• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A friction gear has a two-part compression device so that the two partial compressors can preferably have constant slope rotational torque-compressive force characteristics and the overall characteristic nevertheless has a variable slope. It is thus possible to design an installation with tolerances with a very advantageous characteristic.
    公开号:BE1018493A5
    申请号:E2004/0004
    申请日:2004-01-06
    公开日:2011-02-01
    发明作者:Ulrich Rohs；Werner Brandwitte；Christoph Droger
    申请人:Ulrich Rohs；
    IPC主号:
    专利说明:

    METHOD FOR OPERATING A FRICTIONAL GEAR AND FRICTIONAL GEAR
    The invention relates on the one hand to a method of operating a bevel gear and on the other hand to a conical friction ring gear.
    The invention relates in particular to the sector of gears with conical friction rings, as known for example from document EP 0 878 641 A1 or from document EP 0 980 993 A2. Two conical friction wheels with parallel axes are installed in such a way that there remains between them a constant slot in which a friction ring in contact with the two conical friction wheels of one of the conical friction wheels can to be moved around them. In this way, it is possible to create a gearless adjustable gear.
    In addition, however, the invention also relates to all other bevel gear gears in which at least one input member and at least one output member interact in friction with each other. In the present context, the term "frictional" includes any interaction which is not geometrically bonded between two rotating gear members, wherein non-destructive sliding between the two gear elements may occur in preference to rotational torque too high. This term also includes an interaction that acts through hydrostatic or hydrodynamic or electrostatic, electrodynamic or magnetic forces between the two gear elements. The present invention therefore also comprises in particular the conical friction ring gears in which there remains, between the mechanical gearing elements proper a slot filled with a fluid, such as for example a gas or a liquid, and the speeds, the Slit widths, pressures and the like are dimensioned so that this fluid causes for example due to shear forces an interaction between the two gear elements.
    To this extent, the present invention also relates to the bevel gear gears in which there are provided between the two gear elements an interaction factor medium or several media of this type, such as fluids or else another gear element. .
    In all these installations, the interaction between the two gear elements is governed to a relatively large extent by the forces acting on the respective interactive surface of the gear elements. As known for example from document EP 0 878 641 A1 or EP 0 980 993 A2, the two gear elements can be tightly tightened for this purpose, which can for example be guaranteed by bearings. appropriate. In addition, as illustrated by various exemplary embodiments of these documents, compression devices may be provided which provide variable compression forces beyond a defined base load as a function of output output rotational torque. so that with high output rotational torques, high compression forces can also be generated, thereby increasing the transmittable torque of the friction gear. Such installations, however, cause relatively high losses on such friction gears, which calls into question their profitability.
    The object of the present invention is therefore to increase the running profitability of a conque friction ring gear.
    The invention proposes as a solution a method of operation of a conical friction ring gear comprising at least one input member and at least one output member, which are compressed against one another by means of a compression device, which friction gear is distinguished from the fact that the compression device is used with a characteristic operating state-compressive force which has, between a state of rest of the tapered friction ring gear and a first state in operation, an average slope other than between the first operating state and a second operating state. The invention also provides a conical friction ring gear having at least two operating states, wherein at least one input member and at least one output member are compressed against each other by means of less a compression device with the aid of a compression force varying according to the respective operating state and which is distinguished by a compression device having a characteristic line operating state-compressive force already described above.
    As already explained in the introduction, the input element and the output element do not need to be directly connected, but it is conceivable that there may be intermediate gear elements or measurements ensuring the connection. friction, such as additional fluids or other interaction mechanisms. Due to the balance of forces in a gear, the input element and the output element can also be switched. However, since such gears are frequently found in a complex propulsion line, this differentiation will generally have to be maintained. It is further understood that a compression of the two gear elements against each other can also take place through degrees of freedom oriented with a shift of these gear elements, as long as at least one component degrees of freedom used during compression or pressure is appropriately directed to the interactive surface of a corresponding gear element.
    The conical friction ring gears according to the invention can be used in different operating states as well as taking into account different types of operating states. Such types of different operating states can be, for example, input or output rotational torques, speeds, forces or force ratios, pressures or also temperatures, times or the like, and magnitudes. proportional to these. During the operation of such a cone-type gear, the respective operating state types are used in different operating states, certain types of operating states-depending on the concrete embodiment or the conversion. - being of only subordinate importance or being proportional to other types of easily measurable operating state.
    Such a management of the method according to the invention can be carried out in particular with a conical friction ring gear proposed as a second solution, in which the compression device comprises at least two compression units. With a compression device of this type comprising at least two components, the characteristic operating state-compression force can be adapted by relatively simple means to the desired requirements. This is particularly valid for the different average slopes of the operating state-compressive force characteristic as previously described. At this level, the term "average slope" between two operating states or between an operating state and a state of rest describes a value that is determined by a calculated average slope or a calculated average line of the first bypass in the operating state. corresponding interval of the characteristic operating state-compressive force. Due to the modification of the slope, there is a possibility of optimizing the operating state-compressive force characteristic in at least two respects in terms of propulsion requirements. It is thus possible to ensure, between the two operating states, as optimal as possible ratios at the level of the propulsion force as a function of the respective concrete operating state, so that the compression force is chosen in such an optimal manner. as possible with respect to the momentary operating state. It is thus possible to minimize the losses with optimum performance of the conical friction ring gear. The adaptation of the characteristic between the first state of operation and the state of rest allows on the other hand a direct transition between these two states, which makes it possible to further minimize the basic charges and thus the base losses. It goes without saying that this measure does not necessarily have to lead to an optimal result alone, this can already be the case - depending on the existing peripheral conditions. Those skilled in the art, however, through the present invention, have the opportunity to improve the performance of such conical friction ring gears. It will then find a trade-off between other measures that increase performance and, where appropriate, higher costs.
    In particular, it is advantageous for the two compression units to have, as an integral part of the compression device, different operating state-compressive force characteristics. By combining the two features, the overall feature of the compression device can be adapted accordingly in a visible and understandable manner.
    The two compression units can preferably respectively provide, in the first operating state, a first contribution to the compressive force and, in the second operating state, respectively a second contribution to the compressive force, the difference between the first and the second contribution of the first compression device diverging from the difference between the first and second contributions of the second compression device. Thus, a system is created in which the respective operating states provide, in the respective operating states, a different contribution to the overall compressive force of the compression device, thereby influencing the characteristic of the all of the compression device in a simple way at the design level.
    The two compression units can then be designed, independently of the other features of the present invention, at the level of the determination of the operating state and / or the compressive force, so as to act in parallel or in series.
    In this way as well as thanks to suitable transmission ratios with a corresponding coupling, the overall characteristic of the compression device can be adapted without problems to the existing requirements.
    It is certainly possible, by means of appropriate cam slides or similar measurements, to adapt a characteristic operating state-compressive force for such a compression device within relatively wide limits. However, this generally has the disadvantage that external influences such as tolerances, play, thermal expansion or the like cause a shift in the characteristic, so that this characteristic is no longer correctly tracked according to the state of play. corresponding operation. In these cases, therefore, it is no longer guaranteed that a modification of the operating state also causes the desired modification of the compression force. It is for this reason that it is presently proposed - also independently of the other features of the present invention - that at least one compression unit, preferably both or all of the compression units, have a characteristic operating state-force compression having a substantially constant slope. Such an installation is relatively insensitive to the aforementioned tolerance or disturbance problems because, for each compression unit which is designed accordingly, an external disturbance is not important insofar as a modification of the operating state of the The fact that the constant slope of the respective characteristic causes, independently of disturbances of this type, the same modification of the corresponding compressive force. To this extent, such a solution is particularly advantageous if the conical friction ring gears are used with compression devices whose overall characteristic diverges from a straight line. In this context, it is understood that the term "substantially constant slope" is to be considered, with regard to other tolerances otherwise existing in the system as well as other requirements for precision in the overall propulsion line. so that at this level the term "constancy" of a slope should not be used in a narrower context than is required by the overall accuracy or overall tolerance of the system.
    The compression units are preferably coupled to each other, the coupling being able to be carried out mechanically or hydrodynamically or hydrostatically. This is particularly valid also for the case where the compression units are respectively provided separated on a gear element. In particular in a compression device or a compression unit provided on the input side, an input load can be considered, this being able to take place because with partial loads, the compressive force decreases, which makes it possible to reduce the losses. of the tapered ring gear, so that such a compression device or compression unit provided on the propulsion side is also advantageous independently of the other features of the present invention.
    By coupling the input-side compression unit to the output-side compression unit, it becomes further possible to reduce the partial load compressive force with optimal full load behavior so that overall losses can be reduced.
    Different parameters of the respective conical friction ring gear can be used as the operating state type. These can be in particular an input torque, an output torque, the overall load, appearing forces or other parameters already mentioned above.
    It is particularly advantageous to check the input and / or output torque and, if necessary, the overall load, since information can be obtained directly on the forces occurring or necessary for the friction connection of the two. gear elements.
    It is therefore advantageous that, for the comparison of the average slope between the idle state and the first operating state or the first operating state and the second operating state, the first operating state is the rotation torque the lower expected under full load and that the second operating state is the highest torque expected under full load. Consequently, for a suitable dimensioning of the characteristic, it is possible to determine the compression force required for the lowest expected torque under full load and for the highest torque expected under full load so that the corresponding characteristic can be designed directly as a line between these two points.
    The advantage of a straight line as a feature has already been explained in detail previously. It can also be between the state of rest or the minimum compression force required so that the gear does not slip and / or does not click when starting and the compression force required for the lowest expected torque under full load load, define a straight line, so that here also the insensitivity to the tolerance can be used when using features with constant slope. This choice of characteristic has the great advantage that a base load is reduced to the minimum absolutely necessary, so that at this level too, such a conical friction ring gear is optimized.
    It may be advantageous to vary the two compression units at their respective compressive strength or at their contribution to the overall compressive force of the compression device by different types of operating states. It is thus possible in this regard to vary a compression unit for example at the input torque or the overall load and a compression unit at the output torque in its compressive force. In this way, the overall behavior of the conical friction ring gear can be adapted in a wide range to the given requirements so that it can be optimized, particularly with regard to its degree of efficiency.
    Other advantages, properties and objectives of the present invention are explained based on the following description of the accompanying drawing. FIG. 1 shows a first friction gear according to the invention in schematic sectional representation; Figure 2 a schematic section of Figure 1; Figure 3 the characteristic of the internal ball unit of the installation according to Figures 1 and 2; Figure 4 the characteristic of the outer ball unit of the installation according to Figures 1 and 2; Figure 5 the characteristic of the entire compression unit of the installation according to Figures 1 and 2; Figure 6 an alternative characteristic of the internal ball unit of the installation according to Figures 1 and 2; Figure 7 a characteristic adapted to the characteristic according to Figure 6 of the outer ball unit of the installation according to Figures 1 and 2; Figure 8 the characteristic of the entire compression unit taking into account the characteristics of Figures 6 and 7 of the installation according to Figures 1 and 2; Figure 9 a possible feature of a compression device; Figure 10 another possible feature of a compression unit; Figure 11 a particularly advantageous characteristic configuration; Figure 12 a second friction gear according to the invention in schematic sectional representation; Figure 13 the characteristic of the input compression unit of the installation according to Figure 12; Figure 14 the characteristic of the output compression unit of the installation according to Figure 12; Figure 15 the characteristic of the entire compression unit of the installation according to Figure 12; Figure 16 a third friction gear according to the invention in schematic section; Figure 17 a fourth friction gear according to the invention in schematic sectional representation; FIG. 18 the characteristic of the input compression unit of the installations according to FIGS. 16 and 17; FIG. 19 shows the characteristic of the entire output compression unit of the installations according to FIGS. 16 and 17 and FIG. 20 shows the characteristic of the assembly of the compression device of the installations according to FIGS. 16 and 17.
    The friction gear shown in FIGS. 1 to 8 and explained, including its characteristics, has an inlet cone 1 and an outlet cone 2, which interact with each other via a friction ring. adjustable friction 3. The inlet cone 1 is then in operative connection with a drive shaft 4 and the output cone 2 with a driven shaft 5. The cones 1, 2 are, in this embodiment, supported in the radial direction by bearings with cylindrical bearings 6 (shown only schematically in Figure 1). In addition, the cones 1, 2 are, in this embodiment, pressed against each other in the axial direction by axial cylindrical rolling bearings 7, so that the necessary compression forces can be applied so that the rotational torque can be transmitted by the friction ring 3 of the inlet cone to the outlet cone 2 and vice versa.
    To tighten or to generate the necessary compression forces, a compression device 8 is furthermore provided between the driven shaft 5 and the output cone 2, whereas, in this embodiment, the input shaft 4 is connected directly to the inlet cone 1. The compression device 8 is able to vary the axial distance between the inlet cone 2 and the cylindrical axial bearing bearing 7 on the output shaft 5 or -at the clamping state- to generate compressive forces varying accordingly due to a spring device 9.
    It is understood that instead of the bearings 6 and 7, also other bearing installations, such as axial angular ball bearings, axial roller bearings, axial grooved ball bearings, Tapered rollers or bearings or similar types of bearings may be combined with each other to hold the cones 1, 2 tight on the one hand radially and on the other sufficiently radially. Hydrodynamic or hydrostatic bearings may also be used, for example.
    In the course of operation, it is possible to adjust the friction ring in an unexplained manner, more precisely here but known, and thus to choose the transmission ratio. It is understood that during operation, the entire installation is subjected in particular to different rotational torques. Since it concerns, in particular as regards the functional connection between the two cones 1, 2, a friction connection, the compression forces must preferably be chosen so high that it does not occur. no slip or only minimal slip on the friction ring 3. On the other hand, unnecessarily high compressive forces would result in a relatively high base load, which would in turn adversely affect the efficiency of the drive gear. friction. Therefore, in the present embodiment, a torque-dependent compression force control is chosen, but the compression force can also be selected as a function of other operating states. As can be seen directly in FIGS. 1 and 2, the output torque, other operating states, such as the global load or the rotational torque, are chosen as adjustment variable for the compression force control. input can be used as it will be demonstrated on the basis of the exemplary embodiments explained hereinafter.
    In the present exemplary embodiment, the compression device 8 comprises two compression units 10 and 11 connected in parallel with their torque measurement and in series with their compression force efficiency, which are respectively represented by inner balls 12 or outer balls 13 (see Figure 2). The balls 12, 13 circulate respectively in ball rails which are provided in compression plates 14, 15 and 16 located on the side of the cone or the side of the shaft.
    In this embodiment, the compression plates 14 and 15 located on the shaft side are arranged in a fixed manner in rotation with respect to the driven shaft 5, while the compression plate 16 located on the cone side is arranged in a fixed manner in rotation with respect to the driven cone 2. On the other hand, the compression plates 14, 15, 16 axially displaceable by means of corresponding sliding bearings 17, 18, 19 on these respective aggregates. While thus a rotational torque can be transmitted from the driven cone 2 through the bearing 19 to the compression plate 16, thence through the balls 12, 13 as well as through the plate of 15 and the bearing 18 to the compression plate 14 and the compression plate 14 through the bearing 17 to the driven shaft 5, the compression plates 14, 15, 16 can move axially against the spring force of the spring devices 9 and against a compression bearing 20 which is supported by an axial cylindrical bearing bearing 21 and a bearing plate 22 on the driven cone 2, and in this way generate according to the cam slide a compression force depending on the torque. In this regard, Figures 1 and 2 show, in the upper peripheral zone of the compression device 8, the installation with a low rotational torque, while the lower zone represents the installation with a high torque, while it can be seen in the lower zone that the compression plate 16 rests, at a higher torque, on a shoulder 23 of the driven cone 2, so that it is easy to influence the characteristic of the set of the installation I according to the torque.
    The cam slides may for example be designed so that the characteristics shown in FIGS. 3 and 4 result. Due to the parallel circuit function of the rotational torque, the characteristic represented in FIG. 5 is obtained. adding due to the parallel circuit at the torque level and the compression force being identical in the two compression units due to the series circuit at the level of the axial compression force. Once the shoulder 23 has reached, only the outer compression unit 11 contributes in its characteristic to the overall characteristic.
    Another characteristic conformation is illustrated in FIGS. 6 to 8, a particularly desirable overall characteristic resulting from the negative slope in the inner compression unit (FIG. 8).
    As can be seen directly in FIGS. 3 to 8, the compression units have, in the present exemplary embodiments, a characteristic operating state-compressive force or a compression torque-compression force characteristic having a substantially constant slope. Thanks to the use of two compression units, a characteristic adapted to the respective requirements can be realized despite these substantially constant slopes. This is possible inter alia because the two compression units 10, 11 provide, at a first torque, respectively a first contribution to the compressive force and, at a second torque, respectively a second contribution to the force. of compression, the difference between the first and the second contribution of the first compression device diverging from the difference between the first and the second contribution of the second compression device 11.
    In general, the friction gears operate within a certain operating range with respect to the different types of operating states. With regard to the compressive force, it then generally becomes imperative that a first defined compressive force exist at the lower end of this gap and a higher compressive force at the upper end of this gap. In order not to have any problems with regard to possible tolerances, it may be advantageous to provide in the operating interval a constant slope of the operating state-compressive force characteristic between these two points. Under these conditions, for example, the characteristic shown in FIG. 9 can be converted with a compression device simply comprising a compression unit, even if the operating interval is simply between 50 Nm and 350 Nm. However, this has the consequence that there remains in the system a considerable base load which significantly reduces the degree of efficiency. This can be counteracted by, for example, giving the cam slide a variable slope, as illustrated in FIG. 10. The characteristic then preferably has, in the operating range from 50 Nm to 350 Nm, a substantially constant slope and drops in below the operating range up to a compressive force around 0 N, especially below 1 Nm, in the state of rest (0 Nm). The basic load in the overall system thus decreases considerably, thereby increasing the overall efficiency level. A variable slope of the cam slide on a compression unit, however, has problems with tolerances, which is solved by the present invention through the use of at least two compression units, as already described above.
    The invention preferably provides that, as illustrated in particular in FIGS. 10 and 11, the operating state-compressive force characteristic has a lower average slope in an operating range (compare 50 Nm to 350 Nm in FIG. ) below this operating range. This reduces the base load of the entire system, increasing the efficiency. On the other hand, installations which show as desired a characteristic similar to the characteristic shown in Figure 5 with an operating range of 100 Nm to 350 Nm are also conceivable. Such a characteristic can also be achieved in particular by virtue of two compression units with a low sensitivity to tolerance.
    To further minimize losses throughout the system, it may be advantageous to reduce the compression force as a function of a second operating state, such as for example the overall load or an input torque. , as illustrated for example in FIG. 11. In this way, the degree of efficiency of the entire system can be further increased.
    This last point can for example be guaranteed by the installation shown in FIG. 12. This installation is substantially equivalent to the installation shown in FIGS. 1 and 2, the cones being, in this installation, in addition to bearing on the cylindrical ball bearings. 6, supported by oblique ball bearings 24 in the axial direction.
    In this embodiment also, the compression device consists of two compression units 25, 26. In contrast to the configuration of the installation according to FIGS. 1 and 2, a compression unit 25 is however provided on the cone. 2 and the other compression unit 26 on the inlet cone 1. In this way, the entire compression unit can both directly determine the input torque that the output torque and transform it in a compressive force. The compression units 25, 26 have the features shown in Figs. 13 and 14. This results in the characteristic shown in Fig. 15, which is substantially equivalent to the characteristic of the output compression unit 25, but continues in a horizontal direction. at low torques depending on the load. The slope of the characteristic of the output compression unit 25 is chosen such that this characteristic cuts the ideal full load characteristic in the operating range, so that a sufficiently high compressive force results. at high output couples. The entire system is further designed so that at full load, the ideal full load characteristic is not under-exceeded even in the lower torque range. In the case of partial loads, the ideal full load characteristic may be underloaded depending on the load, so that the overall load in the system is further reduced, although high compressive forces per se are provided in operation. at full charge. By choosing the slope of the characteristic for the output compression unit 25, one can shift its intersection point with the ideal full load characteristic to thereby reduce the overall losses. As can be seen directly in FIG. 15, the slope of the characteristic of the output compression unit 25 may be chosen not equal to the slope of the ideal full load characteristic in the operating range, since the effects have no effect. not then to be supported by the second compression unit 26.
    This is also possible when coupling the two compression units 25 and 26, as shown by way of example on the basis of FIGS. 16 and 17. These installations are also substantially equivalent to the installations according to FIGS. 2 or 12, aggregates acting identically are also designated identically.
    In these embodiments also, the compression units 25, 26 are respectively disposed in different gear elements of the friction gear as is already the case in the embodiment according to FIG. 12. The compression units 25 , 26 respectively comprise ball devices 27, 28 which respectively rest on compression plates 29, 30 of the input shaft 4 or of the output shaft 5. The balls 28 are supported by on the other hand on a compression plate 31 which is designed axially displaceable but fixed in rotation with respect to the inlet cone 1. This compression plate is at the same time a piston for a hydraulic retro-coupling 32 comprising a piston 33, which is of its the side connected to the compression plate 30. In the compression unit on the outlet side 25, no other compression plate is provided because the balls 27 are disposed of the remainder directly. t on the driven cone 2, a separate compression plate can also be provided at this level to receive the corresponding cam slides.
    The hydraulic backcoupling 32 is guided by passages 34, 35 inside the cones 1, 2, a mechanical system 35 according to the installation of FIG. 17, which interacts with corresponding plates 36, 37 of the compression units 25, 26, which can also be provided instead of such a hydraulic retrocoupling 32.
    Such a coupling makes it possible to choose the output compression unit 25 in its characteristic precisely with the slope of the ideal characteristic in the operating range (see for example FIG. 11). This characteristic is then raised to the desired level by the input compression unit 26. At low loadings therefore a load dependent decrease occurs, so that the overall disposition of the ideal characteristic according to FIG. substantially as shown in Figure 20.
    权利要求:
    Claims (24)
    [1]
    A method of operating a conical friction ring gear having at least one input member (1) and at least one output member (2), which are compressed against each other by means of a compression device (8; 25,26), characterized in that the compression device (8; 25,26) operates with a characteristic operating state-compression force which has between a rest state of the gearing with a conical friction ring and a first operating state, a mean slope other than between the first operating state and a second operating state.
    [2]
    2. Method according to claim 1, characterized in that the first operating state is the lowest expected torque at full load.
    [3]
    3. Method according to any one of claims 1 or 2, characterized in that the compression device (8; 25,26) has a characteristic torque-compression force-force which causes, upon a disappearance of the torque of rotation, a compressive force around 0 N, especially less than 1 N.
    [4]
    A tapered ring gear having at least two operating states, wherein at least one input member (1) and at least one output member (2) are compressed against each other by means of at least one compression device with at least one compressive force varying according to the respective operating state, characterized in that the compression device (8; 25,26) comprises at least two devices compression (10, 11; 25, 26).
    [5]
    Tapered ring gear according to claim 4, characterized in that the first operating state is the lowest torque at full load.
    [6]
    Tapered ring gear according to one of claims 4 or 5, characterized in that the compression device (8; 25,26) has a compression torque-compression force characteristic which, when a disappearance of the torque, a compressive force around 0 N, especially less than 1 N.
    [7]
    Tapered ring gear according to claim 4 to 6, characterized in that the two compression units (10, 11; 25, 26) have different operating state-compressive force characteristics.
    [8]
    Tapered ring gear according to one of Claims 4 to 7, characterized in that the two compression units (10, 11; 25, 26) provide, in the first state of operation, respectively a first contribution to the force of compression and, in the second operating state, respectively a second contribution to the compressive force, the difference between the first and the second contribution of the first compression device diverging from the difference between the first and the second contribution of the second compression device .
    [9]
    Tapered ring gear according to one of Claims 4 to 8, characterized in that the two compression units are designed to act in parallel with the determination of the operating state and / or at the same time. compression force.
    [10]
    Tapered ring gear according to one of Claims 4 to 9, characterized in that the two compression units (10, 11; 25, 26) are designed to act in series at the level of the determination. the operating state and / or the compression force.
    [11]
    A conical friction ring gear according to one of claims 4 to 10, characterized in that at least one compression unit (10, 11; 25, 26) has a characteristic operating state-compressive force exhibiting a substantially constant slope.
    [12]
    Tapered ring gear according to one of claims 4 to 11, characterized in that the compression device (8; 25,26) comprises at least two compression units (10,11; 25,26). coupled to each other.
    [13]
    13. Conical friction ring gear according to claim 12, characterized in that the coupling is mechanically made.
    [14]
    A conical friction ring gear according to claim 12 or 13, characterized in that the coupling is hydrodynamically or hydrostatically performed.
    [15]
    A tapered ring gear according to one of claims 4 to 14, characterized in that a compression unit (26) is arranged on the input side and a compression unit (25) on the output side.
    [16]
    16. Conical friction ring gear having at least two operating states, wherein at least one input member (1) and at least one output member (2) are compressed against one another by means of at least one compression device (8; 25,26) with a compressive force varying according to the respective operating state, characterized in that the compression device has a characteristic operating state- compression force which has, between a state of rest of the conical friction ring gear and a first operating state, a mean slope other than between the first operating state and a second operating state.
    [17]
    17. Conical friction ring gear according to claim 16, characterized in that the first operating state is the lowest expected torque at full load.
    [18]
    Tapered ring gears according to one of claims 16 or 17, characterized in that the compression device (8; 25,26) has a torque-compression-force characteristic which, when a disappearance of the torque, a compressive force around 0 N, especially less than 1 N.
    [19]
    19. A method or gear with a conical friction ring according to any one of claims 1 to 18, characterized in that the operating state is chosen proportionally to the output and / or input torque.
    [20]
    20. A method or gear with a conical friction ring according to any one of claims 1 to 19, characterized in that the second operating state is the highest torque expected at full load.
    [21]
    Method or gear with a conical friction ring according to one of Claims 1 to 20, characterized by at least two compression units (25, 26) whose respective compressive force is varied by different types of states. of operation, such as, for example, the input torque, the output torque, the overall load, forces or the like.
    [22]
    22. A method or gear with a conical friction ring according to any one of claims 1 to 21, characterized in that the compression device (8; 25,26) has a torque-compression-compressive force characteristic which has full load, between the lowest expected torque during operation and the highest expected torque during operation, a lower average slope than below the lowest expected torque in the course of operation; operation.
    [23]
    23. A method or gear with a conical friction ring according to any of claims 1 to 22, characterized in that the compression device (8; 25,26) has a load-dependent compressive torque-force characteristic. .
    [24]
    24. A method or gear with a conical friction ring according to claim 23, characterized in that the compressive force is, at loads below the full load, lower than the compression force under full load.
    类似技术:
    公开号 | 公开日 | 专利标题
    FR2590638A1|1987-05-29|Variable speed drive device with ball coupling
    FR2575258A1|1986-06-27|CONTINUOUSLY ADJUSTABLE REPORT TRANSMISSION OF VARIABLE THROUGH PULLEYS SURROUNDED BY A FLEXIBLE LINK
    FR2655100A1|1991-05-31|ELEMENTS OF MACHINES IN PARTICULAR BEARINGS.
    FR2907495A1|2008-04-25|TURBOMACHINE
    BE1018493A5|2011-02-01|METHOD FOR OPERATING A FRICTION GEAR AND FRICTIONAL GEAR.
    FR2708068A1|1995-01-27|Continuously variable friction transmission.
    FR2644888A1|1990-09-28|MEASURING DEVICE FOR INPUT OF THE BEARING LOAD APPLIED ON A CYLINDER BEARING
    FR2479939A1|1981-10-09|ROLLER-TYPE PLANETARY GEARS HAVING PRELOADING ARRANGEMENT
    CA2319848A1|2002-03-21|Proportional action propulsion system
    FR2602017A1|1988-01-29|CENTRIFUGAL CLUTCH
    FR2597416A1|1987-10-23|Arrangement of a propulsion unit
    FR2681928A1|1993-04-02|DRIVING PULLEY OF A VARIABLE SPEED BELT TRANSMISSION EQUIPPED WITH TOOTHED MASSELOTS.
    EP3245427B1|2018-11-07|Method for manufacturing a propeller reduction gear
    FR2781542A1|2000-01-28|DEVICE AND METHOD FOR REDUCING OSCILLATIONS FOLLOWING AN OSCILLATION PROPAGATION DIRECTION, ESPECIALLY IN A HELICOPTER
    FR2816020A1|2002-05-03|METHOD FOR IMPLEMENTING AND INSTALLING REGULATION OF A CLUTCH
    EP0467758A1|1992-01-22|Multi-frequency vibrator
    CA2034563C|1998-11-24|Variable speed control pulley with transmission diaphragm
    FR2995056A1|2014-03-07|MECHANICAL SYSTEM WITH A UNIDIRECTIONAL CLUTCH, ALTERNATOR AND METHOD FOR MANUFACTURING SUCH A SYSTEM
    FR2922976A1|2009-05-01|HIGH CAPACITY FRICTION DEVICE FOR SLIDING TORQUE TRANSMISSION
    FR2712367A1|1995-05-19|Continuous variable speed drive with conical satellites and centrifugal control.
    FR2518206A1|1983-06-17|CONTINUOUSLY VARIABLE DRIVE ROLLER TRANSMISSION DEVICE
    EP0789151B1|2000-05-10|Hydrodynamic bearing comprising a fixed sliding surface and tiltable sliding pads
    EP0319354B1|1991-03-13|Driving device of a toothed wheel by way of a self-aligning pinion
    FR3078377A1|2019-08-30|TRANSMISSION DEVICE FOR A HYBRID VEHICLE
    FR3096312A1|2020-11-27|Method of controlling a transmission chain
    同族专利:
    公开号 | 公开日
    FR2849684B1|2014-08-22|
    BR0307188A|2005-08-23|
    ITBZ20040001A1|2004-04-02|
    DE10361546A1|2004-07-15|
    FR2849684A1|2004-07-09|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR1317081A|1961-03-08|1963-02-01|Excelermatic|Variable gear ratio transmission|
    FR2181388A5|1972-04-20|1973-11-30|Piv Antrieb Reimers Kg Werner|
    FR2217602A1|1973-02-08|1974-09-06|Cam Gears Ltd|
    EP0466113A1|1990-07-10|1992-01-15|Nissan Motor Co., Ltd.|Continously variable traction roller transmission|
    EP0878641A1|1995-11-16|1998-11-18|Rohs, Ulrich, Dr.|Transmission with cones and friction ring|
    EP0980993A2|1998-08-18|2000-02-23|Rohs, Ulrich, Dr.|Transmission with cones and friction ring and control method for the speed ratio of such a transmission|
    US20020128113A1|2001-01-04|2002-09-12|Tibbles Thomas Theodore|Control system for a continuously variable traction drive|
    KR101171123B1|2003-06-17|2012-08-03|울리히 로스|Friction ring -type transmision and method for operating such a friction ring-type transmission|
    DE10348718A1|2003-06-17|2005-06-30|Ulrich Dr.-Ing. Rohs|Compression device for tensioning intermeshing gearing elements of friction gearing in automobile operated in dependence on detected parameter for preventing slip|
    DE102006023648B4|2006-05-18|2009-08-13|Getrag-Ford Transmissions Gmbh|Pressing device for a cone ring gear|
    法律状态:
    2018-02-15| MM| Lapsed because of non-payment of the annual fee|Effective date: 20170131 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE10300373|2003-01-06|
    DE10300373|2003-01-06|
    [返回顶部]