TW201712252A - Continuously variable transmission and vehicle comprising a CVT - Google Patents

Abstract

The invention relates to a continuously variable transmission (CVT) and a vehicle comprising a CVT of said type. The CVT (1) comprises: a V-pulley (2) that includes an axially stationary cone pulley (20) and an axially movable cone pulley (21); an axially slidable inner sleeve (53) that is connected to the axially movable cone pulley (21) so as to rotate therewith and be translationally coupled thereto; and an axially slidable outer sleeve (54) that is arranged coaxially to the inner sleeve (53), is translationally coupled thereto, and is rotationally disconnected therefrom. The outer sleeve (54) includes a rotationally fixed threaded nut (8) designed to engage and cooperate with a rotatable, translationally stationary lead screw (7) in order for an axial position of the axially movable cone pulley (21) to be adjusted so that said cone pulley (21) is coupled to the outer sleeve (54) for translation and conjoint rotation therewith.

Description

CVT transmission and vehicle with CVT transmission

The present invention relates to a CVT transmission and a vehicle including a CVT transmission. More particularly, the present invention relates to an apparatus for actively and centrifugally adjusting the transmission of a transmission of a CVT transmission.

Different designs of CVT (Continuously Variable Transmission, English: transmission with steplessly variable transmission ratio) are known from the prior art. With a continuously variable transmission, a suitable gear ratio can be achieved in the vehicle compared to a transmission with a fixed gear. A particular application area of this type, in particular a centrifugally actuated-CVT transmission, is a small vehicle such as a two-wheeled vehicle, a tricycle, a so-called spurt, a snowmobile, a Quad (four-wheeled all-terrain vehicle) or a scooter.

In the case of such CVT transmissions, a mechanical centrifugal force regulator is typically used to adjust the position of the belt on the pair of tapered washers. This mechanical centrifugal force regulator is provided on the primary side of the CVT transmission. This primary side is placed directly on the crankshaft. The secondary side and the primary side are balanced in torque and balanced. The primary side and the secondary side are coupled, for example, through a belt as a power transmission member. The centrifugal force of the mechanical centrifugal force regulator is related to the weight load and its rotational position is moved in relation to the rotational speed and thereby changes the axial distance between the two pulleys which are conical and opposite, also referred to as conical spacers. Thereby the belt is forced to run at a radius determined by the track.

That is, the centrifugal force of the centrifugal force adjuster moves its radial position according to the rotational speed, thereby changing the axial distance between the two tapered washers, thereby changing the transmission of the transmission.

A disadvantage of such a device is that it is not possible to have controllable or adjustable interventions in the transmission of the CVT transmission. Therefore, the prior art CVT transmission with a centrifugal force regulator is typically not operated at the optimum point, thus increasing fuel consumption and/or emissions of the vehicle. In view of this, it is advantageous to utilize this potential when using a centrifugally regulated CVT transmission to reduce fuel and reduce emissions.

In addition, in terms of vehicle dynamics, there is no optimal design for centrifugal force-regulated CVT transmissions. In particular, when the vehicle accelerates from a standstill and accelerates during acceleration of the vehicle (eg, from the first speed to the second speed), the transmission ratio based on the non-optimal selection of the centrifugally-adjustable CVT transmission is still There is a great room for improvement.

Furthermore, there is no direct connection between the driver, the control unit and the transmission drive. That is, active drive selection is not possible through the driver. The change in gear ratio is currently determined by the mechanical structure and characteristics of the CVT transmission.

An advantage of the CVT transmission of the present invention having the features of claim 1 is that, according to the present invention, the transmission of the CVT transmission can be adjusted independently and actively and centrifugally.

According to the invention, this is achieved by proposing a CVT transmission having a tapered washer pair comprising an axially fixed tapered washer and an axially movable tapered washer, movable with the axial direction The tapered gasket is coupled to the axially movable inner sleeve and the axially movable outer sleeve in a rotationally and translationally coupled manner, the outer sleeve being coaxially disposed with the inner sleeve, and The inner sleeve is rotationally coupled and rotationally decoupled from the inner sleeve, wherein the outer sleeve has a spindle nut constructed to be torsionally rigid, the spindle nut being arranged to adjust the axially movable tapered washer The axially positionally rotatable and translationally fixed threaded spindles engage and cooperate to couple with the outer sleeve in a rotationally fixed and translational manner.

Through these measures, the transmission of the CVT transmission can be changed and adjusted independently and actively and centrifugally. The specific way is that the inner sleeve and the outer sleeve, which are coupled and rotatably decoupled from each other, are translatable and translatably coupled to the outer sleeve by a torsionally and translating spindle nut along the same axis of rotation. The axial position is adjusted by engaging a rotating and fixed screw spindle to the spindle nut such that the position of the inner sleeve and the outer sleeve on the rotating shaft can also be transmitted through the axially movable cone The coupling of the shaped spacers is actively and centrifugally adjusted independently to cause the transmission of the CVT transmission to match.

These sub-items show a preferred refinement of the invention.

Preferably, the outer sleeve is substantially rotationally symmetric with the axis of rotation of the pair of tapered washers on which the spindle nut is disposed. The rotational symmetry of the outer sleeve and the arrangement of the spindle nut on the rotating shaft of the tapered washer can achieve a particularly compact construction of the CVT transmission of the present invention.

According to another preferred embodiment, the outer sleeve has a casing sleeve and at least one first casing end surface. The spindle nut is preferably formed on the end face of the first housing or in the end face of the first housing. This can be achieved by any fixing scheme of the spindle nut. In particular, the spindle nut can be constructed in one piece in the form of a material in the end face of the outer sleeve. These measures have advantages in terms of production and installation, since only a particularly small number of components need to be combined and fixed together.

According to another advantageous embodiment of the CVT transmission of the present invention, the housing sleeve has at least one through hole, wherein the at least one through hole is arranged to accommodate the recoil starter after the CVT transmission is installed (ie by At least one component of the foot-operated starting device and in particular a double gear of the recoil starter transmission are movably and rotatably supported and/or retained on the threaded spindle. Through these measures, a conventional recoil starter can be integrated into the CVT transmission of the invention in a particularly simple manner.

To this end, the threaded spindle preferably has a journal on one end that is arranged to movably and rotatably support and/or retain at least one component of the recoil starter.

According to another embodiment, the housing sleeve has a bell shape comprising a first region of larger diameter and a second region of smaller diameter, wherein in particular the first region faces the inner sleeve and is arranged with the inner sleeve The barrel coupling and/or the second region has a first housing end face that includes the spindle nut. The measures can also achieve a particularly compact construction, since the first region of the outer sleeve can include or enclose a portion of the inner sleeve due to the bell shape of the outer sleeve of the outer sleeve, such that the inner sleeve The barrel and the outer sleeve nest within each other to occupy a particularly small space.

According to another embodiment, the CVT transmission is constructed with an adjustment device for adjusting the axial position of the axially movable conical gasket, wherein the adjustment device is coupled to the outer sleeve through the threaded main shaft and the spindle nut, Wherein the adjustment device has an adjustment transmission for rotating the positionally fixed threaded spindle, and wherein the adjustment device has an actuator and is arranged to be in operation, through the adjustment of the transmission, the threaded spindle and the spindle nut Acting to translate the rotation in the actuator into the rotation of the threaded spindle and the axial movement of the translation of the spindle nut and the axially movable tapered gasket. The arrangement of the adjustment device with the actuator can actively influence the threaded spindle and the controllable and highly reliable adjustment The tapered gasket accommodates the mandrel for the distance between the spacers.

A further embodiment of the CVT transmission according to the invention is provided with a torque arm for and arranged to support and hold the outer sleeve in a rotationally fixed manner. By means of these measures, the particularly high functional reliability of the CVT transmission of the invention is achieved.

When the transmission housing with the socket is constructed in accordance with a further advantageous embodiment, a particularly simple design of the torque arm with a particularly low production and installation cost is produced, wherein the outer sleeve is The first housing end face is received in the socket of the transmission housing, and wherein the first housing end surface and the socket are not rotationally symmetric and at least segmentally complementary to each other, thereby transmitting the first housing The end faces and the sockets of the transmission housing engage each other along the circumference of the socket to effect the torque arm and to achieve and support a positionally correct mounting.

A further way to further improve the operational reliability of the CVT transmission of the invention is that, according to a further advantageous embodiment, the CVT transmission is constructed with a control unit which is arranged to actuate the adjustment device in order to The transmission is changed on the opposite side.

The measure of the invention can also be applied to CVT transmissions which are otherwise constructed in a conventional manner, in particular constructed with at least one centrifugal force element movably arranged on the axially movable conical spacer and A support member disposed on the axially movable tapered gasket and coupled to the drive shaft or the crankshaft, wherein the centrifugal force member is disposed between the support member and a rear wall of the axially movable tapered gasket.

The invention also relates to a vehicle comprising a CVT-transmission device according to the invention, wherein the vehicle is in particular a small vehicle, in particular a two-wheeled vehicle, a tricycle, a snowmobile, a Quad or the like.

Embodiments of the present invention will be described in detail with reference to the drawings.

1‧‧‧CVT transmission

2‧‧‧Conical gasket pair

3‧‧‧ centrifugal force components

4‧‧‧Support elements, support plate

5‧‧‧Adjustment device

6‧‧‧Control unit

6-1‧‧‧Measurement line/control line

6-2‧‧‧Measurement line/control line

7‧‧‧Threaded spindle/spindle

7a‧‧‧End/spindle end, distal end

7b‧‧‧External thread/thread

7c‧‧‧ spindle journal/ journal

8‧‧‧Spindle nut/nut

8a‧‧‧Drilling

8b‧‧‧ internal thread

9‧‧‧Torque support/torque arm

10‧‧‧ Internal combustion engine/motor

11‧‧‧ crankshaft

12‧‧‧Inclusive components/drive belts

13‧‧‧Drive member/second tapered washer pair

14‧‧‧Shear/transmission housing

14b‧‧‧ socket

14c‧‧‧ bump

14d‧‧‧through hole

20‧‧‧Conical gasket/pulley

21‧‧‧Conical gasket/pulley

22‧‧‧ Back wall

41‧‧‧Clamping sleeve

50‧‧‧Executive agency

51‧‧‧Drive shaft

52‧‧‧Adjustment of transmission / transmission

53‧‧‧Inner sleeve/sliding bushing

54‧‧‧Outer sleeve

54-1‧‧‧Region/Section

54-2‧‧‧Zone/Section/Shell Section

54a‧‧‧Sheath cover/coat

54b‧‧‧Shell end/end face

54c‧‧‧shell end face

54d‧‧‧ Notch

54i‧‧‧Internal

55‧‧‧ Radial Bearings/Bearings

57‧‧‧ Groove/bell groove/through hole/window

58‧‧‧ bell groove/through hole

60‧‧‧Back-up starting device / recoil starter / recoil starter

62‧‧‧Backlash starter transmission / gear transmission / recoil starter transmission

64‧‧‧Transmission gear/reverse starter transmission gear

65‧‧‧Brake spring

66‧‧‧Backlash starter nut / recoil starter gear

67‧‧‧Back-up starter double gear / recoil starter gear / double gear, components

68‧‧‧Flange ring

100‧‧‧ Vehicles

A‧‧‧ position

A'‧‧‧ position

B‧‧‧ position

B'‧‧‧ position

D‧‧‧Distance

D1‧‧‧diameter

D2‧‧‧diameter

X‧‧‧Axis axis, rotating axis

X-X‧‧‧Rotary axis

1 is a schematic view of a portion of an embodiment of a CVT transmission of the present invention in accordance with a block diagram; FIGS. 2 and 3 are partial perspective sectional views of another embodiment of the CVT transmission of the present invention; FIGS. 4 to 8 are A perspective side view and a partial cross-sectional side view of another embodiment of the CVT transmission of the present invention, that is, in the outer sleeve, the threaded spindle and the recoil starter; FIGS. 9 to 11 are CVT transmissions of the present invention. Another embodiment of the device focuses on a detailed perspective view on the torque arm.

Embodiments of the present invention will now be described in detail with reference to Figs. The same, the same or equivalent components are denoted by the same component symbols, whether or not repeated in the case.

In general, one aspect of the present invention is to provide a solution for a particularly electronically controlled device that is integrated or integrated into the particular centrifugal force adjustment system and that can be used to adjust the target transmission of the CVT transmission.

This achieves the optimum operating point of the drive train in terms of consumption and vehicle dynamics.

In addition, the optimum design of the CVT transmission can be achieved by the present invention in terms of expansion of expansion in the direction of overdrive, optimization of belt tensioning, and other measures to improve the operating efficiency of the CVT transmission.

Thus, in accordance with the present invention, such centrifugal force weights are optionally also desirable. Keeping In the case of an existing centrifugal force mechanism, the actuation power can be reduced and the cost for the electronic control unit can be reduced.

That is, the device can be integrated into a conventional centrifugal force adjustment system without major structural changes.

Other general aspects and embodiments of the present invention will be further described in detail below with reference to the drawings.

Figure 1 is a schematic illustration of a portion of a first embodiment of a CVT transmission 1 of the present invention in accordance with the type of block diagram.

An inner sleeve 53 is attached to the drive shaft or the crankshaft 11 driven by the internal combustion engine 10 through the clamp sleeve 41 or another fixing member. An axially movable tapered washer 21, also referred to as a second tapered washer, is fixed to the inner sleeve 53 in a rotationally fixed manner. The inner sleeve 53 and the clamping sleeve 41 are arranged coaxially to each other—particularly with respect to the same axis of symmetry X, which coincides with the axis of rotation X of the same rotating shaft and the axially movable tapered washer 21. In particular, the inner sleeve 53 and the clamping sleeve 41 are at least partially plugged into one another, the inner sleeve 53 surrounding the clamping sleeve 41 . The inner sleeve 53 is slidable along the clamping sleeve 41 so as to be axially adjusted along its axis of rotation X in its position.

The axially movable tapered washer 21 and the inner sleeve 53 are connected, which are slidable together along the clamping sleeve 41.

The axially movable tapered washer 21 is axially disposed with a fixed tapered washer 20, which is also referred to as a first tapered washer 20 and is axially movable with a tapered pad The sheets 21 are coupled in a rotational manner and decoupled in a translational manner.

In operation, the device consisting of the first and second tapered spacers 20 and 21 of the tapered spacer pair 2 is driven by the drive shaft or crankshaft 11 driven by the motor 10 to drive the tapered spacer. A containment member 12 running on a radius of 20, 21, such as a belt or the like, for driving a drive member 13 on the drive side, such as a corresponding second pair of tapered spacers 13, in this case the drive member In particular for the purpose of driving a wheel or the like, for example, it is connected to a drive shaft.

A support element 4 is mounted on the clamping sleeve 41 so as to form an accommodation space for one or several centrifugal force elements 3 in the form of one or several spheres or rollers by the bottom surface of the second tapered spacer 21. In the case of the support element 4 on the clamping sleeve 41, the centrifugal force adjustment by means of such a centrifugal force element 3 is not necessary, but is a viable measure for the conventional centrifugal force-regulated transmission adjustment.

Suitable measures are provided for the support element 4 and the second tapered washer 21 for circumventing the second tapered washer 21 at the same rotational speed.

As shown in Figure 1, the measures of the present invention can be combined with such conventional centrifugal force adjustments, i.e., preferably only such measures can be employed.

The centrifugal force element is generally or defined as one or several spaces having one or several spheres or rollers that are further driven from the rotating shaft by the centrifugal force perpendicular to the rotating shaft when rotating. The second tapered spacer 21 is moved.

An outer sleeve 54 is formed by means of the inner sleeve 53 in a translationally coupled and rotationally decoupled manner, wherein the radial bearing 55 is rotationally decoupled. The movement of the outer sleeve 54 is transmitted to the corresponding movement of the inner sleeve by such measures, but wherein the inner and outer sleeves 53 and 54 are rotatable relative to each other.

The outer sleeve 54 has a housing sleeve 54a, a first housing end face 54b disposed on the outer sleeve 54a away from the inner sleeve 53, and a second housing end surface 54c facing the inner sleeve 53 and having a radial bearing 55 formed thereon .

The inner sleeve 53 and the outer sleeve 54 are rotationally symmetrical about the axis of rotation X of the pair of tapered washers 2, wherein the outer sleeve 54 and in particular its outer sleeve 54a at least partially surrounds the inner sleeve 53 concentrically or coaxially.

A spindle nut 8 is formed on the first housing end face 54b or in the first housing end face, the spindle nut having a central bore 8a and an internal thread 8b to which the threaded spindle 7 can be engaged by its external thread 7b. The outer sleeve 54 and the spindle nut 8 can be provided as separate components, in particular in that the nut 8 is embedded in the material of the outer sleeve 54. An integral embodiment can also be used, in particular by, for example, a bore 8a having an internal thread 8b is easily constructed in the first end face 54b.

The spindle journal 7c or the journal 7c on the spindle 7 and its end 7a can also be constructed as a separate component or in a material-integrated construction.

According to the embodiment shown in Fig. 1, the spindle nut 8, the bore 8a, the threaded spindle 7 and its end 7a are coaxial with each other and coaxially with respect to the axis of rotation X as an axis of symmetry.

The threaded spindle 7 has a thread 7b on the outer peripheral surface, at least outside the thread, having an end 7a of the bearing journal 7c of the threaded spindle.

The thread 7b of the threaded spindle 7 is arranged to mesh with the spindle nut 8 of the outer sleeve 54, such that the spindle 7 is rotated as a translationally fixed element to drive the torsion-resistant spindle nut 8 and the outer sleeve 54, in particular along the axis of rotation X A panning occurs.

Control can be performed by the control unit 6 via the first and second measurement lines and/or control lines 6-1 and 6-2, wherein the second control line 6-2 acts on the adjustment device 5 and the actuator 50. The actuator 50 drives the adjustment transmission 52 through the drive shaft 51 and the threaded spindle 7 engaged with the adjustment transmission to rotate, and then transmits the threaded spindle 7b of the threaded spindle 7 and the torsion-resistant spindle nut 8 through the translational direction. The threaded spindle is translated and rotated coaxially here Axis X translation. In this way, for example, between the position A or A' and B or B', the spindle nut 8 and the outer sleeve and the inner sleeves 54 and 53 coupled thereto in translation can be moved along the axis of rotation X in order to change the tapered gasket. The distance D between 20 and 21, in turn, changes the transmission of the belt 12 for the pair of tapered washers 2.

An important aspect of the present invention is that the position of the second axially movable tapered washer 21 relative to the first axially fixed tapered washer 20 is coupled to the inner sleeve 53 and the outer sleeve 54 and to the translation. Active and (as appropriate) centrifugal force independent adjustability achieved by the movable and torsionally resistant spindle nut 8 and the first axially movable tapered washer and the first axial position of the tapered washer pair 2 A controllable change in the distance of the tapered gasket 20, in particular by the user, such as the driver of the vehicle, is actively controlled by the control unit 6.

The conventional control device of the CVT transmission is composed, for example, of a centrifugal force regulator on the primary side and a compression spring having a torque ramp on the secondary side.

According to the invention, by the combination of the actuator, that is, the inner sleeve 53, the outer sleeve 54, the threaded spindle 7 and the spindle nut 8 operated by the actuator 50, an additional force can be applied to change the CVT transmission, and This is done independently of the motor speed and the pressing force on the secondary side.

Therefore, another advantage of the present invention is that the pressing force on the secondary side can be reduced. Thereby, the only criterion associated with the spring and the torque ramp is the embodiment in the macroscopic sliding sense of the sliding operation of the CVT transmission.

As described above, it is not necessary to perform centrifugal force adjustment by the centrifugal force element 3 supported on the support member or the support plate 4. If the centrifugal force adjustment is present, it can be understood that the inner sleeve 53 of the sliding bushing can be pressed, blocked or the like by the three fingers and the movable pulley 21, for example. Connected or connected in a similar manner. The slide bushing 53 slides on the clamp sleeve 41 together with the fixed movable sheave 21. The fixed pulley 20, the clamp sleeve 41 and the support plate 4 are fixedly coupled to the crankshaft 11 via a kickback starter nut 66.

The kickback starter nut 66 can also accommodate a fixed bearing of the spindle system.

Another task of the kickback starter nut 66 is to introduce the rotary motion of the kickback starter drive 62 from the recoil starter 60 into the crankshaft 11 to cause a starterless and in particular manual start of the motor.

One or several, in particular three, fingers of the inner sleeve or sliding bushing 53 extend through the grooves in the fixed pulley 20. In particular, as shown in FIG. 5, the flange ring 68 is pressed against the stop ring by a retaining nut and the flange ring is connected to the sliding bushing 53 in such a fixed manner.

The electric gear motor acts as an actuator 50 to cause a rotational movement of the spindle system. This rotational motion is converted into a translational motion or introduced into the outer sleeve 54 or bell through the spindle system/spindle nut system in the transmission 52.

The other spindle end 7a extends into the outer sleeve 54 or the interior 54i of the bell, in particular by a journal or spindle journal 7c constructed on the end.

The adjustment movement is introduced into the inner sleeve 53 or the sliding bush through the bearing 55 in the outer sleeve 54 for decoupling and linear motion, in particular through the radial bearing, and is transmitted to the movable pulley 21.

The distance D between the two pulleys 21 and 21 changes, so that the belt 12 running between the pulleys 20, 21 must run at the respective diameters given by the pulleys 20 and 21 and their distance D.

The gear drive mechanism 62 of the kickback starter 60 is engaged through a recess 57 in the outer sleeve 54. The recoil starter double gear 67 is directly supported on the main shaft 7 or its end 7a. On the journal 7c. The rotation of the kickback starter transmission mechanism 62 is transmitted through the transmission gear 64 to the recoil starter double gear 67. The helical teeth move the recoil starter dual gear 67 until its crown or spur gear meshes with the crown gear of the kickback starter nut 66.

If the internal combustion engine 10 is automatically operated, the first recoil starter gear 67 is slightly braked by the brake spring 65. The tooth profile of the crown gear and the reverse rotation of the recoil starter drive mechanism move the recoil starter dual gear 67 back to the initial position, i.e., without engaging the kickback starter nut 66.

The particular geometry of the outer sleeve 54 of the type of bell and the complementary or corresponding shape of the housing 14 prevent undesired rotation by rubbing in the bearings. This in particular prevents the bell grooves 57, 58 from colliding with the teeth of the recoil starter drive gear 64. Moreover, the shape causes a correct mounting of the position between the bell and the housing.

2 is a partial cross-sectional side elevational view of another embodiment of a CVT transmission 1 of the present invention.

As a complement to the element shown in Fig. 1, Fig. 2 shows on the one hand more clearly that the threaded spindle 7 with the external thread 7b engages the bore 8a and the internal thread 8b of the spindle nut 8, and the display has a spindle journal 7c or The construction of the end 7c of the journal 7c.

In addition, as shown in FIG. 2, the housing sleeve 54a of the outer sleeve 54 has a first through hole 57, which may also be understood as a first window or first recess and for the kickback starting mechanism 60. Engaged in an outer sleeve 54 constructed as a hollow body for accessing the second recoil starter gear 66 by, for example, a first recoil starter gear 67 constructed as a dual gear - here based on a recoil start The type of nut is in turn engaged with the second recoil starter teeth.

The first recoil starter gear 67 is supported as a double gear on the spindle journal 7c On the outer peripheral surface. The first recoil starter gear 67 is engageable with the recoil starter nut as the second recoil starter gear 66 by axial movement along the axis of rotation X for initiation upon actuation of the recoil starter 60 Recoil start process.

In addition, the housing sleeve 54a of the outer sleeve 54 has a second window, which can be understood as a second through hole or a second recess through which the brake spring 65 for the kickback starting device 60 passes. The two windows enter the interior 54i of the outer sleeve 54.

2 also shows that the housing sleeve 54a has a first region 54-1 including a larger diameter d1 and a second region 54-2 including a smaller diameter d2, wherein a radial bearing is constructed in the first region 54-1 55. A spindle nut 8 is constructed in the second region 54-2.

Figure 3 is an embodiment of Figure 2 having the same position of the first and second tapered spacers 20 and 21 with respect to their axial distances, wherein Figure 3 is shown in a complementary manner between the tapered spacers 20 and 21 Containment member 12.

The sequence of Figures 4 through 8 shows in detail a detailed view of the outer sleeve 54 in accordance with an embodiment of the present invention, a partial perspective view, wherein Figure 7 is a side cross-sectional view.

The outer sleeve 54 of this embodiment has a housing sleeve 54a that includes a first region or section 54-1 of larger diameter d1 and a second region or section 54-2 of smaller diameter d2.

The second housing section 54-2 includes a first housing end face 54b that substantially encloses the opening of the housing sleeve 54a. The journal 7c of the threaded spindle 7 aligned with the inner portion 54i of the outer sleeve 54 extends through the first housing end face 54b. In this case, the threaded spindle 7 itself is engaged to the internal thread 8b of the spindle nut through the bore 8a in the spindle nut 8.

To couple with the kickback starter mechanism 60, the housing sleeve 54a has a first window 57 as a first through hole. Further, a second through hole 58 for accommodating the brake spring 65 is provided.

In Fig. 4, the threaded spindle 7 has not been fitted with the journal 7c on the end 7a.

In Figures 5 to 8, the threaded spindle 7 having the journal 7c and the thread 7b on the end 7a has passed through the bore 8a of the spindle nut 8.

Figures 6 to 8 show additional components of the recoil starter 60. The recoil starter transmission 62 has a first recoil starter gear 67 of the type according to a dual gear, the first recoil starter gear being externally driven by a recoil starter of the recoil starter 60 The drive gear 64 of the device 62 is combed and driven. The double gear 67 is supported on the journal 7c on the end 7a of the threaded spindle 7.

9 through 11 are perspective views depicting the socket 14b of the transmission housing 14 and the transmission housing 14 for receiving the outer sleeve 54.

The outer sleeve 54 has a configuration on its first housing end face 54b, in particular in cross section, which is complementary to the form of the socket 14b of the transmission housing 14. Specifically, in addition to the bore 8a for the spindle nut 8, the first housing end surface 54b has a recess 54d on the outer peripheral surface, and the outer peripheral surface of the first housing end surface 54b is no longer rotationally symmetrical by the recess That is, it deviates from the strict circular shape in the cross section.

For the torque support 9, the socket 14b in the housing 14 has a corresponding projection 14c on its inner peripheral surface, which can also be understood as a flange or a shoulder, so as shown in Fig. 11, at the socket When the 14b and the first housing end surface 54b are inserted into each other, the torsion retention and the correct positioning of the outer sleeve 54 on the transmission housing 14 are achieved, in particular, that is, the shape fit is generated through the recess 54d and the protrusion 14c. . After installation, the threaded spindle 7 is engaged with the transmission mechanism in the transmission housing 14 through the through hole 14d.

2‧‧‧Conical gasket pair

3‧‧‧ centrifugal force components

4‧‧‧Support elements/support plates

5‧‧‧Adjustment device

6‧‧‧Control unit

6-1‧‧‧Measurement line/control line

6-2‧‧‧Measurement line/control line

7‧‧‧Threaded spindle/spindle

7a‧‧‧End/spindle end/distal

7b‧‧‧External thread/thread

8‧‧‧Spindle nut/nut

8a‧‧‧Drilling

8b‧‧‧ internal thread

10‧‧‧ Internal combustion engine/motor

11‧‧‧ crankshaft

12‧‧‧Inclusive components/drive belts

13‧‧‧Drive member/second tapered washer pair

20‧‧‧Conical gasket/pulley

21‧‧‧Conical gasket/pulley

41‧‧‧Clamping sleeve

50‧‧‧Executive agency

51‧‧‧Drive shaft

52‧‧‧Adjustment of transmission / transmission

53‧‧‧Inner sleeve/sliding bushing

54‧‧‧Outer sleeve

54a‧‧‧Sheath cover/coat

54b‧‧‧Shell end/end face

54c‧‧‧shell end face

54i‧‧‧Internal

55‧‧‧ Radial Bearings/Bearings

A‧‧‧ position

A'‧‧‧ position

B‧‧‧ position

B'‧‧‧ position

D‧‧‧Distance

X‧‧‧Axis/Rotary axis

Claims (12)

A CVT transmission comprising: a tapered gasket (20) having an axially fixed tapered gasket (20) and an axially movable tapered gasket (21), and the axially movable cone The gasket (21) is coupled to the axially movable inner sleeve (53) in a rotationally and translationally coupled manner, and an axially movable outer sleeve (54), the outer sleeve and the inner sleeve (53) a coaxial arrangement, translationally coupled to the inner sleeve and rotationally decoupled from the inner sleeve, wherein the outer sleeve (54) has a spindle nut (8) constructed to be torsionally rigid, the spindle nut being arranged for use A rotatable and translationally fixed threaded spindle (7) that adjusts the axial position of the axially movable conical spacer (21) engages and cooperates to flexibly and translatably engage the outer sleeve (54) ) Coupling. The CVT transmission of claim 1, wherein the outer sleeve (54) is substantially rotationally symmetric with a rotational axis (XX) of the tapered washer pair (2), and wherein the spindle nut (8) is disposed On the axis of rotation (XX). A CVT transmission according to any one of the preceding claims, wherein the outer sleeve (54) has a housing sleeve (54a) and at least a first housing end face (54b), and wherein the spindle nut (8) In particular, the material is integrally formed on the first housing end face (54b). The CVT transmission device of claim 3, wherein the housing sleeve (54a) has at least one through hole (57, 58), And wherein the at least one through hole (57, 58) is arranged to accommodate at least one component of the recoil starter (60) and particularly a recoil starter transmission after the CVT transmission (1) is installed (62) The dual gear (67) is movably and rotatably supported and/or retained on the threaded spindle (7). A CVT transmission according to claim 4, wherein a journal (7c) is formed on the distal end (7a) of the threaded spindle (7), the journal being arranged to be movable and rotatably supported and/or retained At least one component (67) of the recoil starter (60). The CVT transmission of any one of claims 3 to 5, wherein the casing sleeve (54a) has a first region (54-1) including a larger diameter (d1) and a smaller diameter (d2) a bell shape of the second region (54-2), wherein in particular the first region (54-1) faces the inner sleeve (53) and is arranged to couple with the inner sleeve and/or the second region has A first housing end face (54b) of the spindle nut (8) is included. A CVT transmission according to any one of the preceding claims, having an adjustment device (5) for adjusting the axial position of the axially movable conical gasket (21), wherein the adjustment device (5) transmits a threaded spindle (7) and the spindle nut (8) are coupled to the outer sleeve (54), wherein the adjustment device (5) has an adjustment transmission (52) for rotating the threaded spindle (7), and wherein The adjusting device (5) has an actuator (50) and is arranged such that, in operation, the actuator (50) is actuated by a combination of the adjusting gear (52), the threaded spindle (7) and the spindle nut (8) The rotation in the middle is converted into the rotation of the thread spindle (7) And the axial movement of the translation of the spindle nut (8) and the axially movable tapered washer (21). A CVT transmission according to any of the preceding claims, having a torque arm (9) arranged to support and hold the outer sleeve (54) in a rotationally fixed manner. A CVT transmission according to claim 8 includes a transmission housing (14) having a socket (14), wherein the outer sleeve (54) is received in the transmission housing with its housing end surface (54b) In the socket (14b) of the body (14), and wherein the shape of the first housing end face (54b) and the socket (14b) are not rotationally symmetric and at least segmentally complementary to each other, thereby transmitting the first housing end face The torque arm (9) is realized by (54b) engaging the sockets (14b) of the transmission housing (14) along the circumferential direction of the socket. A CVT transmission according to any one of claims 7 to 9 having a control unit (6) arranged to operate the adjustment device (5) for the pair of tapered spacers (2) Achieve drive changes. A CVT transmission according to any one of the preceding claims, comprising: at least one centrifugal force element (3) movably disposed on the axially movable conical gasket (21), and a shaft disposed on the shaft a support member (4) coupled to the movable tapered washer (21) and to the drive shaft or crankshaft (11), wherein the centrifugal force member (3) is disposed between the support member (4) and the axially movable cone Between the back walls (22) of the gasket (21). A vehicle comprising a CVT-transmission (1) according to any one of the preceding claims, wherein the vehicle (100) refers in particular to a small vehicle, in particular a two-wheeled or tricycle or a snowmobile or a Quad or the like.