KR20060052706A - Friction ring -type transmision and method for operating such a friction ring-type transmission - Google Patents

Abstract

Disclosed is a pressing mechanism for conical friction ring-type transmissions, which comprises two partial pressing devices (9, 10, 11, 14). The second partial pressing device (14) partly compensates the force applied by the first partial pressing device.

Description

FRICTION RING -TYPE TRANSMISION AND METHOD FOR OPERATING SUCH A FRICTION RING-TYPE TRANSMISSION}

The present invention relates to a friction ring gear having at least two friction wheels radially spaced and a method for operating the friction ring gear, wherein one friction ring is arranged between the friction wheels and one of the two friction wheels Surround the dog.

 This type of gear relates to a continuously variable transmission (CVT), which is described, for example, in documents EP 0 466 113, JP 62-258254, JP 2003-028257, JP 2001-124 163, JP 06- 174 030, JP 06-174028 or U.S. Patent No. 3087348 or U.S. Patent No. 5,184981, U.S. Patent 5094652 or U.S. Patent No. 1 600 974, and toroidal CVT and chain or belt type CVT. A gear member in which one of the gear members surrounds the other gear member or in frictional contact with the two friction wheels has two contact surfaces and the first contact surface of the contact surfaces only contacts the first friction wheel, and the second The contact surface only contacts the second friction wheel. In other continuously variable gears, the friction ring gears are different in that the rotational contact surface of the variable gear member alternately contacts the first and second gear members.

For example, according to a second embodiment of the friction ring gears disclosed in document EP 0878 641A1 or EP 0980993A2, a press device is provided and depends on the torque transmitted by the driven bevel gear of the bevel friction ring gear. The press device constrains the two bevel gears and the friction ring that provides a compressive load that is connected through the two bevel gears and forms a grip around the drive bevel gear. At high torques with the risk of slipping the compressive load is large enough. According to the first embodiment also disclosed in document EP 0980993A2, the compressive load of the press apparatus can be controlled from the outside by the hydraulic cylinder.

According to a problem of the device, the friction ring and the bevel in the friction ring are located when the friction wheel arranged in proximity to the base of the friction bevel gear is located in the friction ring and compared with the position of the friction ring whose radius of the bevel gear is relatively small. The contact surface on the gear is relatively large. Since the contact surface is relatively large, the contact pressure is reduced so that significant sliding occurs on the bevel gear or the friction ring is arranged in a floating state. Particularly when the transmission torque is large, the compressive load is considerable, so that the compressive load is unnecessarily lost at other positions of the friction ring. It is not possible to increase the radius of the friction ring in relation to the pavement space. In addition, since the contact surfaces of the respective gear members rotate on different paths, not only the above problem but also problems with other continuously variable gears arise.

In this regard it is an object of the present invention to provide an improved gear.

For this purpose, according to the present invention, there is provided a friction ring gear having two friction wheels radially spaced, arranged between the friction wheels and surrounding one of the two friction wheels. And the friction wheel and the friction ring are constrained to each other by a press device, wherein the friction ring has a press device having at least two press device parts and a first part of the two press device parts is relative to the second part. It is characterized by having a short response time.

The press device, including two press device parts, can be used in a variety of gears, with one gear member, in particular a friction ring or another gear member utilizing friction in operation, surrounding the other gear member. The gears include the form of rotary gears having gear members that rub against each other.

The entire press apparatus is provided, depending on the position of the friction ring or important variables such as the transmission ratio-compression load which takes into account the excessively proportional compressive load required because the radius difference between the bevel gear and the friction ring surrounded by the friction ring is small. The second press device component can optionally be operated as desired. As a result, the first press device component can be configured fairly simply without failure.

The reaction time of the first press device component is shortly selected so as to respond quickly to impact or the like. It is preferred that a completely mechanical configuration is provided, requiring no reaction time. The press apparatus can be quickly adapted to a temporary change to prevent slipping of the gear members moving together.

According to the above arrangement, the first press device component can be directly operated without a control action as a function of only important variables such as transmission torque. Thus, the first press device component (and consequently the entire press device) can be adapted quickly and reliably to changes in the above parameters that are not impacted or nearly unstable or stable. For this purpose it is not necessary for the first press device component to be optimized for the characteristic curve depending on the variable. The first press device component can suitably respond to impact or unstable action with a very small response time.

The optimum characteristic curve of the whole press apparatus is provided by the second press apparatus part, which second press apparatus part does not need to respond quickly to shock or sudden instability reactions, or the characteristic curve of the whole press apparatus or the second press apparatus. Optimized for component characteristic curves It is advantageous that the second press device component is controlled such that the characteristic curve is best selected. The press device components can be operated by various different variables, which can respond in detail to the respective requirements. In general, the press device can be optimized in the control loop for attenuation of vibrations that reduce the response time, but this property is relatively less important because the first press device component reacts with a relatively small response time.

Specifically, according to the configuration of the present invention, the loss of the gear is considerably minimized. The first press device component is adapted such that the second press device component has a characteristic curve and that the first press device component is optimized for operational safety or safety so as to adequately compensate for the transition from the first press device component and for safety-related transitions of the characteristic curve. Can be configured.

Thus, in order to achieve the above object, there is provided a friction ring gear arranged between the friction wheels and surrounding one of the friction wheels, with at least two friction wheels radially spaced apart from the other features of the configuration. And the friction wheel and the friction ring are configured to each other via a press device, wherein the press device of the friction ring gear comprises at least two press device parts, and the first press device part of the two press device parts is the entire press. Provide a compressive load that is greater than or equal to the compressive load provided by the apparatus, and the second press apparatus reduces the compressive load provided by the press apparatus.

According to the above configuration, the first press device component excessively provides the compressive load, so that the temporary change can be compensated while maintaining the operation safety. Next, the risk that the second press device reduces excessive compressive loads to minimize losses and in response to temporary shocks, etc., provides insufficient compressive loads.

The press device, in particular the first press device part, comprises a spring element. A spring element is provided which provides the basis load, so that the press device, including another mechanical press device having a variable response, provides a compressive load starting from the basis load. The above configuration is applied to the first press device component so that the characteristic curve for the press device can be selected even more flatly. As a result, a linear slope for the mechanical pressing means can be provided without generating an excessive compressive load which must later be compensated by the second press device component. Regardless of other features of the invention, two press device parts comprising at least one spring element can be advantageously used in a friction ring gear or continuously variable transmission. This configuration is advantageously used when the second press device component has a hydraulic component.

Optionally, the second press device component provides a load that reacts with the load provided by the first press device component. The load can thus be reduced while maintaining operational safety. According to the above configuration, the first press device part can directly use the characteristic curve, and if necessary, can react to the load reduction caused by the second press device part.

The load provided by the first press device part is advantageously partially received by the second press device part.

Even if the features are used individually in the press apparatus or in the corresponding gears, the losses can be significantly reduced by the features when the press apparatus is properly optimized. The support load generated by the compressive load is minimized, and each support member is moved on the frame or the casing by the support load, so that the loss can be significantly reduced. Safety margins must be provided to secure the gear members against unexpected rapid changes in operating parameters, and the safety margin can be minimized because the first press device component responds quickly with sufficient force reserve. have. Under normal operating conditions, the second press device component reduces the compressive load or the load for restraining the frame or casing. Overall losses are reduced because shocks or rapid changes occur only for a short time and act slightly for the entire run time.

The press apparatus can be used in various gears with gear members working together. Specifically, the press apparatus is suitable for a device in which each gear member is mutually restrained in a frictional state, interacts in a frictional state, or interacts in the event of a slip due to a released compression load. In this configuration, losses are minimized by the press apparatus.

With a hydraulic system, for example, the corresponding compressive load can be provided by an electromagnetically actuated piston. The configuration is small and compact and has a mechanically simple structure.

In the stroke path of the piston, the piece barrel is first arranged close to the overflow / refill port. According to the above configuration and method, a sufficient amount of hydraulic liquid is always provided between the piston and the press device. When applied to the load on the piston, the fluid is compressed towards the press device until the press device generates sufficient reaction pressure. If no load is provided for the piston, excess fluid flows out through the port, and fluid is supplied through the port from a fluid source when the fluid is insufficient.

Optionally, a gear pump can be provided for hydraulic operation. Such gear pumps are quite inexpensive and are advantageous, for example, by providing variable compression loads by variable rotational speeds or variable torques, almost requiring no maintenance and maintaining operational safety. In particular, the gear pump can be driven by an electric motor when a current that depends on torque is provided. The driving is performed by limiting or controlling the current, and controlling the current is relatively easier than controlling the voltage. On the other hand, if the operation is performed digitally, it is advantageous to control the voltage due to its easy configuration. Therefore, the variable compression load can be provided easily and reliably. Intentionally it is advantageous for the wing of the gear pump to provide a sliding state without requiring a complete seal. When controlling the torque, for example, the required compressive load is provided by the increased rpm.

In addition to the gear pump, other pumps may be used, such as gear pumps, which provide a pressure gradient or have internal leaks.

The apparatus for generating variable compressive loads to provide the best compressive load for continuously adjustable gears through a range of transmission ratios or adjustment movements is for example press apparatus for continuously adjustable gears such as bevel friction ring gears. It is advantageous to be configured independently of the other features of.

According to a method for operating a friction gear having at least one input member and an output member, which are selectively pressed against each other by a press device, the stop position of the friction gear and the first gear rather than the average slope between the first operating condition and the second operating condition, 1 The press apparatus is operated by a characteristic curve of operating conditions versus compressive load with another mean slope between operating conditions. Optionally, a friction gear having at least two construction conditions is provided such that at least one input member and output member are pressed against each other by at least one press device using varying compressive loads as a function of specific operating conditions, and A press device having a characteristic curve relating to operating conditions versus compressive load is provided for the friction machine. Regardless of other features of the present invention, the working efficiency of the friction ring gear is increased by the above method and apparatus.

It is advantageous to provide the variable characteristic curve for the press device in a friction gear configured with at least one input member and an output member surrounding the input member which interacts in friction. In this regard, the " frictional state " is a non-slip interaction which provides no complete fit of the shape between the two gear members in rotational motion and causes breakage between the two gear members due to excessive torque. It includes. The frictional state includes an interaction acting between two gear members through hydrostatic or hydrodynamic or electrostatic or electrodynamic loads or magnetic forces. Thus, according to the friction gear of the present invention, the intervals between the filling of fluids such as gas or liquid are arranged between the actual mechanical gear members and the speed, gap width and Pressure and so on. The varying characteristic curve is suitable for friction gears provided with media or other gear members that transfer an interaction, such as a fluid, between the two gear members.

In the above configurations, the interaction between the two gear members is controlled by the loads acting on the special working surface of the gear members. When referring to documents EP 0 878 641 A1 or EP 0 980 993 A2, for this purpose the two gear members can be suitably constrained to one another, for example by means of suitable bearings. According to various embodiments of the above documents, a press apparatus is provided which depends on the output torque and provides a variable compressive load when a certain basic load is exceeded, so that a high compressive load is generated at a high output torque, and thus transfer of friction gears. Torque can be increased. According to the prior art, the device of this type generates a significant loss in the friction gears of this type, reducing the utility of the device.

The input member and output member do not need to be connected directly. Gear members with a transmission function or means for providing a frictional connection, such as additional fluids or other interaction mechanisms, may be provided. By the balance of the load acting on the gear, the input member and the output member can be exchanged. This variant can be used because the gears of this type are constructed in a complex drivetrain. As long as the gear members are pressed against each other by the degrees of freedom of the gear members, and the one or more parts with freedom to press against each other or to be pressed against each other are suitably arranged towards the working surface of the gear member, Arranged offset relative to.

The friction ring gears of the present invention can be operated under different working conditions in consideration of various working conditions. Such working conditions are input or output torques, forces, force ratios, pressures or even variables measured in proportion to temperature, time or proportional thereto. While such a friction gear is in operation, the respective operating conditions depend on the important operating conditions, the specific embodiment or the means in proportion to or just based on the directly measurable operating conditions, and are used under a wide variety of operating conditions.

The varying characteristic curve is formed by additionally or alternatively using a friction gear of a press device comprising two press units. As such a press device comprises at least two parts, the working condition-compressive load characteristic curve applies to the required requirements using very simple means. The various average rising slopes of the above application, in particular the operating condition-compression load characteristic curve, are mentioned below. In this regard, the term “average slope” between the stop condition and the operating condition or between two operating conditions is defined by the average straight line of the first change, within the corresponding section of the operating condition-compression load characteristic curve. It is a value formed by the mean slope As the rising slope changes, there is the possibility of optimizing the operating condition-compression load characteristic curves in consideration of two or more needs in the drive. The optimum compressive load is selected until it is feasible for the instantaneous working conditions, while minimizing the loss and at the same time optimal performance of the friction gear. The adjustment of the characteristic curve between the first operating condition and the stop condition is provided in the direction between the two conditions. By allowing the ring, the base loads, and thus the base losses, are minimized, so that such equipment does not need to achieve optimal results, even in situations that depend on the attached conditions. The possibility to improve the efficiency of such friction gears will be given: when necessary, there will be a tradeoff between high cost and efficiency of increasing measurements.

This has an advantage if the two press units contain different operating conditions-compressive load characteristic curves. By combining the two characteristic curves, the overall characteristic curve of the press apparatus is suitable within a clear and understandable way.

Preferably, the two press-on units have a first share in the compressive load at the first operating condition and a second part in the compressive load at the second operating condition, and the first The difference between the first part and the second part of the press apparatus is different from the difference between the first part and the second part of the second press apparatus. The system is provided with respective press units due to different sizes in the overall compressive load of the press apparatus within the respective operating conditions, which directly affects the characteristic curve of the entire press apparatus at the structural side.

Without considering other features of the present invention, the two press units are shaped to operate in series or in parallel with respect to compressive loads and / or upon detection of working conditions. As a result, joining with a suitable transmission ratio is suitable, and the overall characteristic curve of the press apparatus is just right for the existing requirements.

Such a press device is fitted with operating condition-press load characteristic curves within a fairly wide range limited through suitable curved paths or similar installations. Disadvantages are external actions such as tolerances, spacing, thermal expansion, and similar shifting of characteristic curves, which characteristic curves are no longer accurate as a function of their operating conditions. In this case, the change is no longer guaranteed in the operating conditions causing the desired change in compressive load. For this reason, without considering other features of the present invention, preferably all press units or two press units, one or more press units, including operating condition-compression load characteristic curves having essentially constant inclination are limited. . The device is quite unresponsive to the above mentioned problems or problems of tolerances, is shaped according to each press unit, and external failures are not appropriate, and therefore within operating conditions due to each constant slope of the characteristic curve. The change leads to the same change in the corresponding compressive load without considering failures. This solution is therefore particularly advantageous if the friction gears are used in a press device with an overall characteristic curve varied from a straight line. In this application the term “substantially constant slope” is formed taking into account the tolerances that exist in the system in different ways, and is formed taking into account the requirements of different accuracy within the entire drive train. From the point of view, the term “constancy” of slope cannot be understood with a narrower understanding than the need for overall tolerance and overall accuracy of the system, respectively.

The press units are joined together and the coupling is shaped mechanically, hydrostatically or hydrodynamically. This applies especially in the case of press units which are provided separately on one of the respective gear members. In the case of a press unit or press device provided on the input side in more detail, it is particularly achieved in a compressive load which has been reduced under partial loads taking into account the input load, which reduces the overall loss of the friction ring gear and The press apparatus or press unit provided on the drive side has the advantage without considering other features of the present invention.

As the press unit provided on the input side is coupled to the press unit provided on the output side, the maximum load action can be optimized to further reduce the compressive load under partial load when the total loss is minimized.

Various parameters of the friction gear are available for various operating conditions. This is the input torque, output torque, total load, other parameters mentioned above or forces generated.

It is particularly advantageous to restrain the input torque and / or the output torque as well as the possible total load and directly represent the forces required or generated at the frictional connection between the two gear members.

Therefore, when comparing the average slope between the stop condition and the first operating condition and the average slope between the first and second operating conditions, the first operating condition is the lowest torque generated under the maximum load, and the second operating condition is the maximum. The highest torque generated under load. Thus, in order to adequately provide the characteristic curvature, the required compressive load for the lowest torque to occur at maximum load and the highest torque to occur at maximum load is determined so that the characteristic curve is shaped into a straight line between the two points.

The advantages of the characteristic curve shaped in a straight line are already mentioned in detail above. In addition, it is expected to occur under the maximum load between the minimum compression load or stationary state required to ensure rocking and / or slipping while ensuring the required compression load and gear initiation at the lowest torque. Tolerance insensitivity achieved by using the characteristic curve including the slope can be used. By selecting the characteristic curve, the basic load is limited to the minimum required range, which has the great advantage that the efficiency of the friction gear is optimized.

Two press units for some or each compression load within the total compression load of the press apparatus have the advantage of varying through various working conditions. The compressive load of one press unit is thus varied with respect to the total load or input torque and the other press unit taking into account the output torque, for example. In this way, the overall action of the friction gear is widely adapted to the given requirements and is particularly optimized for efficiency.

1 is a cross-sectional view showing a press device and a first gear of the invention.

2 is an illustration of an output bevel gear of a press device and a second gear of the invention similar to that of FIG.

3 is an illustration of an output bevel gear of a press device and a second gear of the invention similar to that of FIG.

4 is a diagram of the force ratio in the embodiment shown in FIG.

FIG. 5 is a diagram of the force ratio in the embodiment shown in FIGS. 2 and 3;

6 is a diagram of an alternative power factor.

7 is a diagram of an alternative power factor.

8 is a diagram of an alternative power factor.

9 is a diagram of an alternative power factor in another embodiment.

10 is a cross-sectional view of the alternative in FIG. 6 in a view similar to FIG. 1;

FIG. 11 is an alternative refinement of FIG. 6 within a view similar to FIG. 1;

12 is a cross-sectional view of an alternative press device and additional gear.

13 is a hydraulic drive for the gear.

14 is an illustration of the friction gear of the present invention in an illustrative cross-sectional view.

15 is a detailed view of FIG. 14;

FIG. 16 shows a function of the press apparatus shown in FIGS. 14 and 15.

17 shows a characteristic curve of the internal ball unit of the device shown in FIGS. 14 and 15.

18 shows a characteristic curve of the external ball unit of the device shown in FIGS. 14 and 15.

19 shows a characteristic curve of the entire press unit of the apparatus shown in FIGS. 14 and 15.

20 shows an alternative characteristic curve of the internal ball unit of the device shown in FIGS. 14 and 15.

21 shows a characteristic curve of the external ball unit of the device shown in FIGS. 14 and 15 applied to the characteristic curve shown in FIG. 20.

22 is a view of the characteristic curve of the entire press unit applied to the characteristic curve shown in FIGS. 20 and 21 of the apparatus shown in FIGS. 14 and 15.

23 shows a possible characteristic curve of the press apparatus.

24 is a diagram of another possible characteristic curve of the press apparatus.

25 shows the shape of the advantage of the characteristic curve.

Figure 26 is a view of a second friction gear of the invention in cross section.

FIG. 27 is a view of a characteristic curve of an input press unit of the apparatus shown in FIG. 26.

FIG. 28 is a view of a characteristic curve of the output press unit of the apparatus shown in FIG. 26;

FIG. 29 shows a characteristic curve of the entire press unit of the apparatus shown in FIG. 26;

30 is a view of a third friction gear of the invention in cross section;

Figure 31 is a view of a fourth friction gear of the invention in cross section.

32 shows a characteristic curve of the input press unit of the device shown in FIGS. 30 and 31.

33 shows a characteristic curve of the output press unit of the apparatus shown in FIGS. 30 and 31.

34 is a view of a characteristic curve of the entire press unit of the apparatus shown in FIGS. 30 and 31.

The gear shown in FIG. 1 is an input bevel gear 1 and an output bevel gear 2 which interact with each other via an adjustable friction ring 3 in a known manner. ). The input bevel gear 1 is thus operably connected to a drive shaft 4 and to a drive shaft 5 on which the output bevel gear 2 is driven. The bevel gears 1 and 2 of the embodiment are moved on a cylindrical roller bearing 6 in the radial direction. In an embodiment, the bevel gears 1, 2 are constrained to each other in the axial direction by four point contact bearings 7A, and the required press-on forces are the input bevel gears ( From 1) to the output bevel gear 2 and vice versa to transfer torque through the friction ring 3. The axial support of the input bevel gear 1 is formed through a four-point contact bearing 7A or an axial cylindrical roller bearing or the like, although not explicitly shown in the accompanying drawings.

In order to generate or release the required compressive loads, in this embodiment the press-on apparatus 8 is operated with the shaft 5 driven with the drive shaft 4 directly connected to the input bevel gear 1. It is formed between the output bevel gears (2). The press device 8 has an axial direction between the output bevel gear 2 and the four-point contact bearing 7A on the shaft 5 which is capable of being driven or driven as the compression loads change in the locked state. It is possible to change the interval.

Axial angular contact ball bearings, axial self-aligning ball bearings, axial deep groove ball bearings , Tapered roller bearings or similar bearings or other bearing devices, such as several types of bearings, are moved axially on one side, and the bevel bearings 1, 2 on the other side are moved, May be coupled to each other to be constrained to each other. Hydrostatic or hydrodynamic bearings are used.

During operation, the friction ring 3 can be adjusted in a known manner, which is not mentioned in detail below, and the transmission of ratio of the gear is selected in this way. It will be appreciated that during operation the entire device is subject to different torques. Since the connection formed between the two bevel gears 1 and 2 is a frictional connection, the compressive loads are preferably chosen to be high enough to cause controllable slippage on the friction ring 3. It is done. Controllable and especially sufficiently high slippage has the advantage of facilitating the adjustment of the gear, and the revolutions per minute (rpm) need to control only the variable torques as they are transmitted and adjusted by the compressive load.

In this regard, the operation of a friction ring gear comprising controlled slippage is easy to consider other individual features of the present invention to prevent large losses due to excessively large compressive loads intended to prevent slippage.

The adjustment of the compression load depending on the torque and the appropriate adjustment of the compression load are selected in this embodiment and will be discussed below even if the compression load is selected depending on other conditions of use. According to FIG. 1, the output torque is more particularly selected as a control for variously adjusting the compressive load.

Within the embodiment, the press device 8 is supported on one side by a screw-down disk 10 by the output bevel gear 2 and on the other side by the shaft 5 and , Two screwing disks 9, 10 comprising guide paths for the ball 11. The screwing disc 9 or screwing disc 10 is transmitted from the bevel gear 2 with torque driven to the screwing disc 10, and is passed through the balls 11 to the screwing disc 9, and the screw It is arranged as it passes from the clamping disk 9 to the driven shaft 5. The guide paths for the balls 11 cause the increased torque to cause the screwing disks 9, 10 to rotate relative to each other, in turn the balls 11 are arranged along the guide paths, and the screwing disks 9, 10) are arranged as if they were separated by this result. The ideal device performs unconstrained movement, and due to the oblique guiding paths the torque directly causes an increase in the compressive load. In this way, the press apparatus 8 generates a compressive load which depends on the output torque.

The advantage of the device as a mechanical device is that it has an extremely short reaction time which responds particularly well to impacts in a drive train located on the output side.

The balls 11, plates 9, 10 in parallel are separated by a spring arrangement 12 in which a certain basic load is applied to the press device 8. As a result of this, the press device 8 allows the balls 11 in the screwing discs 9 and 10 to be provided with linear ramps without being provided with an excessively enlarged compressive load. do. Linear ramps have the advantage that the characteristic curve is independent of various variables such as structural tolerance or thermal expansion process.

The characteristic curve of the device formed of the springs 12 and the balls 11 and formed of the plates 9, 10 can only be optimized to a certain range. Thus, the characteristic curve includes portions in which the compressive load is excessively formed. The total loss of the gear is significantly increased as a result of this. For this reason, the apparatus of FIG. 1 includes force compensation, in particular for partial load ranges. Within the embodiment, the compensation is made by the hydraulic pressure generated between the plate connected to the driven shaft 5 and the compression plate 10 which interferes with the compressive load generated by the balls. Compensation is controlled by the action of the position of the friction ring in the axial direction along the two bevel gears, and a very large compressive load causes the friction ring 3 to lift the rigid end of the input bevel gear from the floating in operation. It is done in such a way as to ensure that it is provided within the surrounding positions. Instead of measuring the position, for example, the transmission ratio is chosen to change in proportion to the position. Other variables are used as they are considered in the same way. In close proximity to the friction ring 3, the compressive load is more compensated for and positioned against the prominent end of the input bevel gear 1. Compensation, on the other hand, weakens when opposing effects are controlled.

The thickness of the arrows describing the strength of each force in accordance with the situation is shown schematically in FIG. 4. The hydraulic pressure 14 cancels out a fairly large force of the spring 12 or the balls 11, so that the bearings 6, 7A will not be subjected to unnecessary loads. Arrow 90 shows the external forces of arrow 91, the external forces of the driven shaft 5 from the output bevel gear and the internal forces of arrow 92.

In the embodiment shown in FIG. 1, the hydraulic pressure 14 is via a hydraulic pressure line arranged on an additional shaft 16 that is tightly connected to the shaft 5 via a screw 17. Is provided. Screw 17 seals fill port 18 with undercut 20 and line 19, provides bubble-free filling of hydraulic pressure space, while simultaneously providing operational safety. To ensure. On the end away from the driven shaft 5 the shaft 16 comprises a hydraulic seal so that the hydraulic pressure 14 is controlled from the outside as required and immediately builds up.

The device shown in FIG. 1 additionally comprises a mounting body 21 via an output bevel gear 2 which is transmitted radially. Through the mounting body 21 the press device 8 can be placed immediately inside the driven bevel gear 2.

The device shown in FIG. 2 is essentially consistent with the embodiment shown in FIG. 1 and structural parts having the same function denote the same reference numerals, which will not be mentioned again again.

Within the embodiment, the base load is not generated by the springs placed in parallel except for the springs 22 placed in series with the press device 8, but is supported by the driven shaft 5, this embodiment This is achieved by using a four-point contact bearing 23, which transmits a compressive load between the screwing disk 9 and the driven shaft 5 on one side and drives against the driven shaft 5 on the other side. Provided to move the bevel gear 2 in the axial direction.

In the vicinity, a hydraulic pressure supply 24 projects away from the bevel gear 2 driven in contrast to the hydraulic pressure supply 24 of the embodiment shown in FIG. Are arranged directly on the component part 13 which is firmly connected to the driven shaft 5, which will be referred to below as a counterplate 13. As pressure is applied to the line 26 provided in the hydraulic pressure supply 24, the hydraulic pressure 14 causes the screwing disk 10 and the counter plate to counteract the compressive load generated by the balls 11. 13) to reduce the overall compressive load of the press apparatus 8.

As evident from FIG. 2, the counter plate 13 is screwed into the shaft 5 in this embodiment, and additional screws having the two functions mentioned above are used in the embodiment shown in FIG. 1. It is done. The hydraulic pressure space formed between the screwing disk 10 and the counter plate 13 is sealed to the outside via seals 27 (not shown in FIG. 1).

As is apparent from FIG. 5, the apparatus shown in FIG. 2 causes a similar operation to the embodiment shown in FIGS. 1 and 4. Compensating force is generated through the pressure 14 so that the overall compressive load and consequently the locking force acting on the bearings 6 and 7A are minimized through the pressure 14.

Instead of the hydraulic pressure device, a motor-driven arrangement is illustrated by way of example in the embodiment of FIG. 3 and in FIG. 3 in accordance with the action as shown in FIG. 5 and the rest of the embodiment shown in FIG. 2. As shown, it may be selected for the second press device component instead of the device for generating the pressure 14.

The device generates a basic load through a series connected spring arrangement 22 which is moved on a shaft 5 driven by a four point contact bearing. Threaded bolt 28B in a threaded hole 28A of the driven shaft 5 to improve the motor drive system of the second press-on apparatus part 14. Is provided, the bolt is moved on the bevel gear 2 driven by the four-point contact bearing 29 and on the screwing plate 10, the function of the threaded hole 28A being within the device. It matches the function of the counter board 13. The threaded bolt 28B is moved to the shaft 5 by the motor 30 and is operated by means of the gear 31 via slip rings 33 and electric lines 32. This allows the generation of various counterforces to counteract the compressive load generated by the springs 22 and the balls 11.

According to Fig. 6, the device of the present invention can also be improved without a spring device for generating a base load. Schematic devices corresponding to the state shown in Fig. 6 are shown in Figs. In addition a press device 8 is provided which comprises a raceway for the balls 11 and which is supported by a shaft 5 on which a screwing plate 9 is driven. The raceways are not provided in the other threaded plates as in the embodiment shown in FIGS. 1 to 5 but are provided directly in the driven bevel gear 2. The second press device component 14 thus acts directly on the bevel gear 2 driven by the pressure space 34. With respect to the rest, the functions will not be discussed in detail in accordance with the functions of the embodiments already discussed. Furthermore, in the embodiment shown in FIG. 10, it will be seen that the bevel gears 1, 2 move the axial cylindrical roller bearings 7B in the axial direction. Furthermore, in the embodiment, the second press device component 14 is operated principally as a function of the input torque registered by the input shaft 4, and the screwing disk 35 rotates on the drive bevel gear 1. Connected not only to the piston 37 but also to the balls 36, the input shaft 4, which is impossible to connect but axially moveable, and is fed by hydraulic pressure into the pressure space 34 by the line 38. . Line 38 is connected via leadthroughs 39 to the respective structural components that rotate with the bevel gears 1, 2.

In addition, an input toque actuation 40 is formed by the component members 35, 36, 37, and the second press device component 14 also drives the piston 41 as a function of additional parameters. It is controlled or operated through An alternative arrangement to the embodiment shown in FIG. 10 is shown in FIG. 11 in which input torque detection is sent to the second press device component via a lever arrangement 42. In addition, additional control parameters via servo 43 are used to adjust the second press device component.

The second press device part or the whole press device can be operated or adjusted by using different control parameters. More specifically, the torque of the motor, the input revolutions per minute, the output revolutions per minute, the adjusting distance or adjustment position of the friction ring 3, the gear oil or the gear temperature, the wheel revolutions per minute or for example the ABS (anti Lock brake system) signal, external shock detection or other parameters.

The measured values are transferable to the press device 8 by means of hydraulic pressure or by a motor as already mentioned. In a hydraulic pressure system, this is done in particular by the pressure regulation and by pumps already formed in the motor vehicle or by pumps such as gear pumps. In addition, piston devices and electric motor systems are considered.

In more detail, a gear pump 61 is provided which is driven by an electric motor 62 to move the fluid from the reservoir 64. Torque is applied to the gear pump 61 via the voltage 63 applied to the electric motor 62, which torque rotates the pump and in this way the fluid or press device 8 is subjected to the pressure generated from the torque. Generate a matching counter pressure.

A similar function is shown in FIG. 7, with the internal forces 92 being formed by the spring devices 12 connected in parallel and the balls 11 connected in parallel to the hydraulic pressure 14. The internal forces 92 are opposed by the external force 90 of the driven shaft 5 as well as by the external force 91 of the output bevel gear 2.

An alternative function shown in FIG. 8 includes the arrangement of the hydraulic pressure 14 and the balls 11 connected in parallel as the hydraulic pressure 14 and the balls 11 are subjected to internal forces 92. The external force of the driven shaft 5, the external force 90 and the driven output gear 2 is combined into the internal forces 92. As shown in FIG. 6, the apparatus of FIG. 8 does not require additional spring elements.

In the embodiment of FIG. 9, the balls 11, the hydraulic pressure 14 and the spring element 12 act in parallel. As a result, the internal forces 92 are opposite to the external force 90 and the external force 91.

The gear shown in FIG. 12 comprises an input bevel gear 1 and an output bevel gear 2 working together via an adjustable friction ring 3. The input bevel gear 1 is operably connected to the drive shaft 4, and the output bevel gear 2 is operably connected to the driven shaft 5. In this embodiment, the input bevel gear 1 is moved on one side by tapered roller bearings 80 and on the other side by cylindrical roller bearings. Tapered roller bearings 80 are suitable for receiving axial forces as well as radial forces. In the embodiment, the output bevel gear 2 only moves on the driven shaft 5 and the cylindrical roller bearings 6 of the output bevel gear 2 which are additionally moved by the tapered roller bearings 81. It is done. The two bevel bearings 1, 2 are fixed to each other in the axial direction by tapered roller bearings 81, and in this way the required compressive load is such that the transmission of torque from the input bevel gear 1 to the output bevel gear (2) is allowed to be applied, and is formed in reverse by the friction ring (3).

A press device 8 is provided between the driven shaft 5 and the output bevel gear 2 to generate or release the required compressive load, in which the input shaft 4 is an input bevel gear. It is directly connected to (1). In the embodiment, the press device 8 is capable of varying the axial distance between the tapered roller bearings 81 and the output bevel gear 2 on the driven shaft 5 and is capable of varying the compressive load which changes when in a restrained state. Can be generated. According to the above technique, the bearings 2,80,81 provided in this embodiment are to be moved to one side in the radial direction and the axial direction to the other side with the bevel gears 1 and 2 constrained. It can be combined with other bearing devices and replaced with other bearing devices. Hydrostatic or hydrodynamic bearings are used because of these results.

The transmission ratio of the gears shown is selected by positional shifting of the friction ring 3, whereby different forces, more particularly different torques, are formed to act as the overall device. The frictional connection between the two bevel gears 1 and the bevel gears 2 in order to allow for compressive loads has the advantage of being suitable for various conditions of use, and the press device 8 provides a guide path for the balls 11. Two screwing disks 9, 10 comprising a < RTI ID = 0.0 > Each screwing disk 9 and screwing disk 10 has torque transmitted from the output bevel gear 2 to the screwing disk 10 via the balls 11 and to the screwing disk 9. It is formed in a shape that is transmitted from the screwing disk (9, 10) to the driven shaft (5). Guide paths for the balls 11 are increased in torque to cause the two screwing disks 9 and the screwing disk 10 to rotate with each other and to cause the balls 11 to be repositioned along the guide path. The screwing disk 9 and the screwing disk 10 is formed to be separated. Ideally, the rotation between the screwing disk 9 and the screwing disk 10 is not formed if the device is inherently hard. Due to the oblique guiding paths the torque directly increases the compressive load. In this way, the press apparatus 8 generates a compressive load which depends on the output torque. Advantageously, the device has a mechanical device that responds very well to shocks in a drive crane located on the output side in an extremely short time. The screwing disk 9 and the screwing disk 10 are separated in parallel to the balls 11 by means of a spring device 12 which provides a certain basis load in the press device 8. As the characteristic curve of the press apparatus 8 is optimized to a limited range, the press apparatus 8 includes compensating forces within some load ranges. Within the embodiment, pressure is generated hydraulically between the plate and the screwing disk 10 connected to the driven shaft 5, the pressure being generated by the springs 12 and the balls 11. Offset the load. In this way, excess or unnecessary compressive loads generated by the springs 12 and the balls 11 are hydrodynamically compensable.

The pressure is provided through a hydraulic line 15 arranged in an additional shaft 16. An oil space 82 is formed between the press apparatus 8 and the output bevel gear 2. The oil contained in the oil space better offsets the centrifugal forces acting as oil in the press apparatus 8. A reservoir 64 is provided to contain a sufficient amount of oil to control the press apparatus 8. Torque may be applied to the pump 61 via the voltage 63 applied to the electric motor 62, which is a counter pressure counter in which the fluid or press device 8 corresponds to the pressure formed from the torque. It is controlled in such a way as to generate pressure.

The embodiment shown in FIG. 13 is alternatively formed on the casing 44 by a spacer 45, in which a pressure is applied to the casing 44 by a spring 49 inside the coil 46. The piston 48 and the core 47 are arranged. If a current is applied to the coil 46, the core 47 is pushed to the center of the coil 46 with respect to the spring 49, which causes the piston 48 to be pushed into the cylinder 50 and the coil 46. It is generated in the cylinder 50 and the line 51 in contact with the variable pressure as a function of the tension applied to it. Line 51 is connected to the supply 26 of the embodiment shown in FIGS. 1 and 2 or to the line 38 of the embodiment shown in FIG. 7.

Within the cylinder 50 is provided a port 52 which is sealed as if it is sealed in the first position during movement forward of the piston 48. The port 52 is connected to the overflow / refill port 53 so that the liquid is filled or replenished with the entire device in a relaxed state to compensate for the overpressure and leakage formed from external actions. It will be appreciated that the electrical action of the hydraulic piston, such as leakage protection and / or can be found in this application without considering other features of the present invention.

The friction gear is described with characteristic curves, and is shown through FIGS. 14-22, which show an input bevel gear 101 and an output bevel gear 102 that interact with each other via an adjustable friction ring 103. Include. The input bevel gear 101 is operably connected to the drive shaft 104, and the output bevel gear 201 is connected to the driven shaft 105. In an embodiment the input bevel gear 101 and the output bevel gear 201 are moved radially onto the cylindrical roller bearing 106 (shown in FIG. 14). In addition, the input bevel gear 101 and the output bevel gear ( 201 are constrained to each other in the axial direction via the axial cylindrical roller bearing 107, and the necessary compressive loads are transferred to the output bevel gear 201 from the input bevel gear 101 via the friction ring 103. Is applied.

In order to generate and restrain the necessary compressive loads, a press device 108 is formed between the driven shaft 105 and the output bevel gear 201, and the input shaft 104 is directly connected to the input bevel gear 101. Lose. The press device 108 generates various compressive loads generated from the spring device in the constrained state or sets the axial distance between the axial cylindrical roller bearing 107 and the output bevel gear 201 on the driven shaft 105. Can change.

Axial angular contact ball bearings, axial self-aligning ball bearings, axial deep groove ball bearings, Other bearing arrangements, such as tapered roller bearings or similar bearings or several types of bearings, are moved axially on one side, and bevel bearings 101, 102 on the other side, in order to be restrained from one another. Can be combined with each other. Hydrostatic or hydrodynamic bearings are used.

During operation, the friction ring 103 can be adjusted in a well known manner, which is not discussed in detail below, and the transmission of the gear is selected in this way.

During operation, the entire apparatus may be seen that different torques are applied. The connection acting between the two bevel gears 101 and 102 is a frictional connection, with compression loads selected for controlling the slip occurring on the friction ring 103 are preferred. Unnecessarily high compressive loads on the other side create a fairly high basis load, while at the same time lowering the efficiency of the friction gear. For this reason, although the compressive load is selected according to the function of the different use conditions, the torque which depends on the adjustment of the compressive load is selected in the embodiment. According to FIGS. 14 and 15, the output torque is selected as a function for varying the compressive load, and other kinds of operating conditions such as the total load or the input torque are used to be clear from the embodiments to be discussed below. .

Within an embodiment, the press device 108 is formed and applied by each inner ball 112 or outer ball 113, is formed continuously against compressive loads, and connected in parallel to the torque measurement. It includes two screwing disk 110 and the screwing disk 111. The balls 112, 113 roll in raceways formed in press-on plates 114, 115, 116 respectively situated on one side of the shaft and on the side of the bevel gear. In this embodiment, the press plates 114, 115 are provided on the side of the shaft arranged to be non-rotatable with respect to the driven shaft 105, while the press plate 116 is provided with respect to the driven bevel gear 102. It is arranged on the side of the bevel gear arranged to be non-rotable. On the other hand, the press-on plates 114, 115 and 116 are moved to coincide with the sliding bearings 117, 118 and 119 in order to move axially on the respective structural parts.

Torque is transmitted from the output gear 102 driven through the bearing 119 to the press plate 116, and presses from the press plate 116 through the balls 112, 113 and the press plate 115 and the bearing 118. Electrolyte to plate 114, electrolyzed from press plate 114 to shaft 105 driven through bearing 117, press plates 114, 115, and 116 drive through bearing plate 122 and axial cylindrical roller bearings. Positionally axially relative to the press bearing 120 supported by the bevel gear 102 and against the force of the spring devices 109. According to FIGS. 14 and 15, in the upper edge portion of the press device 108, the device is of low torque whereas in a low region a high torque device is formed, in which the press plate 116 is driven at a high torque. The shoulder of the bevel gear 102 is stopped relative to the shoulder 123 so that the characteristic curve of the entire device is directly affected by the function of the torque.

FIG. 16 is shown as a combination of two press units 110 and 111 with structural parts having the same function as the structural parts shown in FIGS. 14 and 15 which are designated by the same reference numerals. The balls 112 and 113 roll in raceways shaped to different slopes β and γ. More complex raceways are used when needed, and linear raceways have the advantage of preventing thermal effects or spacing.

It is shown in the lower part of FIG. 16 by an adjustment travel (V) for the devices at the top of FIG. 16 at a given shift or at a given torque, the raceway forming an overall stroke G. Each stroke H !, H @ is formed. Stroke H1 is limited by a limit stop, whereby the entire stroke G is not determined linearly on the adjustment stroke V.

Raceways are formed to represent the characteristic curves shown in FIGS. 17 and 18. The characteristic curve shown in Fig. 19 is obtained because the torque is dependent on parallel connection, and the pairs are added due to the parallel connection to the torque, and the compressive load because they are connected in series with respect to the axial compressive load. Is the same in the two press units. As the shoulder 123 is reached, only the characteristic curve of the press-on unit 111 contributes to the overall characteristic curve.

The other characteristic curves shown in FIGS. 21-20 are designed with the negative slope of the inner press unit to form the desired overall characteristic curve (FIG. 22).

According to FIGS. 17-22, the press unit in this embodiment comprises a torque-compression load characteristic curve and an operating condition-compression load characteristic curve each having an essentially constant slope. With the use of press units the characteristic curve accommodates the respective demand points despite the inherent constant inclination. As a result, the two press units 110, 111 have a first compressive load portion at the first torque, a second compressive load portion at the second torque, and a first compressive load and a second compression of the first press apparatus 110. The difference between the loads is possible because the difference between the first compressive load and the second compressive load of the second press apparatus 110 is different.

In general, friction gears are operated within specific operating intervals for different kinds of conditions of use. In view of the compressive load, what is required is that a high compressive load be applied at the upper end of the section and a specific first compressive load be applied at the lower end of the section. It would be advantageous to provide a constant slope of the compressive load characteristic curve-use conditions between the two points within the operating interval to avoid problems that may arise with tolerances. Under this condition, the characteristic curve shown in FIG. 23 will be improved using press apparatuses except for one compression, although the operational interval is in the range between 50 Nm and 350 Nm. In conclusion, significant ground loads are present in the system, which significantly reduces efficiency. This result is consistent with the given raceway of varying slopes shown in FIG. The characteristic curve preferably has a constant slope between 50 Nm and 350 Nm, dropping the operating range to near 0N and forming in more detail at rest (0Nm) and below 1N at rest. Thus, the basic load in the overall system is considerably reduced, thereby increasing the overall efficiency. Various slopes of the raceway within the press unit include tolerance problems, which avoids the problems caused by using the at least two press units mentioned above.

Preferably, the present invention provides an operating range of an average slope (50 Nm to 350 Nm, see FIGS. 24 and 25), wherein the operating condition-compression load characteristic curve is smaller than the operating range as shown in FIGS. 24 and 25. It is intended to include. Thus, the base load of the overall system is lowered and the efficiency is increased. On the other hand, the devices form a characteristic curve required to have an operating range between 100 Nm and 350 Nm as shown in FIG. 19. Such a characteristic curve is only formed by the two press units at low tolerance sensitivity.

It is easy to reduce the compressive load as a function of the second load condition, i.e. the total load or the input torque, in more detail in order to minimize losses in the overall system, which is shown in FIG. The efficiency of the overall system is additionally increased. This is ensured by the apparatus shown in FIG. The device essentially corresponds to the device shown in FIGS. 28 and 29, in which bevel gears 101, 102 move on tapered roller bearings 124 in the axial direction except on cylindrical roller bearings 106. do.

In an embodiment, the press device is formed from two press units 125, 126. Departing from the configuration of the apparatus shown in FIGS. 28 and 29, the press unit 125 is arranged on the output bevel gear 201 and the other press unit 126 is arranged on the input bevel gear 101. In this way, the entire press apparatus can directly detect the input torque and the output torque together and convert them into compressive loads. Press apparatuses 125 and 126 include the characteristic curves shown in FIGS. 27 and 28. As a result, the characteristic curve shown in FIG. 29 essentially coincides with the characteristic curve of the output press unit 125 but becomes a horizontal line at low torque as a function of load. The slope of the characteristic curve of the output press unit 125 is chosen such that the characteristic curve intersects the ideal full load characteristic curve in the operating section, which results in a sufficiently high compressive load at high output torque. . The entire apparatus is shaped to extend the ideal maximum load characteristic curve at full load at low revolutions per minute. At partial loads, even if too high compressive loads are provided in the maximum load process, the overall load is reduced in the system, falling short of the ideal maximum load characteristic curve depending on the load. As the slope of the characteristic curve for the output press unit 125 is selected, the intersection of the ideal maximum load characteristic curve will be moved to minimize the overall loss. According to FIG. 29, for the reason that the second press unit 126 does not operate, the characteristic curve slope of the output press unit 125 cannot be selected to be equal to the slope of the ideal overall load characteristic curve within the operating range.

The latter, on the other hand, becomes possible as the two press units 125 and 126 are combined, which is illustrated by the embodiment of FIGS. 30 and 31. The device is essentially identical to the device shown in FIGS. 28 and 29 or 26 as well as the structural parts having the same numbered identical functions.

In this embodiment, the press units 125, 126 are arranged in the various gear members of the friction gear, which is shown in the embodiment of FIG. The press units 125, 126 comprise ball devices 127, 128, respectively, supported by the press plates 129, 130 of the output shaft 105 and the input shaft 104, respectively. On the other hand, the ball 128 is supported by the press plate 131 which is provided to be rotatable in the axial direction with respect to the input bevel gear 101. At the same time, the press plate is provided to the piston 133 as a piston for hydraulic feedback and is connected to the press plate 130 at the same time. No other press plate is formed in the press unit 125 on the output side, and balls 127 are arranged directly on the bevel gear 102 driven for the rest, and separate for accommodating the raceways. Press plate is provided in the above aspect.

Hydraulic feedback 32 is guided into the input bevel gears 101 and 102 through leadthroughs 134 and 135, and according to the apparatus shown in FIG. Instead of the feedback 132, the mechanical system intersects the plates 136, 137 of the press units 125, 126. This connection allows selection for the output press unit 125 and has the exact slope of the ideal characteristic curve within the operating range (shown in FIG. 25). Through the input press unit 126, the characteristic curve is desired. Raised to height At low loads, depending on the load, the entire device essentially follows the ideal characteristic curve shown in FIG. 25 as shown in FIG.

Claims (32)

In friction ring gear, The friction ring gear comprises two or more radially spaced friction wheels 1,2 and one friction ring 3 arranged between the friction wheels, wherein the two frictions Surrounding one of the wheels, the friction wheels 1 and 2 and the friction ring 3 are constrained together via a press-on apparatus 8, The press device comprises at least two press device parts 9, 10, 11 having a shorter reaction time than the second press device part of the two press device parts. . Friction ring gear according to claim 1, characterized in that the first press device component (9, 10, 11) is unregulated. Friction ring gear according to claim 1 or 2, characterized in that the second press device component (14) is controlled or regulated. In a friction ring gear, the friction ring gear The friction ring gear comprises two or more radially spaced friction wheels 1,2 and one friction ring 3 arranged between the friction wheels, wherein the two frictions Surrounding one of the wheels, the friction wheels 1 and 2 and the friction ring 3 are constrained together via a press-on apparatus 8, The press device comprises at least two press device parts 9, 10, 11, 14, the first press device parts 9, 10, 11 having a compression equal to or greater than the compressive load provided by the press device. Providing a load, wherein the second press device (14) reduces the compressive load provided by the first press device (9, 10, 11). 5. The friction ring gear according to claim 1, wherein the press device comprises a spring element 12, 22. 6. 6. The press device according to claim 1, wherein the second press device 14 provides a force opposite to the force provided by the first press device parts 9, 10, 11. 7. Friction ring gear, characterized in that. The press device component (14) according to claim 1, wherein the second press device component (14) partially accumulates the force exerted by the first press device components (9, 10, 11). Friction ring gear, characterized in that. 8. A friction ring gear according to any one of the preceding claims, wherein the second press device component (14) is hydraulically actuated. 9. A friction ring gear according to claim 8, wherein the hydraulic actuation comprises an electromagnetically actuated piston (48). 10. Friction ring gear according to claim 9, wherein the piston seals the overflow / refill port (52) on a path for generating pressure. 9. A friction ring gear according to claim 8, wherein the hydraulic actuation comprises a gear pump (61). 12. The friction ring gear according to claim 11, wherein the gear pump is operated by an electric motor to which a voltage depending on torque is applied. The at least one input member 101 and the at least one output member 102 have at least two operating conditions which are compressed with one another by at least one press device, each of which is When a varying compression pressure acts as a function of operating conditions, Friction ring gear, characterized in that the press device (108, 125, 126) comprises two or more press-on units (110, 111, 125, 126). 14. A friction ring gear according to any one of the preceding claims, wherein the two press-on units (110, 111, 125, 126) comprise different operating condition-compression load characteristic curves. 15. The method according to any one of claims 1 to 14, wherein the two press units (110, 111, 125, 126) are at a first share and at a second operating condition in a compressive load at a first operating condition. A friction ring characterized by having a second part within the compressive load, the difference between the first part and the second part of the first press device being different from the difference between the first part and the second part of the second press device Gear. 16. Friction ring gear according to any of the preceding claims, characterized in that the two press units are shaped to operate in parallel in determining the compressive load and / or operating conditions. 17. Friction ring according to any of the preceding claims, characterized in that the two press units (110, 111, 125, 126) are shaped to operate in series in determining the compression load and / or operating conditions. Gear. 18. Friction ring gear according to any one of the preceding claims, characterized in that the one or more press units (110, 111, 125, 126) comprise an operating condition-compression load characteristic curve with a constant slope. 19. Friction ring gear according to any of the preceding claims, wherein the press device (108, 125, 126) comprises two or more press units (110, 111, 125, 126) coupled to one another. 20. The friction ring gear as in claim 19, wherein the coupling is mechanically shaped. 21. A friction ring gear according to claim 19 or 20, wherein the coupling is hydrodynamically or hydrostatically shaped. 22. Friction ring gear according to any of the preceding claims, characterized in that the press unit (126) is arranged on the input side and the press unit (125) is arranged on the output side. 23. The method according to any one of claims 1 to 22, wherein at least one input member 101 and at least one output member 102 have two or more operating conditions that are compressed with each other by one or more press devices 108, 125, 126. When a varying compression pressure is applied as a function of each operating condition, The press device comprises an operating condition-compression load characteristic curve having a different average slope between the stationary position of the friction gear and the first operating condition than in between the first and second operating conditions. Gear. In a method of operating a friction ring gear, One or more input members 101 and one or more output members 102 are compressed with each other by press devices 108, 125, 126, The press apparatuses 108, 125 and 126 are operated with an operating condition-compression load characteristic curve having a different average slope between the stationary position of the friction gear and the first operating condition than between between the first and second operating conditions. To operate the friction ring gear. 25. A method according to any one of claims 1 to 24, wherein the operating conditions are selected in proportion to the input torque and / or the output torque. Friction ring gear. 26. A method as claimed in any one of claims 1 to 25, wherein the first operating condition is a lower torque to occur under full load. Ring gear. 27. A method or friction ring gear according to any one of claims 1 to 26, wherein the first operating condition is a highest torque to occur under maximum load. 28. A method according to any one of the preceding claims, wherein the compressive load of each of the two or more press units 125, 126 is various operating conditions such as input torque, output torque, total load, force or the like. Friction ring gear or a method for operating a friction ring gear, characterized in that it changes by. 29. The press apparatus as claimed in any one of claims 1 to 28, wherein the press apparatuses 108, 125 and 126 comprise a torque-compression load characteristic curve which forms a compressive load near 0 N of less than 1 N at an insignificant torque. A method of operating a friction ring gear or a friction ring gear. The press device 108, 125, 126 according to any one of the preceding claims, wherein the press devices 108, 125, 126 are less than or equal to the lowest torque that may occur during operation under maximum load, between the highest torque that may occur during operation and the lowest torque that may occur during operation. A friction ring gear or method for operating a friction ring gear, characterized in that it comprises a torque-compression load characteristic curve comprising a smaller average slope. 31. A method as claimed in any one of claims 1 to 30, wherein the press devices 125, 126 comprise a load which depends on the operating condition-compression load characteristic curve. Ring gear. 32. A method as claimed in claim 31, wherein the compressive load under load below the maximum load is smaller than the compressive load under maximum load.

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