invention, but also can be a different infinitely variable speed transmission, can effectively be connected as a starting clutch, a torque-converters, a friction disk, a hydraulic coupling or a synchronizer with a bonding point at input end or output terminal.The advantage of the infinitely variable speed transmission that layout is opposite is that infinitely variable speed transmission or drive unit are protected in starting process, have therefore prolonged working life.It is very favorable at output terminal starting clutch or bonding point being set, and stops because can adjusting when engine running in such layout.On the other hand, input end starting clutch or bonding point allow to insert other driving component, if do like this.

These two branch's driving mechanisms preferably engage with an input end of subsequently drive path with its output terminal and so just flock together.When the input end of next drive path is that main differential mechanism promptly connects and when driving the differential mechanism of two wheels of a driven automobile axle, the structure of this transmission device is very compact.Such compact structure shows as the parts minimizing on the one hand and can reduce cost thus.On the other hand, such compact structure has determined little structural volume, and the result can further reduce the automobile overall cost.

According to the difference of concrete Environmental Conditions, in these two branch's driving mechanisms one comprises a reverse gear and perhaps one first grade and second branch's driving mechanism comprise that this infinitely variable speed transmission and especially conical friction ring transmission device are favourable.Especially abandon one independently first grade the time when first branch's driving mechanism, along with unusual compact structure and bring above-mentioned advantage.

These two branch's driving mechanisms preferably can insert respectively or disconnect.This accomplishes that especially so promptly each branch's drive path disconnects by a clutch.In this case, it is important hardly that disconnection is carried out on which position, this can carry out at output terminal, also can carry out at input end, wherein, be arranged in bonding point driving component over there and can successfully do not bear the running together of load ground, therefore, these two branch's drive path not necessarily are equipped with two clutches respectively.But the loss that driving component caused for fear of driving because of idle running also can be provided with a plurality of clutches in branch's drive path.But, these branch's drive path have increased number of components and required structure space, and this has had influence on cost again.

The structure of the infinitely variable speed transmission of certainly, such branch's driving mechanism that has a parallel connection is also advantageously irrelevant with further feature of the present invention.This is particularly useful for cooperating with conical friction ring transmission device as infinitely variable speed transmission, because so, can be realized compactly with other branch's driving mechanism very effectively by the advantage that turns to change of conical friction ring transmission device decision.

In addition, about compact structure proposed, in an infinitely variable speed transmission and especially conical friction ring transmission device, one is played the clutch piece that inserts or disconnect the drive path effect that comprises this infinitely variable speed transmission and is arranged in one of them stepless adjustable driving component of infinitely variable speed transmission at that time, for example in a cone.In an infinitely variable speed transmission, must on main driving component, provide bigger alternation face, so that can guarantee corresponding variability.By such clutch piece is set in comprising the driving component of big alternation face, can save sizable structure space because utilized in this driving component otherwise the structure space that is not used.Certainly, in an infinitely variable speed transmission, such layout of clutch piece also irrespectively shows corresponding advantages with further feature of the present invention.

In addition, in the transmission device that has two driving components that on different axis, turn round, often to clamp described driving component relatively, so that between these two driving components, provide enough alternation power by a hold down gag.This especially also is applicable to infinitely variable speed transmission, especially when they frictionally during alternation, wherein impacting force is perhaps irrespectively selected with the moment of torsion that will transmit.

In such layout, irrespectively being provided with one with further feature of the present invention selectively makes that these two driving components separate with one the 3rd driving component by disconnection or makes the clutch piece that they are connected with the 3rd driving component by access, so each drive path is selectively received on the total driving mechanism.In such layout, insert the needed power of clutch piece and preferably produce by hold down gag.It is favourable that clutch piece is arranged in the line of force of impacting force this.

In such layout, to need only on an appropriate location compensation impacting force just much of that for cut-off clutch, thereby impacting force applies load no longer for corresponding clutch.So, disconnect corresponding clutch, and these two driving components are broken away from correspondingly related.Especially when hold down gag and moment of torsion are controlled relevantly, directly just cause impacting force to reduce, because depend on the clutch ground of disconnection, moment of torsion can't transmit again.Like this, the power that applies for disconnection has directly reduced many.In addition, the reducing of impacting force also determined reducing of loss, and this loss may be by the perhaps still driving component of idle running decision.In order to insert clutch, only need reduce corresponding counter-force, thereby hold down gag has just worked again.Therefore, insert clutch and do not need optional feature.

In addition, in addition or as an alternative mode ground has proposed a kind of infinitely variable speed transmission, conical friction ring transmission device especially, and it has one and is arranged between the output terminal and reverse gear that connect with all the other driving mechanisms.Such layout has such advantage on the one hand, and promptly this transmission device can be stablizing the constant work that turns to, this to infinitely variable speed transmission control or the adjusting of friction ring is favourable.In addition, also can realize the layout of step-less adjustment reverse gear.

On the meaning of reverse gear layout, term " series connection ", " preceding " or " back " relate to the power transmission line in comprising the driving path of an infinitely variable speed transmission.Thus, according to the present invention, reverse gear should be disposed in series in infinitely variable speed transmission in driving the path on that side of motor.

Reverse gear preferably includes an epicyclic train, and it has the transmission bracket of at least one around the movement, and this stent support at least one driving component of this epicyclic train and selectively is fixed together with the driving component of a shell or an around the movement.By such layout; a reverse gear is provided; it as required also can be when drive unit rotates and conical friction ring transmission device or infinitely variable speed transmission be access in when rotating; its way is; the driving component quilt of around the movement selectively respective fixation is lived, and wherein such fixing obtains corresponding protection ground by suitable clutch or synchronizer and carry out.Such gear shift possibility especially is adapted to the requirement of conical friction ring transmission device, and this conical friction ring transmission device itself only could change its velocity ratio under rotary state.

Reverse gear especially can be an epicyclic train, it comprises planetary pinion, sun gear and external gear, one of them first driving component effectively is connected with the output terminal of infinitely variable speed transmission, one second driving component effectively is connected with the output terminal of the general arrangement that is made of infinitely variable speed transmission and reverse gear, and the relative shell of the 3rd driving component is being fixed aspect its degrees of freedom at least.An epicyclic train has favourable performance, promptly fixing one of them driving component (external gear, sun gear or planetary pinion, wherein planetary pinion should advantageously keep its rotation ability) time, other driving component can continue around the movement respectively and according to the velocity ratio that obtains thus and interaction effect.Especially, a driving component is at least in the notable change that has firmly been determined the relative velocity between all the other two driving components aspect the degrees of freedom by respective fixation, and therefore, this relative velocity changes can be used to control reverse gear.

The latter can be guaranteed like this that promptly the 3rd driving component is a planetary pinion.If the planetary pinion in epicyclic train itself is fixed around the degrees of freedom of corresponding sun gear rotation, then direct consequence is exactly the change that turns between external gear and the sun gear, thus one, if what realize when the planetary pinion respective synchronization detours is forward gear, then can realize a corresponding reverse gear, wherein perhaps can suitably select velocity ratio by epicyclic train.

When first driving component was driven with the small gear of the driven cone around the movement of conical friction ring transmission device by one, the structure of the general arrangement that is made of infinitely variable speed transmission or conical friction ring transmission device and reverse gear was very compact.Such layout has guaranteed direct power transmission line and the moment of torsion transfer line between conical friction ring transmission device and reverse gear, thereby very compact and thereby especially Hyundai Motor has been constituted this general arrangement most economically.

About the latter's requirement, may be more favourable or also advantageously, second driving component is connected the ground around the movement with the support of the around the movement of a differential mechanism.Especially in the time of in being used in automobile, can advantageously utilize main differential mechanism here, therefore, reverse gear directly is integrated in the differential mechanism, and compact structure has irrespectively been realized with the input end structure of reverse gear in wherein especially relevant with conical friction ring transmission device ground.

If first, second driving component can be fixed together, then this is favourable to normal operation especially.According to the concrete performance of the gear-change operation relevant, also can advantageously utilize such adjusting to fix the required operating mode of epicyclic train with reverse gear.Because first, second driving component can be fixed together, so guaranteed direct power transmission by epicyclic train, as a result, under this operating mode, epicyclic train can't harm especially relevantly with the forward gears efficient operation of lost territory work and this general arrangement substantially.Selecting of the 3rd driving component or preceding two driving components is fixing preferably correspondingly relevant, thereby epicyclic train can work safety ground running under its state.Following measure is highly beneficial to this, and promptly first or second driving component because so, can very simply be realized the required cooperation between the driving component compactly by the external gear of epicyclic train or sun gear constitutes and the 3rd driving component is made of planetary pinion.This is applicable to that especially second driving component directly links to each other with the support of the around the movement of a differential mechanism or is integral with it and/or first driving component when directly being driven by a small gear with driven cone around the movement.In such form of implementation, this general arrangement especially concerning the orthodox car drive unit, caused very compact and thereby cost very cheap and can be used on transmission device in the compact car, and traditional automotive proplsion is subjected to a large amount of parts and complete automobile rank to change the driving that restrictedly always has in the same way.

Fixing for opposite shell as the transmission bracket of around the movement or the degrees of freedom of planetary pinion or the 3rd driving component, can be so various modes of fixedly employing such as frictional engagement or form fit connection.It is especially favourable that such frictional engagement is proved to be, and promptly it can realize transition smoothly, and this transition according to concrete form of implementation and surely even allow to insert reverse gear in rotation.But, because than higher power and frictional loss, the latter is not favourable to any application, therefore, can advantageously between motor and conical friction ring transmission device a starting clutch be set especially under these circumstances.For fixing, suitably adopt clutch, inertia brake, synchronizer and similar device according to ground, concrete application, as they and the transmission device of knowing already develop relevantly.

Certainly, except feature of the present invention or alternative feature of the present invention ground, such layout of reverse gear also is favourable.

Therefore, task of the present invention provides a kind of infinitely variable speed transmission, and it also can work safety and loses and transmit high torque littlely.

For provide a kind of can work safety and lose the infinitely variable speed transmission that transmits high torque littlely and propose, except above-mentioned feature or replace above-mentioned feature ground, such transmission device has at least two stepless adjustable branch's driving mechanisms, they are arranged in parallel in the drive path, wherein, these two stepless adjustable branch's driving mechanisms are received on an input component or the output member by a total moving driving mechanism.

Adopt the advantage of a total moving driving mechanism (being also referred to as the stack driving mechanism) to be, first driving component of the branch's driving mechanism fixation that differs has identical rotating speed or exactly determined rotating speed in the prior art like that.Exactly, these two branch's driving mechanisms have been finished himself to total contribution relevant with rotating speed of moving the final rotating speed of driving mechanism.Therefore, layout of the present invention can control separately and regulate these two branch's driving mechanisms and thereby utilized such advantage, be about to that an infinitely variable speed transmission is divided into two stepless adjustable branch's driving mechanisms and the advantage brought, for example moment of torsion is given this two branch's driving mechanisms, and do not have appearance thus by the shortcoming that the rotating speed that forces brings, resemble and must tolerance pay as frictional loss or higher adjusting.

Therefore, these two branch's driving mechanisms have unexpectedly determined to imagine or its advantage aspect utilizing at transmission device by the asymmetric free misconnection of total moving driving mechanism own, especially the advantage aspect requiring in efficient and control, this is under the situation of symmetry as be forced to not accomplish under the situation of being mutually related at the planetary pinion because of a planet train of gearings.

The typical typical example of total moving driving mechanism of the present invention is epicyclic train in this way, wherein two parts in three transmission device constituent elementss (planetary pinion, sun gear and external gear) link to each other with two branch's driving mechanisms and the 3rd driving component as input end or output terminal, wherein planetary pinion is used as a driving component together, typical case's representative of total moving driving mechanism of the present invention also can be a differential mechanism, wherein, these two branch's driving mechanisms are connected with one of differential of differential mechanism respectively.

These two stepless adjustable branch's driving mechanisms have a common driving component in its that side back to total moving driving mechanism.It for example can be a common input shaft or a common output shaft.It also especially can be these two direct driving components in stepless adjustable branch's driving mechanism, and this driving component is used jointly by two branch's driving mechanisms.For this reason, for example at conical friction ring transmission device with one of them cone as common driving component.By such form of implementation, compact and constitute such transmission device at low cost, because can reduce the total number of parts of corresponding transmission device by this dual utilization.

In this article, term " back to that side of total moving driving mechanism " is a direction in drive path, and it is decided by the power transmission line of transmission device and not necessarily conforms to shape or spatial depiction.

A plurality of infinitely variable speed transmissions have a main transmission plane, be provided with critical piece such as input shaft and output shaft, input cone and output cone or similarly rotate symmetric objects in this main transmission plane, so just limit a transmission plane.When two main transmission planes of these two branch's driving mechanisms were arranged in parallel to each other, the structure of transmission device of the present invention was very compact.She Ji transmission device of the present invention very constitutes and can do with the comparison high pulling torque in the level land like this.In addition, thus, such transmission device is particularly useful for the jubilee wagen with diesel engine because its structure space can according to as the mounting type that is installed under the pressurized machine very well design, and can successfully tackle the high moment of torsion of modern diesel engine.

In addition, another adjustable branch's driving mechanism can be set as especially a speed changer or a reverse gear between one of stepless adjustable branch's driving mechanism and always moving driving mechanism.By such layout, can realize having very broad drive performance and especially can stepless driving forward gears and the transmission device of reverse gear.Especially, even if in the drive unit of operation, such transmission device also can be implemented feedback, stops thereby make output terminal not have moment of torsion ground.

Even if the present invention compares the efficient that has improved overall transmission device with the transmission device of prior art, but infinitely variable speed transmission is especially under the more stable operating conditions as after the starting or at interstate road or tell under the operating mode that occurs when travelling on the highway and demonstrate than higher loss.For fear of such loss, especially not necessarily needing to use under the situation of infinitely variable speed transmission, can tap at least one of them stepless adjustable branch's driving mechanism be favourable.So, for example can under above-mentioned operating mode, walk around loss than higher stepless adjustable branch's driving mechanism, thereby, under these operating conditions, improved efficient.Certainly, so adopting two stepless adjustable branch's driving mechanisms irrespectively is favourable with all the other features of the present invention also.

Description of drawings

Describe other advantage of the present invention, purpose and characteristics according to the description of the drawings, accompanying drawing is depicted as:

Fig. 1 represents first transmission device with the sectional view along the line I-A-B-C-D-I of Fig. 2;

Fig. 2 is with the transmission device of diagrammatic side view presentation graphs 1;

Fig. 3 is the schematic representation of transmission device shown in Figure 1;

Fig. 4 is the schematic representation of another transmission device;

Fig. 5 is the schematic representation of another transmission device;

Fig. 6 is the schematic representation in the driving path of an active cone that has a coaxial line and driven cone;

Fig. 7 is the schematic representation that has another driving path of the active cone of coaxial line and driven cone, wherein shows to be in two friction rings on the working position;

Fig. 8 represents feasible reverse gear;

Fig. 9 represents another transmission device with the schematic representation similar to Fig. 3;

Figure 10 is with the transmission device along the sectional view presentation graphs 9 of the bearing of differential mechanism, reverse gear and output cone;

Figure 11 is with along the transmission device shown in the sectional view presentation graphs 9,10 of the driven cone of differential mechanism, reverse gear and output cone;

Figure 12 is with the transmission device shown in the view table diagrammatic sketch 9-11 similar to Fig. 1;

The partial enlarged drawing of Figure 12 when Figure 13 is illustrated in hold down gag and opens;

Figure 14 represents the structure of the Figure 13 when hold down gag shortens;

Structure shown in Figure 13,14 when Figure 15 is illustrated in cone clutch and opens;

Figure 16 amplifies the part of expression Figure 15;

Figure 17 is the schematic representation of an additional or reverse gear of replacing;

Figure 18 is that another replenishes or the schematic representation of the reverse gear of replacement;

Figure 19 schematically illustrates the possibility that infinitely variable speed transmission may be divided into two branch's driving mechanisms;

Figure 20 represents to have the transmission device of Figure 19 of additional gear shift possibility;

Figure 21 is to represent that to Figure 19,20 similar views infinitely variable speed transmission can be divided into another possibility of two branch's driving mechanisms;

Figure 22 is to represent that to Figure 19,21 similar views infinitely variable speed transmission can be divided into the another possibility of two branch's driving mechanisms;

Figure 23 represents to have the gearbox of Figure 22 of additional gear shift possibility.

Embodiment

Transmission device shown in Fig. 1-3 mainly comprises two drive path 1,2, and they can be access in one by a synchronous speed changer 3 selectively and drive in the path.

Here, first drive path 1 has a conical friction ring transmission device that has two opposed cones 4,5, described cone is to arrange like this, promptly moves in this slit, road around cone 5 ground leaving 6, one friction rings 7 in one slit between the cone 4,5.For making the conical friction ring transmission device can transmitting torque, cone 4 comprises a hold down gag 8, and it tightens this two cones 4,5 applying clamping between the bearing 9,10 under the situation of the variable power of depressing.

Cone 4 has a running face 12 and a clamping element 11 is arranged on the other hand on the one hand, work between them at a hold down gag 8, wherein, hold down gag 8 can make clamping element 11 move vertically relative to running face 12, the result, clamping element 11 is bearing on the fastening bearing 9 and on the other hand on the one hand running face 12 is pressed onto on the friction ring 7, and here, this pressure is dealt with by second cone 4 and additional fastening bearing 10.

Specifically, hold down gag 8 comprises two disc springs and two compressing members and two rollers 17 that are arranged between the compressing member.Disc spring and compressing member are connected with regard to impacting force, therefore, when moment of torsion changes, compared with prior art big many movement clearance are provided for one of them compressing member, and this causes the accurate and reproducible adjusting of impacting force.In addition, disc spring has radial cavities, wherein is embedded with the parts with running face 12 or the corresponding projection of compressing member.So, disc spring is transmitting torque between parts that have running face 12 and compressing member, thus one, compressing member by with the slip unloading of bearing torque load of the parts that comprise running face 12, this causes the higher reproducibility of the final impacting force relevant with moment of torsion again.In this embodiment, move in the raceway of roller 17 each compressing member, described raceway has the different degree of depth.Like this, can realize distance between the compressing member relevant with moment of torsion, wherein, if compressing member week upwards because of moment of torsion occurring when mobile, roller 17 is used for the height reproducibility of final impacting force.Certainly, above-mentioned feature can irrespectively be advantageously used in the reproducibility of final impacting force each other.

Also disclose, replaced ball 17 ground also can use roller such as roller or be fixedly supported upon roller on the compressing member.Be also contemplated that such hold down gag also can be arranged in the active cone 5.

But, replace this mechanical structure ground, replace in the form of implementation at one, an electric motor driven servomechanism of dependence that is used for hold down gag also can be set, it resembles hydrodynamic thrust bearing or the quiet liquid thrust bearing and controls according to the moment of torsion that records, so that realize the impacting force relevant with moment of torsion.

Disclose on the other hand, have only the displacement of compressing member or comprise the parts of running face 12 and clamping element 11 the displacement that upwards occurs in week or for example axial force that acts on fastening bearing 9,10 can be used to determine the moment of torsion that occurred.

In addition, the embodiment shown in Fig. 1-3 relevantly with stepless change conical friction ring transmission device comprises a starting clutch at input end, and this starting clutch becomes the form of three wheeled fluid torque converters.Comprise that the speed change gear of conical friction ring transmission device 1 can directly be connected with the pump impeller 21 of three wheeled fluid torque converters 20 by speed changer 3, and starting can realize by the turbine 22 and a differential drive portion 23 of three wheeled fluid torque converters 20 here.This differential drive portion 23 is rigidly connected with one of them the differential end 24 that has turbine 22, and the second differential end 25 is by the output terminal utilization of this speed change gear and by gear 27 engagements of a gear 26 with a main driven shaft 28 that should always move driving mechanism, and it is by main differential mechanism 15 engagements of a small gear 33 and an automobile, here, gear 27 on the other hand with output terminal 29 engagement of conical friction ring transmission device 1.Differential drive portion 23 comprises two friction clutches 30,31, and they selectively are fixed on the primary input end of differential mechanism 23 on shell 32 or the output terminal 25.Like this, as shown in the figure, turning to of output terminal can be changed, and the result can successfully realize a forward gears and a reverse gear.Under the situation that clutch 30,31 disconnects, differential mechanism and turbine 22 freely turn round, and therefore, although there is the joint of output terminal, still can utilize conical friction ring transmission device.

The advantage of this layout is, in order to start or in reverse gear, can to utilize the advantage of three wheeled fluid torque converters 20.In addition, by differential mechanism 23, can realize forward gears and reverse gear very compactly.On the other hand, by speed changer 3, can avoid the shortcoming of three wheeled fluid torque converters 20, promptly when running well, cause high power loss and moment of torsion too high because of skidding, this is because speed changer 3 is directly realized the driving of turbine 22 short circuits and conical friction ring transmission device 1 by pump impeller 21.These two drive path 1,2 also allow from the velocity ratio of the gearshift procedure adjusting taper like this friction ring transmission device 1 between these two drive path 1,2 in the connection of output terminal, and promptly these two drive path 1,2 also almost have been synchronized at input end.Remaining can itself be finished by speed changer 3 synchronously, and wherein three wheeled fluid torque converters 20 also can play the support effect.

In transmission configuration shown in Figure 4, two around the movement, reciprocally the coaxial line cone 91,92 of arranging is also effectively continuous by a friction ring 93, this friction ring can move along one slit staying between cone 91,92 outer circumferential faces, as a result, can realize different velocity ratios.In such layout, initiatively cone 91 and driven cone 92 all can be received on the main driven shaft 95 by a synchronizer 94, and this main driven shaft meshes by the main differential mechanism 97 of a small gear 96 and an automobile again.In such structure, initiatively cone 91 links to each other with main driven shaft 95 under the identical situation of commutation number of times with driven cone 92, thereby, directly guaranteed commutation by synchronizer 94.This layout allow number of components minimum and thereby the lowland of cost realize a forward gears and a reverse gear.Here, commutation can only be by the driving belt of meshed gears or around the movement selectively therein cone 91 or 92 with synchronizer 94 between generation, therefore, by this structure, perhaps also can demonstrate one first grade or an overdirve gear cost efficient.According to the difference that driving turns to, small gear 91a, 92a link to each other by a belt dressing with gear 91b, 92b or directly engagement.What can also expect is to be provided with a tumbler gear between small gear 96 and main differential mechanism 97.

Preferably this synchronizer has a position of rest or a middle position, thereby

cone

91,92 can dally.So, friction ring 93 or another connected member also can be conditioned when parking of automobile.

Device shown in Figure 4 especially is used for realizing inexpensively forward gears and reverse gear with the commutation of conical friction ring transmission device.Thus, it also is applicable to the infinitely variable speed transmission that other transposing turns to.

Transmission device shown in Figure 5 also comprises a conical friction ring transmission device 40 as stepless adjustable branch driving mechanism ground, wherein, be equipped with a power divider 41 and be equipped with a power divider 42 for it for this conical friction ring transmission device 40 at input end at output terminal.Here, by power divider 41,42 parallel first grades 43 of inserting conical friction ring transmission device 40, here, they are in output terminal selectively is access in driving path between output terminal 47 and input end 46 as described above synchronously and by friction clutch 44,45.

Embodiment shown in Figure 6 shows the situation of input end and output terminal coaxial line layout, and in infinitely variable speed transmission and especially conical friction ring transmission device, this has advantageously realized both sides coaxial line output.This causes smaller shell load on the one hand, on the other hand very compact structure can be arranged, and, especially in this embodiment, driven 50 50 active cones 51 of passing a conical friction ring transmission device 52 is arranged preferably here.In other infinitely variable speed transmission type, this structure also can advantageously be used with motor, and in the latter case, driven shaft also can pass the armature shaft of motor.

At this point, in this embodiment, a unshowned motor drives initiatively cone 51 by a drive unit 53, and this active cone acts on a driven cone 55 by a friction ring 54 again.Driven cone is by a small gear 56 and driven gear 57 engagements that are positioned on the driven shaft 50.

Transmission device shown in Figure 7 has similar structure, and its shell 60 is installed on the housing 61 of a motor.In this embodiment, armature shaft 53 is hollow and is passed by driven shaft 50.But driving gear 58 engagements of a driven gear 56 and a differential mechanism 59, this driving gear is connected with bipartite driving shaft 50 again.Because just a gear must be set here originally, so this configuration structure is very compact.

In addition, this configuration structure has an epicyclic train 62 that is used to reduce moment of torsion additionally between motor and infinitely variable speed transmission, so that do not make the infinitely variable speed transmission overload.

Conical friction ring transmission device 80 shown in Figure 8 especially can use with respective outer side edges shown in Fig. 5-7 and realize a reverse gear very compactly, and wherein, transmission device 80 comprises two

cones

81,82, and they are by ring 83 interaction effects.Come out outside the normal tapered zone (D), cone 82 also has a zone (R) of oppositely going in ring, in this embodiment, this realizes by a tapered collar 84, this tapered collar is around planetary pinion 85 motions, and these planetary pinions are supported on securely again in the gear mechanism housing 86 and with its internal surface and roll on a diminished shaft 87 of cone 82.Like this, tapered collar 84 oppositely rotates with the remaining part of cone 82.In addition, cone 82 has a neutral region (N), and it comprises a ring 88 that is bearing on the diminished shaft 87 free to rotately.

In such configuration structure, friction ring 83 at first moves into neutral region (N) from the main region (D) of cone 82, and wherein tapered collar 88 is adapted to the rotation by main cone body 82 and friction ring 83 decisions.If friction ring 83 continues to shift to the zone (R) of drawback movement, then it leaves main region (D) on the other hand, the result, and this neutral region (N) turns to and can be matched with this ring that falls back 84 and turn to.So, realized a reverse gear very compactly.

A reverse gear 80 like this or the commutation layout that designs in a known way especially can realize in the embodiment shown in fig. 4 with having, because so, when the distributor of power and/or rotating speed or adder 41 or 42 misconnection and can suitably select velocity ratio time the suitably, just can realize stopping of output shaft 47, although conical friction ring transmission device 40 and axle 43 are rotating.So, concerning automobile, all running condition are promptly moveed backward, are advanced and stop and can need not the no transition ground realization of other clutch ground, wherein, for other running condition such as full load operation or continuous loading running, clutch or other speed change gear can be set fully.

Shown in Fig. 9-16 correspond essentially to structure shown in Fig. 1-3 and thereby the device abandoning being repeated in this description in, be provided with two drive path 101,102, they selectively are access in one by a synchronous speed changer 123 or cone clutch 134 and drive in the path.Here, first drive path 101 has a conical friction ring transmission device that comprises the cone 104,105 of two positioned opposite again, these cones are arranged to leave 6, one friction rings 107 in one slit and move in this slit around cone 105 ground between cone 104,105.In order to make this conical friction ring transmission device energy transmitting torque, cone 104 comprises a hold down gag 108, this hold down gag in known manner or aforesaid way under the situation that applies a variable impacting force, these two cones 104,105 are pressed between the fastening bearing 109,110.For this reason, hold down gag has two rollers 117 and guide way 118,119, they are clamped and apply an impacting force relevant with moment of torsion as described below by them by disc spring 120, its way is, this hold down gag 108 ground relevant with moment of torsion distending and correspondingly being bearing on the bearing 109,110.

Especially as shown in Figure 9, reverse gear 124 comprises a driving gear 124, and drive path 102 is come out with this gear branch from the main transmission path.Drive a walking gear 125 by intermediate gear 130,133, it engages with small gear 126 by synchronous speed changer 123, and the direct again external gear 127 with main differential mechanism 115 of this small gear meshes.General structure is very compact, and if driving gear 124 is connected with driving shaft 121 by a synchronous speed changer and direct and external gear 127 engagements, then can also obtain compacter general structure.

Except reverse gear 102, this device also has a forward gears, and this forward gears is realized by infinitely variable speed transmission.Forward gears engages with external gear 127 also by small gear 129 so engages with reverse gear 102, and can be access in or disconnect by clutch 134.As shown in the figure, under off state, each driving component of branch's driving mechanism 101,102 also dallies.

As mentioned above, hold down gag 108 and clutch 134 cooperatings.In conjunction with Figure 13-16, understand working method the easiliest.Shown in Figure 13,14, hold down gag 108 ground relevant distending with transmitting torque.Here, Figure 13 represent moment of torsion high and thereby the structure of impacting force when big, Figure 14 represents the structure of impacting force hour.So roughly produce moment of torsion according to impacting force, promptly supporting mass 119 is supported on the fastening bearing 109 by a counterpart 150 and a driven shaft 151.Driven gear 129 is also arranged on axle 151.In addition, axle 151 passes through needle bearing 152 radial support on a centering thing 153.Moment of torsion is passed to driven gear 129 by tooth 154 (seeing Figure 16) from driven cone 104.

In hold down gag 108, moment of torsion causes ball 117 displacements, the result, and impacting force can change according to the mode of hope, shown in Figure 13,14.From seeing Figure 13-16, these two parts 119,150 are close to by the conical surface 156,157 (seeing Figure 16) respectively as direct.At last, these two conical surfaces 156,157 constitute effective clutch 134, and it is switched on by hold down gag 108.For cut-off clutch 134, this general arrangement has cylindrical body 158, one pistons 159 that are fixed on the shell moves in cylindrical body, and this piston can bear pressure by a hydraulic pipe line 160.Piston 159 is supported on the supporting mass 119 by a thrust bearing 161 and a supporting mass 162.If now piston 159 is exerted pressure, then it makes the parts 150 of clutch 134 no longer be subjected to the impacting force and the cut-off clutch 134 of hold down gag 108, the result is transmitting torque again, thereby, hold down gag 108 releases, it must only apply a very little pressure for this reason and come cut-off clutch 134 or make it to keep off state.Under clutch 134 disconnection, between the conical surface 156,157, leave one slit 163, as shown in figure 16.Certainly, replace piston 159 and hydraulic pipe line 160, also other measure can be set, make parts 119 releases and cut-off clutch 134 by these measures.Any means on the shell that parts 119 are supported on whole transmission device all are suitable for.

The characteristics of Figure 13-16 shown device are that especially piston 159 is not driven rotation, therefore, can realize the sealing that cost is more worthwhile.

The advantage of this configuration structure is, inserting clutch does not need the mechanism of adding.In addition, engaging force and transmitting torque are irrelevant and along with moment of torsion increases, because originally with regard to the corresponding hold down gag that is equipped with associatedly.

Device shown in Figure 17,18 comprises a conical friction ring transmission device 201 and a reverse gear 202 of connecting with it respectively.In these embodiments, conical friction ring transmission device 201 itself has essentially identical structure and an input cone 203 is arranged and an output cone 204 respectively, these cone axis are to moving abreast and in setting relative to one another and the slit 206 of friction ring 205 between these cones, as a result, can adjust variable velocity ratio with friction ring 205 positions relevantly.In this embodiment, friction ring 205 is round active cone 203, and driven cone 204 is equipped with driven gear 207.Certainly, according to the difference of concrete form of implementation, also can differently constitute conical friction ring transmission device.

In the embodiment shown in Figure 17, driven gear 207 directly meshes with the parts 208 that the sun gear 209 of a planet train of gearings 210 is housed.An epicyclic train 211 that has a sun gear 212 is also arranged in structure shown in Figure 180, and this sun gear is driven by driven gear 207.This realizes by a drivign belt 213 and the gear 214 with sun gear 212 around the movement.As drivign belt 213, belting that all are known or Transmitted chains device can adopt, by these Transmitted chainss or belting, and the power transmission of the safe enough that guaranteed continuously to work together.

Two epicyclic trains 210,211 have

planetary pinion

215 or 216 respectively, their on the one hand with separately

sun gear

209 or 212 engagements and on the other hand with separately external gear 217 or 218 engagements.

In the embodiment of Figure 17, external gear 217 directly links to each other with the support 219 of the around the movement of a differential mechanism 220.Thus, in this configuration structure, epicyclic train 210 and and then reverse gear 202 be located immediately on the differential mechanism 220.Therefore, this configuration structure be proved to be structure very compact and efficient very high because the driving component quantity in driving the path has reduced.Certainly, reverse gear 202 that is set directly on the differential mechanism 220 also can be with all the other features of the present invention irrespectively because of compact structure but very favourable.In addition, the commutation that its driven gear 207 directly determines with layout reason conical friction ring transmission device that the output gear of the input gear engagement of a reverse gear and this reverse gear directly is connected with the support of the around the movement of a differential mechanism and highly beneficial to the general automobiles motor, this is because such layout is only required driving component seldom and therefore had very high efficient.

And in the embodiment of Figure 18, external gear 218 and 221 engagements of driven gear and around the movement thereupon, this driven gear engage with the support 222 of the around the movement of a differential mechanism 223 again.Jue Ding commutation compensates by belting 213 thus, and wherein in the embodiment of Figure 18, reverse gear is arranged on the jack shaft 224 or around the jack shaft.Arrange directly that with the cloth that Figure 17 proposes the layout on the differential mechanism 220 compares, the advantage that is arranged in the structure on the jack shaft 224 is that the general arrangement of Figure 18 can design on space layout more neatly.Especially the surrounding environment to such is favourable for this, promptly under this surrounding environment, limits the spatial depiction that is close to differential mechanism by the 3rd parts.Certainly, reverse gear is arranged in (the especially commutation of this decision of reason) irrespectively is favourable with further feature of the present invention also on the jack shaft 224.When conical friction ring transmission device should be used with the external motor with counterturn, the latter especially was suitable for.In these cases, can abandon belting 213 and gear 207 and gear ring 214 engagements.In addition, it may be favourable that driven cone 204 is arranged on the axle 224, thereby can abandon independently a driven gear 207 and a belting 213 fully.

In addition, those skilled in the art can know directly that driving can begin not to be from the driving of conical friction ring transmission device 201 to be undertaken by

sun gear

209 or 212, but by external gear 217 or 218 or other driving component by reverse gear carry out.The driving of reverse gear is also not necessarily carried out through external gear 217 or 218.Exactly, also can adopt sun gear or other driving component for this reason.

In order to make the embodiment's work safety ground shown in Figure 17,18 keep it " to advance " or " falling back " state, be respectively equipped with fixing device, driving component with exactly be one in these embodiments and can rigidly fix with fixing device around the

support

225 or 226 of motion with the planet gear ring and to be in the same place,

planetary pinion

215 or 216 in described support upper support.In addition, such fixing device is arranged, promptly they can realize the interfixing of two driving components of each epicyclic train 210 or 211.In this case, planetary pinion 216 supports 226 of sun gear in the embodiment of Figure 17 209 and external gear 217 and external gear in the embodiment of Figure 18 218 and around the movement selectively interfix.

In order to be fixed on driving component on the shell or to fix with each other, can adopt various fixing device such as clutch, inertia brake or synchronizer.Just be provided with wherein three for example in the embodiment shown, wherein, according to concrete requirement, these fixing devices can successfully be changed.

In the embodiment of Figure 17, planetary pinion 215 supports 225 are fixed by an electromagnetic brake 227, and this break can be braked a spragging gear 228 selectively, and this spragging gear meshes with planetary pinion 215 supports 225 again.Therefore, turn to, then start break if in this layout, will change, the result, according to the degree that support 225 relative sun gears 209 and external gear 217 slow down, output terminal travel or rotating speed successively decreases, finally stopping and change subsequently up to it turns to.

The fixing of external gear 217 and sun gear 209 realized by a break 229, wherein, planetary pinion 215 phase external gear wheels 217 and sun gear 209 is fixed.Because epicyclic train 210 loses under this state and turns round minimumly, so, this forward gears that is chosen as in the best state, here, can find out obviously that the break corresponding to break 229 also can be arranged between support 225 and sun gear 209 and/or the external gear 217.Just can be enough to make epicyclic train 210 itself correspondingly to stop and around the movement as a whole as long as prevent that planetary pinion 215 from rotating relative to support 225.

In the embodiment of Figure 18, realize selectable fixing by a synchronizer 230, by this synchronizer, be equipped with planetary pinion 216 and thereupon together the support 226 of around the movement selectively with external gear 218 or a relative fixed gear 231 by synchronously, this fixed gear is fixed on the shell 232 in this embodiment.Thus the mechanism of action of Chu Xianing corresponding to as the mechanism of action described in conjunction with the embodiment of Figure 18, here, it is synchronous that support 226 obviously also can external gear 218, rather than with sun gear 212.

The infinitely variable speed transmission of Figure 19 element has an input cone 301 and two output cones 302,303, and they are connected with input cone 301 by the friction ring 304,305 that moves around output cone 302,303 separately respectively.By friction ring 304,305 is moved along the slit of staying between the cone 301,302,303, the branch's

driving mechanism

306 or 307 that can step-less adjustment constitutes by cone 301,302 or 301,303.

At output terminal, these two branch's driving mechanisms 306,307 or these two output cones 303,302 are received on the output shaft 309 by a total moving driving mechanism 308.In the embodiment shown in Figure 19, always moving driving mechanism 308 comprise one comprise an external toothing 311, planetary pinion 312 and a sun gear 313 epicyclic train.External toothing 311 firmly is connected with another gear ring 314, and another gear ring 314 meshes with a small gear 315 again, and this small gear is arranged on the driven shaft 316 of cone 303.Sun gear 313 also firmly is connected with a gear 317 and around the movement thereupon, and this gear meshes with a small gear 318 again, and this small gear is arranged on the driven shaft 319 of cone 302.In addition, a plurality of planetary pinions 312 are bearing in the support 320, this support connect with driven shaft 309 and with driven shaft 309 and planetary pinion 312 around the movement.Therefore, provide a total moving transmission to record a demerit 308, wherein the rotating speed of small gear 315,318 or driven cone 302,303 is summed into total rotating speed of axle 309 according to the position of velocity ratio and friction ring 304,305.Preferably so select velocity ratio, promptly on the same position of friction ring 304,305 in other words under the same rotational speed of these two driven cones 302,303, planetary pinion 312 under the rotation of 320 li on support stops and only with external toothing 311 and sun gear 313 around the movement together.So, reduced the loss in the continuous running.In addition, a clutch 321 is used to reduce the loss, driven shaft 309 directly is connected with this clutch or is connected with active cone 301 by a speed changer according to specific embodiment, thereby especially under high more uniform rotating speed, can these two branch's driving mechanisms 306,307 of tap, wherein under above-mentioned speed, this just can't utilize the advantage of an infinitely variable speed transmission and such infinitely variable speed transmission to cause undesirable loss.

As directly seeing, always moving driving mechanism 308 is added up the rotating speed of these two cones 302,303 and is played the effect of the torsion balance that is used to act on the moment of torsion on this cone 302,303.

Therefore embodiment shown in Figure 20 corresponds essentially to the embodiment of Figure 19, acts on identical parts and also represents with same tag and abandoned being repeated in this description identical function.Not in the scope of embodiments of Figure 19, the embodiment of Figure 20 has a fixed clutch 322 on the one hand, can be fixed on the external toothing 311 by the support 320 of this fixed clutch the around the movement of planetary pinion 312, on the other hand, it also has a clutch 323, this support 320 and driven shaft 309 can by this clutch be fixed on that a time prestige is not shown specifically and fixed clutch housing on.First clutch 322 is used to force planetary pinion 312 stopping rotation under certain operating mode, thus avoided the loss that planetary pinion 312 brings and make shell 320 and axle 309 with external toothing 311 and sun gear 313 around the movement.Second clutch 323 is used for fixed-site ground but can keeps planetary pinion 312 around self rotational ground.This structure especially is provided for uniting use with a transmission device, and wherein this transmission device is like this design, i.e. external toothing and sun gear 313 around the movement or oppositely detour oppositely.This for example can be by additional realizing between the gear of centre or by the reverse gear in the drive path between one of them branch's driving mechanism 306,307 and total moving driving mechanism 308 subsequently.In such layout, always moving driving mechanism 308 is controlled like this by these two branch's driving mechanisms 306,307, promptly on axle 309, caused zero rotating speed, although initiatively cone 301 is being rotated.Under this state, clutch 320 can be used to the fixed conveyor device.In such layout, only by regulating friction ring 304,305 or just can realizing the starting of driven shaft 309 by regulating branch's driving mechanism 306,307.

Device shown in Figure 21 corresponds essentially to the device of Figure 19.At this point, branch's driving mechanism 307,306 is identical in these two devices.In the device of Figure 21, have only total moving driving mechanism 308 have with device shown in Figure 19 in different structures.Therefore, specific descriptions have also been abandoned here to same composition part and function thereof.

In infinitely variable speed transmission shown in Figure 21, driven shaft 309 directly is connected with the external toothing 324 of a planet train of gearings and around the movement therewith.In addition, planetary pinion 312 is bearing in the support 325, this support is with planetary pinion 312 and a gear 326 around the movement, wherein this gear 326 and 315 engagements of the small gear on the driven shaft 306 of cone 303, and sun gear 313 is as engaging this gear and 318 engagements of the small gear on cone 2 driven shafts 319 like that with a gear 317 in the embodiment shown in Figure 19,20.

Therefore, driving mechanism 308 shown in Figure 21 has also played the effect of total moving driving mechanism and with the rotating speed addition of these two branch's driving mechanisms 306,307 or subtract each other.

Device shown in Figure 22 also is being equal to the device shown in Figure 19-21 aspect branch's driving mechanism 306,307.Basically the structure of having only driving mechanism 308 is different.Here, always moving transmission is recorded a demerit and 308 is driven by the bevel gear on the driven

shaft

316 or 319 that is placed in

cone

303 or 302 respectively 327 or 328.For this reason,

bevel gear

327 or 328 and

bevel gear

329 or 330 engagements,

bevel gear

329 or 330 engage with the bevel gear 331 or 332 of the fixed-site of differential mechanism ground around self rotational again.The output terminal of the transmission device of Figure 22 is finished by a gear 310, and this gear is connected with the bevel gear 333 of the around the movement of differential mechanism or 334 thrust bearing, these bevel gears again with the bevel gear 331 of differential mechanism or 332 engagements.As shown in the figure, also provide a total moving driving mechanism by such layout.

The embodiment's of Figure 23 basic structure is corresponding to the embodiment of Figure 22, and therefore here, always moving driving mechanism 308 is made of a differential mechanism 335, and it drives driven shaft 309 with a driven gear 336 and by a bevel gear 337.In addition, driven gear 336 and a bevel gear 338 engagements, this bevel gear is connected with active cone 301 by a synchronous clutch 339 again, and the result can come these two branch's driving mechanisms 307,306 of tap as required.In addition, in this layout, the driven shaft 316,319 of driven cone 302,303 is selectively received on bevel gear 342,343 or 344,345 by synchronous clutch 340 or 341, they mesh with bevel gear 346 or 347 again, and bevel gear 346 or 347 is connected with the bevel gear around a fixed axis around the movement of differential mechanism respectively.Therefore,, can change effectively turning to of branch's driving mechanism 306,307 simply by clutch 340 or 341, the result, the transmission device of Figure 23 has most diverse transmission conditions.

Certainly, the ring of conical friction shown in replacement transmission device 306,307 ground, also can be advantageously with other infinitely variable speed transmission as branch's driving mechanism of infinitely variable speed transmission of the present invention.Shown in Figure 19-23, the branch's driving mechanism 306,307 that is limited by the cone axis separately 348,349,350 that is orientated in parallel to each other respectively has branch transmission plane, and described branch transmission plane is all in drawing.So, this transmission device the most flat structure is arranged and be particularly suitable to be used in lorry or jubilee wagen in because they for example can be installed in a pressurized machine below.Because transmission device of the present invention is because of adopting two branch's driving mechanisms also can be under the situation of high moment of torsion, as under the situation of the high moment of torsion that obtains by modern diesel engines, work expeditiously, so such ability is useful all the more, because can avoid very high impacting force by adopting two branch's driving mechanisms.

As according to ground as described in the explanation of Figure 19-22 and the embodiment and for example in conjunction with ground as described in the embodiment of Figure 23, can obviously influence the characteristic of always moving driving mechanism by select these two branch's driving mechanisms 306,307 act on turning to of total moving driving mechanism 308 thereupon.Especially, the driving component that turns to of reverse gear or change is favourable to this.In Fig. 8, for example described one and replaced form of implementation for above-mentioned branch driving mechanism.

Certainly, in the transmission device shown in Figure 19-23, also can select the power transmission line on the contrary, thereby output member 309,310 is as input component, input cone 301 is as the output cone.

Claims

1. conical friction ring transmission device that has stepless adjustable branch's driving mechanism, the drive path that it is characterized in that at least two parallel connections, wherein, this stepless adjustable branch's driving mechanism is arranged in article one drive path in these two drive path, these drive path can be converted selectively by a transmission components (3), this stepless adjustable branch's driving mechanism is arranged on two power dividers (41,42) between, wherein, at least one input end of this stepless adjustable branch's driving mechanism effectively is connected with at least one output terminal of the power divider of an input end, and at least one output terminal of this stepless adjustable branch's driving mechanism effectively is connected with at least one input end of the power divider of an output terminal, is provided with a reverse gear and one first grade or an overdirve gear in the second drive path of these two drive path.

2. conical friction ring transmission device as claimed in claim 1 is characterized in that, described power divider (41,42) is differential drive portion or planetary pinion based part.

3. conical friction ring transmission device as claimed in claim 1, it is characterized in that, at least one forward gears and at least one reverse gear realize by a differential drive portion (23), wherein, at least one parts of this differential drive portion selectively are fixed together with another parts of this shell and/or this differential drive portion.

4. conical friction ring transmission device as claimed in claim 1, it is characterized in that, the output terminal of these two drive path is so interrelated, promptly before one from these two the speed change gears gearshift procedure of changing to another, carry out the coupling of the rotating speed of first drive path by the rotating speed of this stepless adjustable speed-changing transmission device and second drive path.

5. as claim 1 or 4 described conical friction ring transmission devices, it is characterized in that second drive path comprises a differential drive portion (23).

6. as claim 1 or 4 described conical friction ring transmission devices, it is characterized in that it has one the 3rd drive path, the 3rd drive path can be converted by one second transmission components and/or by a freewheel.

7. as claim 1 or 4 described conical friction ring transmission devices, it is characterized in that this stepless adjustable driving mechanism (1) is connected with a pump impeller (21) of one three wheeled fluid torque converter (20) this transmission components (3) and this second speed change gear (2) connects with a turbine (11) of this three wheeled fluid torque converter (20).

8. conical friction ring transmission device as claimed in claim 1 is characterized in that, is provided with an input shaft (53) and an output shaft (50) that a coaxial line is arranged.

9. conical friction ring transmission device as claimed in claim 8 is characterized in that, is provided with a differential drive portion (59) in the output shaft (50) of coaxial line, and it is driven by an output shaft (56) of this infinitely variable speed transmission.

10. conical friction ring transmission device as claimed in claim 1 is characterized in that, is provided with a Vidacare corp that is used for stepless adjustable branch's driving mechanism.

11. conical friction ring transmission device as claimed in claim 2 is characterized in that, is provided with the friction disk mechanism in a bonding point, a hydraulic coupling or a synchronizer at output terminal.

12. conical friction ring transmission device as claimed in claim 11 is characterized in that, described bonding point is a starting clutch or a torque-converters.

13. conical friction ring transmission device as claimed in claim 2 is characterized in that, is provided with a bonding point, friction disk mechanism, hydraulic coupling or a synchronizer (3) at input end.

14. conical friction ring transmission device as claimed in claim 13 is characterized in that, described bonding point is a starting clutch or a torque-converters (three wheeled fluid torque converters).

15. conical friction ring transmission device as claimed in claim 2 is characterized in that, these two branch's driving mechanisms (1,2; 101,102) respectively with its output terminal (26,126; 29,129) concentrate on an input end (27 of next speed change gear (15,115); 127) go up or engage.

16. conical friction ring transmission device as claimed in claim 15 is characterized in that, the input end of this next speed change gear (127) is the main differential mechanism (115) of an automobile.

17. conical friction ring transmission device as claimed in claim 15 is characterized in that, these two branch's driving mechanisms (1,2; 101,102) can insert or disconnect respectively.

18. conical friction ring transmission device as claimed in claim 1, wherein the driving component of at least two rotations on different axles is strained relatively by a hold down gag, it is characterized in that, be provided with a clutch piece (134), these two driving components (104,105) by this clutch piece selectively the disconnection by clutch piece (134) and with one the 3rd driving component (115,129) separately or by the access of clutch piece (134) with the 3rd driving component (115,129) link to each other, this clutch piece is access in by the impacting force that is applied by this hold down gag (108).

19. conical friction ring transmission device as claimed in claim 18 is characterized in that this clutch piece (134) comprises a cone clutch (156,157).

20. conical friction ring transmission device as claimed in claim 2, it has one and is arranged on output terminal (204) reverse gear (202) afterwards and that connect with this infinitely variable speed transmission (201).

21. conical friction ring transmission device as claimed in claim 20, it is characterized in that, this reverse gear comprises a transmission bracket (225 that has at least one around the movement, 226) epicyclic train, this bracket supports at least one driving component (215 of this epicyclic train, 216) and selectively with the driving component (209,217 of a fixed support (227,232) or an around the movement; 212,218) be fixed together.

22. conical friction ring transmission device as claimed in claim 21, it is characterized in that, reverse gear (202) comprises that has a planetary pinion (215,216), sun gear (209,212) and external gear (217,218) epicyclic train (210,211), one of them first driving component effectively links to each other with the output terminal (207) of this conical friction ring transmission device (201), one second driving component and output terminal (220 by the general arrangement of this conical friction ring transmission device (201) and this reverse gear (202) formation, 223) effectively link to each other, and relative support of the 3rd driving component or shell (227,232) are fixed aspect degrees of freedom at least.

23. conical friction ring transmission device as claimed in claim 22 is characterized in that the 3rd driving component is a plurality of planetary pinions.

24. conical friction ring transmission device as claimed in claim 23 is characterized in that, this first driving component is driven by a small gear (207) of accompanying or follow mantle body around the movement.

25. conical friction ring transmission device as claimed in claim 23 is characterized in that, the support (219) of the around the movement of second driving component and a differential mechanism (220) is conjointly around operation.

26. conical friction ring transmission device as claimed in claim 23 is characterized in that, two driving components wherein, and promptly first and second driving components can be fixed with each other.

27. conical friction ring transmission device as claimed in claim 21 is characterized in that, uses a clutch (229), an inertia brake (227,228) and/or synchronizer (230) in order to fix.

28. conical friction ring transmission device as claimed in claim 1 is characterized in that, is provided with two stepless adjustable branch's driving mechanisms (306,307), they are received on an input component or the output member (309,310) by a total moving driving mechanism (308).

29. conical friction ring transmission device as claimed in claim 28 is characterized in that, these two stepless adjustable branch's driving mechanisms (306,307) have a common driving component (301) in that side back to total moving driving mechanism (308).

30. conical friction ring transmission device as claimed in claim 28, it is characterized in that, these two stepless adjustable branch's driving mechanisms (306,307) an input shaft axis (249) and an output shaft axis (348 that is arranged in abreast substantially with it in the branch transmission plane are arranged respectively, 350), wherein said branch transmission plane is arranged in parallel to each other.

31. conical friction ring transmission device as claimed in claim 30 is characterized in that, these two branch transmission planes are identical.

32. conical friction ring transmission device as claimed in claim 28 is characterized in that, these two branch's driving mechanisms have a common input shaft (301,349) or a common output shaft (309).

33. conical friction ring transmission device as claimed in claim 28 is characterized in that, at one of them stepless adjustable branch's driving mechanism (306,307) and between this total moving driving mechanism (308) be provided with another adjustable branch's driving mechanism (321,339,340,341).

34. conical friction ring transmission device as claimed in claim 33 is characterized in that, described another adjustable branch's driving mechanism (321,339,340,341) is a speed changer or a reverse gear.

35. conical friction ring transmission device as claimed in claim 28 is characterized in that, one of them stepless adjustable branch's driving mechanism (306,307) can tap.

36. conical friction ring transmission device as claimed in claim 28 is characterized in that, this always moving driving mechanism (308) has at least one can securing driving component (312,320).