DE102011120904B4 - Method and device for expanding the tractive force of a motor vehicle driven by a piston engine - Google Patents

Abstract

Method for the expansion of the tractive force of a motor vehicle driven by a piston engine, in which the exhaust gas flow discharged from the engine flows into a turbine in order to deliver its energy to an impeller of a drive suitable for the expansion of the tractive force of the motor vehicle, characterized in that the energy the turbine is transferred to a pair of non-reciprocating engine driven vehicle wheels via a transfer case to form an additional, intermittent secondary drive, the deployment of which is electronically controlled, and the operation is electronically controlled.

Description

The invention relates to a need for increasing the tensile force of a single-axle driven vehicle.

More particularly, the invention relates to a method and apparatus in which the exhaust gas flow discharged from the engine flows into a turbine to deliver its energy to an impeller of a drive suitable for expanding the tractive effort of a motor vehicle.

The book by Buschmann / Koesseler "Handbook of Automotive Engineering", Wilhelm Heyne Verlag, born in 1976, Volume 1, pages 436 to 438 describes a method and apparatus for the expansion of engine performance thus the traction of the motor vehicle as a whole. The device described therein constitutes a turbocharger, in which the exhaust gas flow discharged from the engine flows to a turbine in order to deliver its energy to an impeller which drives this device.

The publication JP 2007-321 754 A also describes a device for recovering energy from the exhaust gas of an internal combustion engine in a motor vehicle. It is envisaged to arrange a power turbine in the exhaust region of the internal combustion engine, which selectively drives a generator for generating electrical energy or emits mechanical energy to the output shaft of the internal combustion engine.

A device for energy recovery in an internal combustion engine is also from the document US 4 774 811 A known. One in the exhaust region of the internal combustion engine drives a generator for generating electrical energy.

These known methods and devices have the disadvantage that only part of the exhaust gas energy is utilized for the expansion of the vehicle traction. A higher proportion of it goes outdoors and is lost. Another disadvantage is that even the exploited energy is not delivered directly to the vehicle wheels, but via the engine and the energy consuming change gear.

The invention is based on the object, a device and a method to create so that it avoids the disadvantages mentioned above.

The method according to claim 1 and the device according to claim 4 solve this problem. Advantageous features further develop the subject invention and are each contained in the subclaims. These will now be referred to.

According to the present invention, a self-regulating drive system is created, which actively controls itself in the intensity of its effect and in which a secondary drive is developed intermittently as a function of the exhaust gas flow intensity. This is achieved by transferring the energy of the turbine to a pair of non-driven vehicle wheels via a transfer case. The higher the engine load, the stronger the effect of the secondary drive.

According to a further aspect of the present invention, the use of the secondary drive in the effect, especially when driving through difficult terrain with high driving resistance heavily loaded vehicles designed, with its operation is electronically controlled.

This represents a significant advantage over the prior art, because a conventional uniaxially driven vehicle thus receives additional forces needed to overcome the driving resistance. The wheels of his passive-running axle are actively driven with. In this case, the operation of the vehicle unfolds due to the intermittent starting of the secondary drive in the manner of a four-wheel drive vehicle.

According to a further aspect, an electronic control unit is provided which, depending on the driving characteristics, precisely aims at the speed ratio between the wheels driven by the engine gearbox and those driven by the exhaust gas flow with which the engine power can be optimally utilized.

Furthermore, the ride comfort is increased. The involvement of the secondary drive the hearing of the occupants is spared, because the noise from the howling engine z. B. becomes acoustically spongier when starting on the mountain and the driver applies less force to the accelerator pedal. In addition, the destination could be reached in less time if the current motor vehicles are equipped according to the invention. This is explained by the fact that the high speed can be developed faster and the average speed when driving through difficult roads and tracks can be increased.

Another advantage of the device and the method according to the invention is the fact that according to these the possibility of driving fuel-saving, if not only the fuel itself is consumed for the propulsion of the vehicle, but his burned out of the engine exhausted remainder ,

According to a preferred aspect, it is provided that the drive system according to the invention is designed to be compatible for use in the uniaxially driven vehicles of all kinds and can be inexpensively manufactured and retrofitted to the conventional motor vehicles due to the simplicity of its construction.

Further advantageous features and embodiments are contained in the subclaims.

According to one embodiment of the invention, the device is realized in a construction which, due to its design, is uncomplicated in handling and maintenance. In this embodiment, a turbine transmitting torque is received with a surface of the wheels far away from the axis. Such an embodiment has the effect of amplifying the effect of the secondary drive.

Further details of the invention will become apparent from the following detailed description and the accompanying drawings, in which preferred embodiments of the invention are illustrated by way of example.

1 shows a construction diagram of a preferred embodiment of the device, which explains its structural design.

2 shows a construction diagram of another embodiment of the device for explaining its structural design.

3 is an enlarged view of a portion of the scheme of 1 and 2 showing the partial section of the turbine and a connection to a rotary valve, the pressure lines are shown broken off.

4 is one of the 5 corresponding section through the kinked plane "DD", which shows an embodiment of the device in its initial position, wherein the vehicle wheel is cut off and the waves and the representation of the device are shown broken off to the left of their symmetry axis to save space.

5 is one of the 4 corresponding cross section through the plane "AA", which shows the device in the moment of use in action and explains their suspension to the motor vehicle.

6 represents one of the 5 corresponding side view in the direction indicated by the arrow "C", which further describes the construction of the device.

7 shows one of the 6 corresponding in the vicinity with "I" view, which explains the structure of the housing of the rolling devices.

8th is one of the 5 corresponding horizontal section through the plane "BB".

In this case, the connecting elements of the device are represented in most cases to simplify the representation by their axial lines.

According to the 1 as well as the 2 and 3 For example, the device has a turbine located in the center of the structure 1 on. Like it out 3 is apparent, the turbine is in its illustrated construction with three on its shaft 2 attached paddle wheels 3 equipped, which is the shaft 2 in rotation. The turbine is with its end over a pipe 4 a rotary valve 5 to the exhaust pipe 6 connected to the motor vehicle. In 3 is also the lead 7 to see, which is used for the removal of the currently set by the rotary valve currently excess amount of gas.

The operation of the turbine and its construction are known from the flow technique.

At the other end, the turbine points on its shaft 2 generally assembled with 8th designated transfer case, which serves to redirect the forces generated by the turbine in the form of the drive torque in the direction of the vehicle wheels by 90 °. For this purpose, the transfer case is a toothed gear whose gears are conical in which the shaft 2 acts as an input shaft. It stands on the free end of the shaft 2 attached gear 9 with two similar relatively small gears 10 , which are on the free ends of the arranged symmetrically to the central axis of the device output shafts 11 are always in engagement. The pencils 12 fix an unchanged position of the gears on the shafts.

According to the structural design of the device of 2 , a direct connection of the transfer case with the vehicle wheels is made, in which the output shafts 11 of the transmission 8th at the same time the axes of the non-driven vehicle wheels 13 are. The drive torques from the transfer case are delivered axially to the axles of the vehicle wheels.

In contrast to this embodiment, the embodiment of FIG 1 and 4 to 8th an indirect connection of the transfer case with the vehicle wheels. Here is the transfer of forces with the use of a general with 14 designated rolling device provided, which integral with a serving as a coupling element propeller shaft 15 with the output shaft 11 of the transfer case 8th connected is.

The rolling devices 14 are set up by the turbine 1 produced drive torques on the non-driven wheels 13 of the vehicle tangentially. This embodiment is characterized by its higher efficiency compared to the first.

Furthermore, the transfer case 8th also serve as an amplifier in the sense that are translated high by transmitting the forces. In particular, this applies to a worm gear (not shown) when used in place of the gear train, when on the turbine shaft 2 a worm is placed and the output shafts 11 be connected with a worm wheel.

To the compiled parts of in 4 shown construction of the rolling devices to better recognize the walls of their housing 16 blackened and an inserted insert 17 as well as the role 18 hatched, the roller bearing 19 as well as the vehicle wheel 13 are shown unshaded. In addition, the vehicle wheel is shown without tires.

As it is from the 4 and 5 indicates the rolling devices 14 the Reibradgetriebe which integrally formed for the purpose of fulfilling their tasks, three in the housing 16 having mounted engaged with each other conical rollers. Each rolling device is through the shaft 20 a roll placed in the middle 21 with one at a nahliegendem end of the cardan shaft 15 existing cones 22 Connected and acts as one more two roles 18 driving role. The two roles 18 impart the force transfer to the vehicle wheels as they approach the mentioned wheels through engagement with the rolling means until engagement, thereby acting as constraining rollers.

For such interventions, a part of its body, which is the outer wall, is selected on the vehicle wheel driven by each of the secondary drives 23 an inner oblique shoulder 24 designed surface represents. This surface has in today's most common embodiment a tilted at 5 ° to the center of the wheel contour. Accordingly, the coats of constraints 18 as well as the role 21 one of these contour equal inclination added to adapt to each other and thus to allow a full power transmission to the attacked wheel surface. This can be seen from the 4 and 5 remove.

To achieve the said adjustment properly, the roles are 18 flexibly mounted in the housing and in their positions in the housing 16 relative to the role 21 arranged so that when the full rolling of the rolling devices to the vehicle wheels a functionally appropriate voltage between all affected components is ensured.

For this purpose, there is the housing 16 of two parts, which are used as front 25 and tail parts 26 are formed, in which the insert 17 the roles are separated from each other. In this case, the housing and the insert form three circular surfaces, which are valid as a socket for the bearing of the rollers. In addition, the distances between the axes of said circles are dimensioned and tolerated under the conditions described above. So the role is nested 21 in the insert 17 through the roller bearing 19 one and the wave 20 is to form a joint for flexible mating of their roles 21 with the wheel surface 24 and at the same time with the roles 18 in the form of a sphere 27 educated. In this case, each ball between the hemispherical surfaces formed on the in the insert 17 nested two cushions 28 kept three-dimensionally rotatable.

The connecting elements 29 some both editions, as in 4 and 5 is illustrated. In addition, the balls 27 with the body of the roles 18 for ease of assembly by means of screws 30 rigidly connected. This is in 4 seen.

Furthermore, the more flexible design helps the positional error of the roles 18 , which can occur both in the manufacture and in the function of the device to prevent.

For the composition of the front and rear parts of the housing 16 These are the triangular flanges formed at their common contact surfaces 31 provided and the front part 25 of the housing contains a hole 32 and a recess formed for the head of a screw (not shown) 33 , In addition, the tail section 26 with a hole 34 formed, which is crimped to form a thread. To this goal is also the insert 17 with a through hole 35 provided by which the screw is carried out for their connection with the thread, as this 5 to 7 clarify. The two other screws 36 , which at the same time the housing with a generally with 37 connect designated holders also impart compositions made.

The holder 37 is from two plates 38 and a pressure plate placed on top of it 39 constructed, which are welded together. Here is the distance between the plates 38 given a measure of the strengths of the two flanges 31 of housing 16 is the same, how 6 and 8th further clarify.

Next are the cardan shafts with their other ends through the pins 40 with the output shafts 11 connected. In addition, each of the two pins contains 22 and 40 a pipe neck inseparable from him 41 , through which the cardan shaft comes to the clutch.

For the journal 22 serves the pipe socket as a spacer sleeve, by their connection with the guided through the housing shaft 20 the role 21 have a protruding over the housing part of this. Therefore arises between the pin and the housing a distance that allows an unlimited rotation of the pin. The assembled components are against relative axial displacement by the on the shaft 20 inserted snap ring 42 secured.

For the journal 40 serves the pipe approach 41 as a sliding sleeve, which at the functional stroke or return stroke of the blank holder, the sliding the pin and the cardan shaft 15 as a whole along the output shaft 11 , because of the engagement / disengagement of the rolling devices enabled. This is the cones 22 in one piece over the pipe socket with the output shaft 11 by means of a guided through these two pins 43 coupled and the output shaft is at the coupling point with an axial slot 44 trained to the pen 43 guaranteed a game to slide. As it is based on the 4 is explained.

The rolling means are mounted on the vehicle frame and arranged there so that their constraining rollers have a position within easy reach of the edge of the vehicle wheel. In this way, the vehicle wheels are attacked tangentially by the use in effect of the secondary drive. Consequently, an imaginary lever (the distance between the line of action of the attack forces and the wheel axis), which causes the tangentially directed forces to rotate. In this case, the amount of drive torques received by the vehicle wheels is multiplied high. It is envisaged that the distance from the rollers 18 to their career on the vehicle wheels at the starting position of the rolling devices for the fastest possible contact structure is about 0.5-1.0 mm. The hold of this value is always checked by the control unit. This is described below.

According to the in 5 featured embodiment of the device are the rolling devices with two constraining rollers 18 fitted. This amount represents a least number to reduce the specific pressure on the wheels.

Next are the roles 18 and 21 the rolling devices 14 as well as those with the roles 18 dedicated interface 24 the vehicle wheels 13 as a friction partner for their permanent use made of the friction-resistant materials or covered with a seal-resistant layer.

-förmigen Tragprofil 45 ausgestattet ist, auf dem die allgemein mit 46 bezeichneten Niederhalter montiert sind, welche einstückig zum Aufbau eines Kontakts mit den Wälzeinrichtungen oben anliegend an diesen untergebracht sind, um durch den von ihm erzeugten Krafthub eine kraftschlüssige Verbindung zwischen den Zwängensrollen 18 der Wälzeinrichtung und den Fahrzeugrädern 13 zu bilden, bestehend aus einem in kontinuierliche Berührung mit der Druckplatte 39 des Halters 37 angebrachten als Spanner dienenden Nocken 47 und einem ihn betätigenden Elektromotor 48, auf dessen Welle dieser aufgesetzt ist.In 4 to 6 It can be seen that the vehicle for receiving the device with a welded to the vehicle frame

-shaped support profile 45 is equipped on which the generally with 46 designated hold-down are mounted, which are integrally housed to form a contact with the rolling devices abutting against this, in order by the force stroke generated by him a frictional connection between the constraining rollers 18 the rolling device and the vehicle wheels 13 consisting of one in continuous contact with the pressure plate 39 of the owner 37 attached as a tensioner serving cam 47 and an electric motor actuating it 48 on whose shaft this is put on.

In order to ensure a continuous contact with the hold-downs, the rolling devices are 14 in one piece at the point of the supporting profile, where the hold-down 46 are arranged suspended from the same. In addition, the pressure plate 39 of the owner 37 with a same made of the friction-resistant fabric edition 49 covered. The connecting means which the pressure plate 39 with the edition 49 holds together is not shown.

Said suspension takes place for each individual rolling device by means of two return springs 50 , with both their ends on the eye bolts 51 are hooked on the one hand on the holder 37 and on the other hand on the supporting profile 45 are anchored. This is from the 5 and 6 recognizable. This will keep the springs 50 the hold down 46 to the rolling devices 14 until stop, to keep a contact between the two under bias. In this case, the return springs endeavor to transfer the rolling devices, when they are released by the pressure of the blank holder, in their initial positions.

For their guided shift are the Wälzeinrichtungen 14 equipped with the guide elements. The columns 52 and jacks 53 are there for the posture of the columns provided sleeves 54 in the in 8th shown manner on the holder 37 attached to stiffen its construction and the guide bushes 53 are with the profile 45 connected to the vehicle frame.

In order to bring the effect of the additional secondary drive to vote with the permanent drive, a control unit, not shown, is provided, containing sensors for the Detecting the speed ratios between the driven by the engine gear and the exhaust gas flow intermittently with driven vehicle wheels and for measuring the exhaust gas flow intensity, and other sensor elements that represent these parameters to the control unit. In this case, intermittent starting of the secondary drive after detection by the control unit of the sufficient amount of propellant gas flowing through the turbine is initiated.

The control is followed by an adjustable rotary valve connected to the control unit 5 which is set in such a positional position in which the speed ratio between the two vehicle axles is brought to the useful proportionality depending on the exhaust gas flow intensity, or in another case, the secondary drive is switched out of operation. In the latter setting, the exhaust gases are usually through the line 7 let out into the open and you can drive with pure front or rear drive.

The control of the engagement process of the rolling devices 14 is from the electric motors 48 due to the signals picked up by the sensor elements that turn it on, pause, or switch / switch off.

Furthermore, it is provided that the control unit also contains sensors which are responsible for the continuous monitoring of the correctness of the output positions of the rolling devices. This is important in the case when the motor vehicle drives through bumpy roads. In the course of driving through such terrain, the body is constantly exposed to the damping vibrations that the rolling devices 14 in an indefinite relative to the vehicle wheels 13 Situation that lies outside their starting position. What leads to the delay of the use in effect of the secondary drive.

After processing the signals picked up by the aforesaid sensors by detecting the deviation of the home positions of the rolling means from the tolerated limit, the control unit outputs corresponding electrical signals to those for controlling the cams 47 competent electric motors 48 , Wherein these determine the control signals issued by the control unit individual for each setpoint required by the rolling devices, which are most suitable for the positioning of the cams in order to maintain the starting positions. Because of this appropriately timed control signals rotate the electric motors of the cam in such a direction in which the desired positions of the cam abkürztest be reached.

To protect the device from unnecessary or unwanted treatments, the control unit is designed so that even with the extremely intense acting on the turbine gas flow rate, which can occur when the vehicle, due to a game with the accelerator pedals, turning the wheels impossible power.

The control of the secondary drive for the embodiment according to 2 results from the reading of the first embodiment by simplifying the construction and thus limited performance, since the control of the rolling devices is eliminated.

The present method and apparatus for expanding the tractive effort of a motor vehicle equipped with the piston engine operate under certain conditions. This is explained by the fact that the effect of the exhausts exhausted from the engine when driving through normal roads is weak to form a self-propelled drive.

The effect of the exhaust stream becomes more efficient when driving through difficult terrain, especially for the heavily laden vehicles that are supposed to overcome a steeply inclined track. Thus, the engine is heavily loaded and consumes enormous amounts of fuel. This creates a sufficient amount of gas whose flow reaches about three times the speed of switching at high pressure.

Under these circumstances, the turbine becomes 1 , following the command of the control unit, by appropriate adjustment of its rotary valve 5 with the exhaust pipe 6 connected to the vehicle and the electric motors 48 twist the cams 47 , The rolling devices bring their roles 18 in engagement with the vehicle wheels. This results in a closed chain of the cooperating association parts of the device, which allows transmission of the driving forces to the vehicle wheels.

In this way, occasionally develops a intermittent in cooperation with the piston drive secondary drive, which also rotates non-driven vehicle wheels, in which the exhausted from the engine exhaust flow does its service as a drive means. This automatically creates a unique drive system with four-wheel-like handling when needed.

As the vehicle progresses, the control unit actively coordinates the speed ratios between the permanently and intermittently driven wheels. Thus, on a slope when the vehicle is fully loaded, the revolutions of the wheels driven by the engine gearbox slow down, in contrast to this, the revolutions of the wheels driven by the exhaust gas engine accelerate to promote the development of tractive effort. The vehicle uses its power reserve. The lack of traction to overcome the driving resistance without difficulty, gets the vehicle as a subsidy from the secondary drive, which covers the power deficit with very intense effect.

This partially relieves the engine and, as a result, the revolutions of the wheels driven by it accelerate. This reduces the amount of gas flowing through the turbine. The control unit determines useful proportions of the speed ratios of the wheels from both axles or maintains the speed compensation and thus varies the settings of its rotary valve 5 , The excess for the optimum proportionality of the amount of gas is determined by the appropriate adjustment of the rotary valve 5 separated from the entire exhaust flow and into the open through the pipe 7 omitted.

The pausing of the electric motors 47 means that the current setting of the rotary valve is still up to date. During normal driving the rotary valve locks 5 The administration 4 and that concludes the turbine 1 out of traffic with the exhaust pipe 6 out. The new start of the secondary drive takes place only if a sufficiently strong exhaust gas flow is provided.

In the present invention, it is also possible to drive the motor from the control unit in order to set the variable loading of the turbine in the center of the drive system. In this case, no excess amount of the exhaust gas flow is formed and thereby the fuel is used even more favorably. Subsequently, the efficiency of the drawability of a motor vehicle is increased, which further affirms the advantages of the invention.

Claims (16)

Method for the expansion of the tractive force of a motor vehicle driven by a piston engine, in which the exhaust gas flow discharged from the engine flows into a turbine in order to deliver its energy to an impeller of a drive suitable for the expansion of the tractive force of the motor vehicle, characterized in that the energy the turbine is transferred to a pair of non-reciprocating engine driven vehicle wheels via a transfer case to form an additional, intermittent secondary drive, the deployment of which is electronically controlled, and the operation is electronically controlled. A method of expanding the tractive effort of a motor vehicle driven by the piston engine according to claim 1, wherein the drive torques are transmitted to the vehicle wheels tangentially by a friction gear. A method of expanding the tractive effort of a motor vehicle driven by the piston engine according to claim 1, wherein the drive torques are transmitted axially to the vehicle wheels. Device which is adapted to implement a method according to one of claims 1 to 3, which is an intermittent secondary drive, comprising a turbine driven by exhaust gas flow ( 1 ), a mounted on the common shaft with the turbine transfer case ( 8th ), the 90 ° force redirection at rolling devices ( 14 ), by which recorded drive torques on the wheels not driven by the piston engine ( 13 ) of the vehicle, at least one hold-down device ( 46 ) provided for generating a pressure deliverable to the rolling means and of which the latter is operable, a cardan shaft ( 15 ), which as intermediate shaft the transfer case ( 8th ) with the rolling devices ( 14 ), and an electronic control unit through which the speed ratio between the permanently driven and intermittently driven vehicle wheels can be coordinated. Apparatus according to claim 4, wherein the control unit includes sensors which are suitable for detecting the speed ratios between the driven by the engine gear and the exhaust gas flow intermittently driven vehicle wheels, and for measuring the exhaust gas flow intensity, and further sensor elements that represent these parameters to the control unit, and the control of the use of the secondary drive in action and its operation after the detection of the control unit of the sufficient amount of propellant gas flowing through the turbine can be initiated. Apparatus according to claim 4 or 5, wherein the control unit with a rotary valve ( 5 ), through which the exhaust gas flow into the turbine ( 1 ) is insertable and which is adjustable by the control unit in a position position in which the secondary drive is switched off from the operation. Device according to one of the preceding claims, wherein the control unit is designed with the sensors responsible for the continuous monitoring of the correctness of the output positions of the rolling devices, by means of which the control unit controls the individual sensors for each of the rolling devices ( 14 ) determines respectively required setpoint values which are required for the positioning of the cams ( 47 ) are most suitable to retain the home positions. Device according to one of the preceding claims, wherein the control unit is designed such that even with extremely intense gas flow to the turbine, which can occur when the vehicle is stopped due to a game with the accelerator pedal, the rotation of the wheels can be prevented. Device according to one of the preceding claims, wherein the rolling devices ( 14 ) are a friction gear, comprising integrally substantially each three meshing rolling elements, which are tapered rollers, of which a middle roller ( 21 ) by coupling its shaft ( 20 ) with the cardan shaft ( 15 ) and two more of the role ( 21 ) removable driven rollers ( 18 ), via which the drive torques are transferable to the vehicle wheels, wherein the constraining rollers ( 18 ) for optimal adaptation to the roll ( 21 ) as well as on the attack surface ( 23 ) of the vehicle wheel ( 13 ) to their positions in the housing ( 16 ) are flexibly stored. Device according to one of the preceding claims, wherein the rolling devices ( 14 ) are integrally mounted on the vehicle frame in such positions, in which their constraining roles ( 18 ) in close proximity to the edge of the vehicle wheel to attack them quickly, one with the rollers ( 18 ) dedicated surface on the edge of the wheel to transmit the driving torques to the vehicle wheels tangentially and thereby increase. Device according to one of claims 4 to 10, wherein the hold-down ( 46 ) on the vehicle frame ( 45 ), which are designed to form under the force stroke exerted by these force-locking connection between the vehicle wheels ( 13 ) and the constraints ( 18 ) of the rolling devices ( 14 ) are arranged abutting the latter at the top, consisting integrally of one in continuous contact with the rolling device ( 14 ) attached as a tensioner cam ( 47 ) and an electric motor actuating it ( 48 ). Device according to one of the preceding claims, wherein the contact retention between the cams ( 47 ) from the downers ( 46 ) and rolling devices ( 14 ) by a respective pair of return springs ( 50 ) secured with one of its ends in place of the vehicle frame ( 45 ), where one of the at least one hold-down ( 46 ) and with another end on the rolling device ( 14 ) via a rigidly connected holder ( 37 ) is suspended. Device according to one of the preceding claims, wherein the rolling devices ( 14 ) are formed dimensionally stable and are movably arranged at their seats and by a power stroke by the at least one hold-down in the direction of the vehicle wheels ( 13 ) under the guidance of the guiding elements ( 52 . 53 ) are displaceable. Device according to one of the preceding claims, wherein the distribution gear ( 8th ), in order to achieve a higher power transmission, is designed as a worm gear, wherein the turbine shaft ( 2 ) a worm is placed and the waves ( 11 ) are connected to a worm wheel. Device according to claim 9, wherein the attack surface ( 23 ) of the vehicle wheels ( 13 ), at which the track of the constraining rollers ( 18 ), one on an inner shoulder ( 24 ) of the wheel is designed surface. Device according to one of the preceding claims, wherein for the direct transmission of the drive torque to the vehicle wheels not driven by the piston engine whose axes at the same time the output axes of the transfer case ( 8th ) are.

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