JP4945821B2 - Continuously adjustable conical disk-type winding transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention is a steplessly adjustable conical disc-type winding transmission device, which is wound around by one winding means, each having two conical shapes that are non-rotatably coupled to one shaft. Disc pairs are provided, both conical disc pairs each having at least one conical disc adjustable in the axial direction, the spacing between the conical disc pairs being reversed due to a change in transmission ratio It is adjustable in direction and is further provided with a guide device, the guide device comprising a guide component for guiding the movement of the tensioning section of the winding means.
[0002]
[Prior art]
A conical disk-type winding transmission of the type mentioned at the outset is known, for example, from German Offenlegungsschrift 10017005, which is completely relevant in content. In this transmission, the guide component is formed as a guide rail that houses the outside and the inside of the tensioning section of the winding means with a slight gap therebetween. The guide rail is pivotable about a pin fixed to the housing by a long hole, and is movable relative to the pin. Thus, the guide rail can follow the change in the geometric position of the winding means when adjusting the transmission ratio. By means of this guide rail, the transverse vibrations of the winding means, which can be formed, for example, as chains or belts, are significantly limited or sufficiently prevented with respect to their amplitude. However, due to the wear of the rails during the service life of the transmission, the transverse vibration of the tensioning section causes undesirable dimensions. Furthermore, an operating state in which lateral vibration can occur even in the loose section, that is, an operating state during reverse running can be generated. Even under normal operating conditions, transverse vibrations in the loose section based on different causes were observed. Vibrations in the winding means not only cause acoustic problems, but also reduce the service life of the transmission. This is because vibrations cause undesired stress increases and, in particular, increased surface pressure during entry into the conical disk.
[0003]
[Problems to be solved by the invention]
The object of the present invention is to improve the continuously adjustable conical disc-type winding transmission of the type mentioned at the outset so that lateral vibrations are prevented not only in the tension section but also in the loose section. That is.
[0004]
[Means for Solving the Problems]
In order to solve this problem, in the configuration of the present invention, the guide device is arranged between the two guide components and another guide component for guiding the movement of the slack section of the winding means. And a holding device for holding the component in a movable manner.
[0005]
【Effect of the invention】
According to the present invention, the guide component acts not only on the tension section of the winding means but also on the loose section, thereby preventing lateral vibration. Both guide components are held by holding means arranged between them to save space. As a result, both guide components automatically follow changes in the geometrical position or movement path of the winding means when the gear ratio changes.
[0006]
The feature of claim 2 provides the advantage that the suppression of transverse vibrations over the entire service life of the winding transmission is reliably maintained.
[0007]
According to claim 3, the structural structure of the first advantageous configuration of the holding device is characterized.
[0008]
According to claim 4, another advantageous configuration of the holding device is characterized. This holding device is improved in an advantageous manner by the features of claims 5-11.
[0009]
With the features of claim 12, proper lubrication and cooling of the transmission can be achieved. This lubrication and cooling is advantageous for the efficiency and sustainability of the transmission.
[0010]
The features of claim 12 are improved in an advantageous manner by the features of claims 13-15.
[0011]
Overall, the present invention significantly improves the operating characteristics of conical disk-type winding transmissions that are increasingly used in automobiles for good efficiency and high comfort.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
In the following, embodiments of the present invention will be described in detail with reference to the drawings.
[0013]
According to FIG. 1, the conical disc-type winding transmission has two conical disc pairs 4,6. Both conical disk pairs 4 and 6 are rotatable about axes 8 and 10. Both conical discs of each conical disc pair have conical surfaces located opposite each other. Since the axial spacing of both conical surfaces is variable by moving at least one conical disc in the axial direction of the associated axis, it is provided with a pin supported on the conical surface of the conical disc pair. The effective radius through which the winding means 12, for example the link chain circulates, is variable in accordance with the distance between the two conical disks of one conical disk pair. In the state of FIG. 1, the distance between the two conical disks of the left conical disk pair 4 is the maximum, and the distance between the two conical disk pairs of the right conical disk pair 6 is the minimum. The winding means 12 is wound around the left conical disk pair with a minimum radius and is wound around the right conical disk pair with a maximum radius. Accordingly, the ratio of the rotational speed of the right conical disk pair to the rotational speed of the left conical disk pair is minimized. The described conical disc type transmission is known per se in terms of its structure and its function, and therefore will not be described in detail.
[0014]
For the perfect function of the transmission, it is advantageous if lateral vibrations of the winding means 12, i.e. vibrations transverse to the direction of travel of the winding means 12, are prevented. For this purpose, two guide components 14, 16 are arranged inside the winding means 12 between the conical disk pairs. As is clear from the partial view a) shown in section along the plane AA in FIG. 1, each guide component 14, 16 is formed in a U shape as a whole in cross section. And a contact surface 18 for contacting the winding means 12 and a side web 19 for guiding the winding means 12 at the side as required.
[0015]
The contact surface 18 is preferably formed in a slightly spherical or convex shape in the direction of movement of the winding means 12, so that when the guide component is crimped to the inner side of the winding means 12, the winding means 12. Touches the contact surface softly or gently.
[0016]
Different devices may be provided for crimping the guide components 14, 16 to the winding means and holding the guide components. These devices act on the guide components in opposite directions, respectively, in order to crimp and hold both guide components together on the winding means. Such a holding device may have different types of springs and may be operated hydraulically or pneumatically.
[0017]
According to FIG. 1, an advantageous arrangement of the holding device has a hydraulic cylinder 20 arranged between the conical disc pairs 4, 6 and the guide components 14, 16. The hydraulic cylinder 20 is fixed to the transmission housing 24 by a fixed eye 22 outside the pair of conical discs in the axial direction.
[0018]
In both ends of the hydraulic cylinder 20, the pistons 26 that face the guide components 14, 16 work. The piston rod 28 of this piston 26 ends with a ball head 30. Guide components 14 and 16 are supported on the ball head 30 jointly by ball sockets.
[0019]
Since the inner chamber of the hydraulic cylinder 20 is loaded with hydraulic pressure through the inflow passage 31, the piston 26 is preloaded or preloaded outward and the guide components 14, 16 are wound from the inside. It is pushed away so as to contact the hanging means 12.
[0020]
In FIG. 1, different geometric positions or travel paths are indicated by broken lines. The winding means 12 occupies these travel paths according to the transmission gear ratio. As is evident directly from FIG. 1, the guide components 14, 16 follow the adjusting movement of the winding means and maintain positive contact with the winding means by means of a joint connection with the piston rod. Yes. No post-adjustment work is required over the entire service life, whereby lateral vibrations are suppressed by the reliable contact of the guide component with the winding means. The described apparatus does not require any additional structural space. This is because, apart from fixing the hydraulic cylinder, this device is arranged completely between the conical disk pairs inside the winding means. It has been found that an additional damping element that reliably suppresses high-frequency vibrations may be formed, if necessary, for example on the piston rod or at the joint between the ball head and the ball socket.
[0021]
Due to the operating characteristics and service life of the conical disc-type winding transmission of the type described above, in particular the pin 32 in which the winding means contacts the conical surface 34 (see partial view b) of the conical disc at the end face. In the case of a metal chain with (see partial view a)) perfect lubrication and cooling are important. For this purpose, it is particularly advantageous if the hydraulic cylinder 20 can be loaded with a hydraulic medium, possibly under pressure related to the speed and torque of the transmission. A hydraulic medium passage 36 extends from the inside of the hydraulic cylinder through the piston 26 and the piston rod 28. The hydraulic medium passage 36 continues to the hydraulic medium passage 38. The hydraulic medium passage 38 is formed in the guide components 14 and 16. The transition between both hydraulic media passages 36, 38 through the ball joint joint has been found to be fluid tight, for example by the ball head being in intimate contact with the ball socket in an advantageous manner. The hydraulic medium passages formed in the guide components 14, 16 are the run-in points of the winding means 12 on each conical disc pair (this run-in point is the normal type in the counterclockwise direction according to FIG. 1). In the guide component 14 on the left side and the guide component 16 on the right side), with two openings 40 and 42 (see partial view b) respectively. As formed, the hydraulic medium is sprayed directly onto the conical surface where the winding means engages. By setting the dimensions of the hydraulic medium passage cross-section according to the purpose, it is first ensured in the hydraulic cylinder 20 that a sufficient pressure is maintained for crimping the guide component to the winding means. Second, it is guaranteed that the hydraulic medium will flow out sufficiently to ensure lubrication or cooling.
[0022]
Advantageously, the holes formed through the contact surface 18 can also supply the hydraulic medium to the contact surface, so that there is already effective lubrication there and at the same time winding means along the guide surface. Movement is performed on the liquid film sufficiently without friction.
[0023]
The described apparatus can be varied and improved in a wide variety of ways. For example, the openings 40 and 42 can be omitted, and the hydraulic medium can be supplied to all guide surfaces. This hydraulic medium is entrained by the winding means and conveyed to the run-in place of the winding means on the conical disc pair. To this end, the overall U-shaped configuration of the guide component shown in FIG. 1 is advantageous. A further advantage of this arrangement is that optimum lubrication and cooling are ensured regardless of the direction of rotation of the winding means. The hydraulic medium passages 36, 38 may be formed in the guide components 14, 16 on both sides of the joint joint, which need not be formed as balls. In this case, one valve device can be incorporated in each joint joint between the piston rod and the guide component. Since this valve device operates the left outflow opening or the right outflow opening in accordance with the rotational direction of the transmission, the lubrication is switched in accordance with the rotational direction of the transmission.
[0024]
By directly lubricating or cooling the transmission in the manner described, at the entry point of the winding means on the conical disc pair, the operating characteristics of the winding transmission, for example the torque transmission capacity of the winding transmission, and The acoustic characteristics of the winding transmission and the service life of the winding transmission are improved.
[0025]
FIG. 2 shows a schematic cross-sectional view of a modified arrangement of the guide device for the winding means 12 compared to FIG.
[0026]
According to FIG. 2, the guide components are formed as guide rails 50, 52. The guide rails 50 and 52 accommodate the winding means 12 outside and inside. As is clear from the partial view a) (cross-sectional view along the plane AA in FIG. 2), the guide rails 50, 52 have a U-shaped cross section. In this case, a U-shaped base 54 connects the legs 56 and 58 to each other. Both legs 56, 58 have contact surfaces located facing each other for contact with the winding means 12. Since both the leg portions 56 and 58 are spaced apart from each other so that the winding means 12 is accommodated with slight play, lateral vibration can be reliably suppressed. The contact surface located opposite the winding means 12 is preferably slightly spherical or convex in the direction of movement of the winding means.
[0027]
Both guide rails 50 and 52 are connected to each other in a joint manner via connecting rods 60 and 62 that overlap and intersect each other. In this case, as can be seen directly from FIG. 2, the connecting rods 60, 62 have a corresponding change in the position of one guide rail caused by a change in the gear ratio of the transmission. Since it is guaranteed that a mirror-symmetrical position change is inevitably caused, the connection via the crossed connecting rods 60 and 62 requires a change in the movement of both sections of the winding means 12 when the gear ratio is changed. The movements of both guide rails are linked to each other.
[0028]
Automatic positioning of the guide rails 50, 52 is achieved by the connecting rods 60, 62. This automatic positioning will be described in detail with reference to FIGS. B), c) and d).
[0029]
According to FIG. B), the rightward mobility of the guide device comprising the guide rails 50, 52 and the connecting rods 60, 62 is limited by the upper guide surface of the guide rail coming into contact with the winding means 12. Has been. According to FIG. C), the leftward mobility is limited by contact of the guide surfaces inside the guide rails 50, 52 with the winding means 12. Therefore, the lateral mobility of this system is limited.
[0030]
The tilt angle of the guide rails 50 and 52 is automatically adjusted by the left end or the right end of one guide rail coming into contact with the winding means each time and the guide rail tilts appropriately. . In this case, the other guide rail necessarily follows this tilt symmetrically or in the opposite direction.
[0031]
The lateral movement of the guide device shown in FIGS. B) and c) is such that the transmission operates with a gear ratio not equal to 1, i.e. the transmission is tilted by the winding means 12. It is limited only when it operates with a section to travel. When the gear ratio is equal to 1, the tensioning section and the loosening section of the winding means travel in parallel to the connecting line between the two axes 8 and 10, so that the left and right mobility of the guide device is limited. It has not been.
[0032]
In order to eliminate this situation, according to FIGS. 3 to 5, guide rails 64, 66 are provided on the guide rails 50, 52 arranged between the conical disks of the conical disk pairs 4, 6, respectively. It has been. Both guide-equipped portions 64 and 66 protrude on both sides between the peripheral edge 68 of the conical disc of the conical disc pair. When the guide rails 50 and 52 move left and right based on the entrainment by the winding means according to the travel direction of the winding means 12 at a gear ratio equal to 1, the guide-equipped portions 64 and 66 have the outer diameter or cone of the conical disc. It contacts the outer diameter of the peripheral edge 68 of the shaped disk, thus limiting the mobility of the guide rail. Due to the weak force acting in this case, there is actually no friction due to the appropriately spherical configuration (curvature R in FIG. 5) of the contour of the guide-equipped portion and the liquid present at the peripheral edge 68 during operation. A purely hydrodynamic liquid reservoir can be obtained. It has been found that the peripheral edge 68 of the conical disc can be ground to obtain a high surface quality and thereby avoid mixed friction or wear. In the changed configuration, the guide-attached portion may be formed on the connecting rod.
[0033]
FIG. 6 shows a modified configuration of the guide device compared to FIG.
[0034]
In this configuration, the guide rails 50 and 52 are not formed so as to accommodate the winding means 12 inside and outside, but have base rails 70 and 72. Guide plates 76 and 78 are supported on the base rails 70 and 72 via springs 74. Both guide plates 76 and 78 are preloaded or preloaded elastically with respect to the winding means 12 from the inside. The position of the base rails 70, 72, in which the guide rails formed as guide plates 76, 78 are fixed via springs 74 and possibly additional pins, holes, guides, is similar to the configuration of FIG. The connecting rods 60 and 62 are arranged so as to intersect with each other. As is apparent from FIG. 6, the distance between the pivot points 80 and 82 provided on the base rail 72 is sized larger than the distance between the pivot points 84 and 86 of the base rail 70. Thus, the intersection 88 of the connecting rods 60, 62 is offset upwards from the coupling plane shown in FIG. 6 including the axes 8, 10 of the conical disk pair. In this way, the support pins 90 passing through the longitudinal slits 92 and 94 formed in the connecting rods 60 and 62 can be fixed to the transmission housing 24 outside the conical disk pairs 4 and 6. Thus, the bearing pin 90 serves to hold the guide device comprising the components 14, 16, 60, 62 in place. In this case, the guide components 14 and 16 or the guide plates 76 and 78 have a degree of freedom in order to follow the adjusting movement of the winding means 12 when the gear ratio changes.
[0035]
As will be apparent, the guide plates 76 and 78 are each curved outwardly with a large radius of curvature, so that gentle and uniform inward winding means that reliably suppress lateral vibrations. Touch is guaranteed.
[0036]
In the configuration shown in FIG. 2, the connecting rods 60 and 62 can be formed with long holes or longitudinal slits similar to the longitudinal slits 92 and 94. In this longitudinal slit, a pin for connecting both connecting rods to each other is arranged. However, in this case, in the configuration shown in FIG. 2, the pin is not fixed to the transmission housing.
[0037]
2 and 6, since the lubricating medium and the hydraulic medium as the cooling medium can be supplied to the guide rail, the entry position of the winding means around the conical disk is directly cooled each time. ing. In the configuration shown in FIG. 6, the fluid supply can be made through the support pin 90. In the configuration shown in FIG. 2, the hydraulic medium can be sprayed from the housing onto the guide rail, for example.
[0038]
Steplessly adjustable conical disc-type winding transmission device, two conical disc pairs 4 each non-rotatably coupled to one shaft, wound by one winding means 12 , 6 and the two conical disc pairs 4, 6 are each provided with at least one conical disc which is adjustable in the axial direction, the spacing between the conical disc pairs being such that the transmission ratio changes. Therefore, guide devices 14, 16, 20 are provided, and the guide devices 14, 16, 20 are arranged to guide the movement of the tensioning section of the winding means. In the type comprising a part, the guide device 14, 16, 20 is between another guide component for guiding the movement of the slack section of the winding means 12 and both guide components 14, 16. Arrangement The, characterized in that it has a holding device 20, 26 for retaining the two guide components movably adjustable conical disc type belt-driven continuously variable type.
[0039]
The present invention is not limited to the illustrated embodiment. On the contrary, many variations are possible within the framework of the invention.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a first configuration of a winding transmission device taken perpendicular to the axis of a conical disk pair.
FIG. 2 is a cross-sectional view of another configuration of the conical disk type winding transmission.
3 is a cross-sectional view of the conical disk-type winding transmission device of FIG. 2 when the gear ratio is changed.
4 is a plan view of the transmission device shown in FIG. 3. FIG.
FIG. 5 is a detailed view of FIG. 3;
6 is a view showing another configuration of a conical disk-type winding transmission similar to FIG. 3. FIG.
[Explanation of symbols]
4 conical disc pairs, 6 conical disc pairs, 8 axis, 10 axis, 12 winding means, 14 guide component, 16 guide component, 18 contact surface, 19 web, 20 hydraulic cylinder, 22 fixed eye, 24 Housing, 26 piston, 28 piston rod, 30 ball head, 31 inflow passage, 32 pin, 34 conical surface, 36 hydraulic medium passage, 38 hydraulic medium passage, 40 opening, 42 opening, 50 guide rail, 52 guide rail, 54 base, 56 leg, 58 leg, 60 connecting rod, 62 connecting rod, 64 guide mounting section, 66 guide mounting section, 68 peripheral edge section, 70 base rail, 72 base rail, 74 spring, 76 guide plate, 78 guide Plate, 80 pivot points, 82 pivot points 84 pivot point 86 pivot point, 88 intersection, 90 bearing pin, 92 longitudinal slit,
94 Longitudinal slit

Claims (15)

Steplessly adjustable conical disc-type winding transmission device, which is provided with two conical disc pairs each non-rotatably coupled to one shaft, wound by one winding means Both conical disc pairs each have at least one conical disc adjustable in the axial direction, and the spacing between the conical disc pairs can be adjusted in the reverse direction for changing the transmission ratio A guide device is provided, the guide device comprising a guide component for guiding the movement of the tensioning section of the winding means, wherein the guide device comprises the winding means A separate guide component for guiding the movement of the slack section and a holding device arranged between the guide components for movably holding both guide components, Component, characterized in that is adapted to be pressure-bonded to the wrapping means from the interior of the winding unit by the holding device, adjustable conical disc type belt-driven continuously variable type.   The holding device has a hydraulic cylinder fixed to the transmission housing, and two pistons work in opposite directions in the hydraulic cylinder, and each piston is connected to a guide component. 2. A conical disk-type winding transmission according to claim 1, which is coupled in a formula.   The guide components are jointly connected to each other by two connecting rods intersecting each other so that the guide components are arranged symmetrically with respect to each other with respect to the plane having the axis of the conical disc pair. The conical disk-type winding transmission according to claim 1.   4. The conical disk-type winding transmission according to claim 3, wherein the connecting rod has longitudinal slits that overlap and intersect each other, and a bearing pin is engaged in the longitudinal slit.   5. A conical disk-type winding transmission according to claim 3 or 4, wherein the guide component is formed as a guide rail for accommodating the outside and the inside of the winding means between each other.   At least one guide rail and / or at least one connecting rod is provided with a guide portion, which restricts the mobility of the guide rail in the direction of the distance between the two conical disc pairs. 5. A conical disk-type winding transmission device according to claim 4.   The conical disk-type winding transmission device according to claim 6, wherein the guide-attached portion is movable in contact with a peripheral edge portion of one conical disk.   8. The conical disk-type winding transmission device according to claim 7, wherein a contact surface of the guide-attached portion that can contact the peripheral edge of one of the conical disks is formed in a spherical shape.   5. A conical disc type winding according to claim 3 or 4, wherein the guide component has a guide plate which is elastically preloaded towards the winding means on the outside located opposite the winding means. Hanging transmission device.   5. A conical disk-type winding transmission according to claim 4, wherein the support pin is fixed to the transmission housing.   The distance between the connecting points of the connecting rod and the guide component, measured along the guide component, is different and the bearing pin is transmitted at a distance from the plane having the axis of the conical disc pair. The conical disk-type winding transmission according to claim 10, which is fixed to the device housing. 3. A conical disk-type winding transmission according to claim 2 , wherein the hydraulic medium passage leads to a guide component for supplying hydraulic medium to a surface for guiding the movement of the winding means.   The guide component surrounds the winding means in a U-shape so that the hydraulic medium supplied to the guide component is entrained by the winding means and each of the winding means on the conical disc pair. The conical disk-type winding transmission according to claim 12, wherein the conical disk-type winding transmission is adapted to be supplied directly to the entry point.   13. A conical disk-type winding transmission according to claim 12, wherein the hydraulic medium passage leads to a run-in point of the winding means on the conical disk pair.   14. A conical disk-type winding transmission according to claim 2, 11, 12, or 13, wherein the hydraulic medium passage extends from a hydraulic cylinder.

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