Bicycle hub with internal gear

 

(57) Abstract:

The invention relates to a planetary gear, integrated into the hub of a bike wheel. In Cycling the sleeve (10) in the process of shifting towards higher transmission power is transmitted from the driving element (22) on the holder (43) through the second one-way clutch (51) without coupling (45) clutch. In the process of shifting towards low gear switch (49) mounted to rotate on an axis (21) of the sleeve abuts against the Cam surface (47) of the clutch (45) clutch. When this is passed to the clutch (45) clutch drive torque force is converted into an auxiliary force in the axial direction of the clutch (45) clutch for shifting clutch (45) clutch even if you have a large resistance to disable the first one-way clutch (50) or clutch (45) clutch. The proposed solution provides ease of gear even when the transmission of drive force during the movement. 18 C.p. f-crystals, 10 ill.

The invention relates to a Bicycle hub, and in particular to the sleeve with an internal gear, which can be mounted on the Bicycle frame for transmitting power from ugodnog the/P> Bikes, and especially exercise bikes, which is also called the city, inexpensive and easy to operate and are widely used for trips to work, school, shopping. In the rental of this type on the rear wheel sometimes mounted Bicycle hub with an internal gear in order to drive at high speed on level ground or walking up the slope with a minimum of effort.

Bicycle hub with an internal gear usually includes fixed on the Bicycle frame, the axis of the sleeve, the outer casing, which can rotate around the axis of the sleeve, a planetary gear mechanism (planetary gear) inside the hub shell, a switching mechanism for selecting one of the multiple paths of power transmission with the included planetary mechanism, and the crank lever to move the clutch (see, for example, the patent of the Russian Federation 2019467, publ. 15.04.94, IPC 62 11/16). This design is the most loved and adopted as a prototype. The switching mechanism includes a clutch for switching paths of power transmission by moving in the axial direction and the push rod that pushes the clutch. For Uruchom switch, mounted on the steering wheel.

In this cycle the sleeve with the internal gear actuation of the lever causes the winding and tension of the inner cable pull rope control, what is the impact of the cranked lever on the push rod, the displacement of the clutch in one axial direction and the gear change from a higher to a lower speed level. However, when the inner cable is weakened, the clutch may not be shifted to the other side only one push rod. Accordingly, use bias force of the return spring or etc., for shifting the clutch in the other axial direction and switch gear, for example, from a lower to a higher level of speed.

In the above-described known Bicycle hub with an internal gear in motion when the Bicycle is driven by the pedals with the application, a large drive force, between the clutch and the parts forming the planetary gear, a large resistance. In particular, when the applied driving force increases the frictional force in the interacting parts of the coupling, the coupling is of Ceplene.

To prevent this, the clutch must be advanced with sufficient force to overcome the friction force, when the inner cable is pulled and the clutch is pushed by the pushing rod, and this means that when the winding wire control requires a higher force. The elastic force of the return spring must also be large enough to overcome the friction force, when the control cable is weakened, and the clutch is shifted back by the recoil. However, if you increase the force of the return spring, the push rod will need to transfer the force greater than the force of the return spring, so that greater effort will be needed when the winding of the inner cable lever.

Therefore, the need to increase the force on the lever in order to ensure the gear regardless of the direction switch in position when in motion is transmitted driving force. For this reason, with respect to the sleeve with the internal gear hard to shift gears with a small operating force when operating the pedals when transmitted driving force.

Task is the making and with a light operating force in the sleeve, even when a driving force is applied during the movement.

Bicycle hub with an internal gear in accordance with the invention is a sleeve which can be mounted on the Bicycle frame and in which the power from the input element is transmitted to the output element with a certain selected gear ratio; this sleeve includes an axle sleeve, the leading element, a tubular driven element, a planetary gear, a first one-way clutch, the second and third one-way clutch, the tubular clutch and the control switch. The axis of the sleeve may be fixed on the frame. The leading element is mounted for rotation around the axis of the sleeve and is connected with the input element. A driven element is designed with an internal cavity, is mounted for rotation around the axis of the sleeve and is connected with the output element. The planetary mechanism is placed in the inner cavity of the slave element that transmits power from a driving element to a driven and has a Central gear made integral with the axis of the sleeve coaxially her satellite, which is engaged with the Central gear, drove on which you installed the satellite with the possibility of rotation and to the which is installed rotatably around the axis of the sleeve and meshing with the satellite on its outer side. The first one-way clutch is located between the cage and the rolling element can transmit power in one direction only and can be switched between a state of power transmission and disconnection of the transmission power in the state under the load transmitted power. The second and third one-way clutches are arranged respectively between the leading element and the holder and between the planet carrier and the slave element and transmits power in one direction only. The clutch is installed on the axis of the sleeve for rotation and displacement in the axial direction, and switches through its movement in the axial direction of the lead element and drove between the clutch position and a position of disengagement, and switches the first one-way clutch between the States of the power transmission and disconnection of the power transmission. The control switch moves the clutch in the axial direction and communicates with the clutch with torque conversion drive force of the clutch in its movement in the axial direction.

In this sleeve with the internal gear during the rotation of the input element in one direction and installing clutch with T drove and translates the first one-way clutch is in a break state power transmission, rotation is served on the holder via the drive element and the second one-way clutch and removed from drove through the planetary gear with the speed decrease by an amount determined by the ratio (number of teeth of the clip) : (number of teeth of the Central gear + the number of teeth of the clip). This rotation with decreasing passed through a third one-way clutch from the carrier to the driven element and the output element rotates in the same direction at a reduced speed.

During the rotation of the input element in one direction and installing clutch with control switch in the position of direct transmission, in which she shares the leading element and drove and translates the first one-way clutch is in a state of power transmission, the rotation is transmitted to the yoke via the drive element and the second one-way clutch, and the rotation from the driving element is transmitted to a driven element through the first one-way clutch, and the output element rotates at the same speed in the same direction.

During the rotation of the input element in one direction and installing clutch with control switch in the position of high transmission, where she provides direct with the tion is transmitted to the carrier via the drive element and the clutch and removed from the cage through the planetary mechanism with increasing speed by an amount determined by the ratio (number of teeth of the Central gear + the number of teeth of the clip) : (number of teeth of the clip). This rotation with increasing transferred through the first one-way clutch from the carrier to the driven element and the output element rotates in the same direction with higher speed.

Thus, when the clutch is moved from a position low position high pass through the position of the direct transmission, even if the rotation is fed to the clutch, it will just free to rotate without transmitting torque effort, so to move the clutch in this direction requires very little effort. In the opposite case, when the clutch is moved from a position of increased transmission in the position of direct transmission, a friction clutch between the clutch and planet carrier makes it more difficult to disconnect the clutch from the carrier, and when the clutch is shifted from the position of direct transmission in a low gear position, is transmitted torque drive force through the first one-way clutch, which connects the led to the housing sleeve, which makes it difficult gap power transmission. However, when the interaction element controls the axial direction, creates an auxiliary force, and rotating drive force of the bike uses a clutch to facilitate its movement in the axial direction. Accordingly, it requires less force to move the clutch from a position of increased transmission in a low gear position. Thus, the shifting may be performed in any direction with little effort control even when the transmission of drive force during the movement.

In accordance with a second implementation of the invention in a Bicycle hub with an internal gear, as described in the first execution, the control switching is made in the form attached to the axis of the sleeve guide surface, switch to move the clutch in the axial direction by means of its movement along the guide surface, and a pushing element for pressure switch and clutch installed with the possibility of the shock of contact with the switch and is supplied located obliquely to the axis of the sleeve Cam surface for converting the rotating drive force to move in the axial direction while rotating in one direction at impact contact the surface of the clutch due to its rotation in one direction it follows the Cam surface, and the rotating drive force is converted into the movement of the clutch in the axial direction. Accordingly, with a simple construction is achieved by converting the rotating drive force to move in the axial direction.

In accordance with a third implementation of the invention in a Bicycle hub with an internal gear, as described in the second execution, the axis of the sleeve provided with a slot made through the axis of the sleeve and spiral twisted in the opposite direction relative to the first direction, and a guide surface formed by a part of the surface through the slits inclined at a certain angle to the axis of the sleeve.

In this case, since the guide surface through the slots has a slope relative to the axis and is twisted in a spiral in a direction opposite the first direction when the clutch rotates in the first direction, and the switch should be up on the Cam surface, he pressed a Cam surface to guide surface along the entire length of his contact with the latter, and go to the OS is a great effort in the axial direction rather will move the switch and not the clutch, so that in this position, when the driving force is too large, the gear shift will not happen, and this reduces the shock load when shifting and prevents damage to the parts of the power transmission mechanism due to the increased drive force.

In accordance with the fourth version of the invention in a Bicycle hub with an internal gear, as described in the third version, the slot with the guide surface inclined to the axis of the sleeve at an angle lying in the range from 10 to 50o. If the angle is less than 10othe switch will have a tendency to retreat in the axial direction when pressure is applied to the Cam surface. However, if the angle is greater than 50owhen the transfer pressure switch pusher element resistance will be high and will require a higher force control for gear shifting.

In accordance with the fifth version of the invention in a Bicycle hub with an internal gear, as described in the third or fourth version, the angle of inclination of the Cam surface of the clutch otnositelnoy Cam surface more than the angle of the slots, the angle of the guide surface, which moves the switch is less than the angle of inclination of the Cam surface at impact contact of the switch with the clutch, so that the switch can move back from the Cam surface. If the angle is smaller than 20othen the slope is too steep, and the rotating drive force cannot be effectively converted into movement in the axial direction, but if the angle exceeds 70othen the slope is too gentle, and will not be achieved sufficiently offset in the axial direction, and even if the rotating drive force is converted into a displacement in the axial direction, the clutch will be difficult to separate from the carrier, and therefore, it will be difficult to translate the first one-way clutch from the state of power transmission in the break state power transmission.

In accordance with the sixth version of the invention in a Bicycle hub with an internal gear, as described in the fourth or fifth version, the switch is made with a triangular cross-section and is located in the through slits in such a way that its longitudinal direction is perpendicular to the axis of the sleeve. In this lucrezi, and this movement may be limited frictional forces. In particular, when the Cam surface comes into impact contact with one of the triangular surfaces of the switch and presses it, the other surface is in contact with the guide surface, and the frictional forces impede the movement of the switch in the axial direction. During the displacement of the switch under the action of the pusher element, only one surface is in contact, and the other free, and this reduces the resistance during the movement.

In accordance with the seventh version of the invention, a Bicycle hub with an internal gear, as described in any of the performances from second to sixth, equipped with the first shifting element (a first coil spring to bias (clamp) clutch toward the carrier, the second shifting element (a second coil spring) to offset (down) switch in the direction of the clutch and the third shifting element (a third helical spring), located between the switch and the clutch and intended for the extraction of these two elements in opposite directions by means of the elastic force to the shock of contact, the switch is ripped in the side drove the first shifting element, when the clutch is put in engagement with the planet carrier during its movement in the direction of increased transmission, even if they are not in the position kinematic link, they can easily engage with the rotation of the clutch. Further, since the switch is pressed in the direction of coupling the second shifting element, a clutch can be reliably shifted towards low gear when she moves in her direction. In addition, since the switch and clutch presses from each other, the third shifting element, even if the switch is set against the Cam surface during the switch to a lower gear, the switch and the Cam surface are separated from each other when the clutch is separated from the carrier. Accordingly, the Cam surface will not hit the switch in the process of moving, and the noise will not occur.

In accordance with the eighth version of the invention in a Bicycle hub with an internal gear, as described in the seventh implementation, the third shifting element is designed in the form of helical springs, limited to a certain total length. In this case, can be adjusted by the offset resistance of the branch is small, the gap between the switch and the clutch will be equal to the fixed length of this bias element, so that the clutch will be positioned more accurately.

In accordance with the ninth version of the invention in a Bicycle hub with an internal gear, as described in the seventh or eighth version, the pushing element transmits to the pressure switch, pressing him to the cage. In this case, when the switch is not under pressure, the clutch is in the low gear position, and when he transferred to the pressure, it is shifted from the position of a direct transfer to a position of increased transmission.

In accordance with the tenth version of the invention in a Bicycle hub with an internal gear, as described in the ninth version, this pushing element is designed in the form of a rod-like element, and the bias pressure of the efforts of the three shifting elements are such that the second bias element is made of the strongest, the third shifting element is weaker, and the first bias element is the weakest. In this case, when the pushing element recedes in a direction opposite to the direction of its efforts to push, bias clamping stress is to be shifted to the second bias element. Further, since the bias force of the third shifting element is greater than the force of the first bias element, the switch does not so easily give shock hard on the clutch, when he presses the clamping element, so that the clutch is moved in the direction of increased transmission of the first bias element.

In accordance with the eleventh version of the invention in a Bicycle hub with an internal gear, as described in the ninth version, the pushing element is designed as a control, representing a rod of a certain length, element, having the possibility of relative movement in the axial direction on the remote end of the control element, and a bias element, located between the control and actuating elements with the possibility of spin in opposite directions, and the switch is capable of transmitting pressure to the clutch in both axial directions, the bias element is a first bias element, and shifting effort is installed such the first bias element is made of the strongest, the second bias element is weaker, and the third enta more force of the second bias element, the switch can be moved to the clamping element in the direction of increased transmission against the action of the second shifting element, so that the clutch moves from low towards high gear. As a result, the switch transmits the pressure to the clutch and it shifts to high gear. When the pushing element recedes in the opposite pushing force direction bias force of the second bias element more efforts of the third shifting element, so that the clutch may be shifted to the second bias element.

Further, since the first bias element that has the greatest effort, is inserted in the clamping element, the number of coils can be increased, and the spring stiffness will be reduced. As a result, the rigidity of other bias elements may also be reduced, which enables to reduce the force control in the overall process of shifting. In addition, since the bias clamping force of the second bias element more efforts of the third shifting element, the switch securely transmits the pushing force of the clutch at the time when the required supporting force at the time per execution of the invention in a Bicycle hub with an internal gear, as described in the seventh or eighth version, the pushing element transmits to the pressure switch, pressing it to the clutch. In this case, when the switch is not under pressure, the clutch is in a position of increased transmission, and when he transferred to the pressure, it moves from the position of direct transmission in a low gear position.

In accordance with the thirteenth execution of the invention in a Bicycle hub with an internal gear, as described in the twelfth version, the pushing element is designed as a control, representing a rod of a certain length, element, having the possibility of relative movement in the axial direction on the remote end of the control element, and a bias element, located between the control and actuating elements with the possibility of spin in opposite directions, and the switch is capable of transmitting pressure to the clutch in both axial directions, the bias element is a second bias element, and shifting effort is installed such the second bias element is made of the strongest, the third CME force of the second bias element more force of the first bias element, the switch can be moved to the clamping element in the direction of climbing gear against the action of the second shifting element, so that the clutch moves from high transmission in the direction of low transmission. As a result, the switch transmits the pressure to the clutch and it shifts to low gear. In addition, since the bias force of the second bias element more efforts of the third shifting element, the switch securely transmits the pushing force of the clutch at the time when the required supporting force while moving in the direction of low transmission. When the pushing element recedes in the opposite pushing force direction, and the clutch operates bias force of the first bias element, the bias force of the third shifting element more force of the first bias element, so that the clutch may be shifted in the direction of increased transmission in position, when the clutch and the switch removed from each other, the third shifting element.

Hereinafter the invention will be described in detail with reference to the drawings, which depict:

in Fig.1 is a side view of a Bicycle with vtalk cross-section;

in Fig. 3 is shown with magnification view of the sleeve with the internal gear in the position to include climbing gear;

in Fig.4 is a perspective view of the drive mechanism;

in Fig. 5 is a schematic depiction of the relative position of the switch and the Cam surface;

in Fig.6 is a longitudinal cross-section of the push rod;

in Fig.7 is a view corresponding to Fig.3 and representing a sleeve with an internal shift in the position of direct transmission;

in Fig.8 is a view corresponding to Fig.3 and representing a sleeve with an internal gear in positions of increased transmission;

in Fig.9 is a view corresponding to Fig.3 and represents the second exemplary embodiment;

in Fig.10 is a view corresponding to Fig, 3, and represents the third PR iMER run.

Information confirming the possibility of carrying out the invention

The first example of execution

General layout of

The bike, which applied the invention shown in Fig.1 in the form of an exercise Bicycle that includes a frame 1 comprising a frame 2 of the two elements and the front fork 3, a steering unit 4, the drive unit 5, a front wheel 6, a rear wheel 7 on which is mounted three-speed sleeve 10 in which each for convenient hand-held remote control bushing with an internal switch.

On the frame 1 are mounted the various components, including the seat 11, the steering node 4, the front wheel 6 and the rear wheel 7.

The steering unit 4 has a rack 14, mounted in the upper part of the front fork 3, and the steering cross member 15 fixed to the rack 14. The brake lever 16, which is part of the front brake device 8, the handle 17 and the device 9 of the shift control mounted on the right end of the steering cross member 15. The device 9, the control gear is mounted on the brake lever 16 from its inner side and is connected with the sleeve 10 with an internal switch with cable 73 control switch, consisting of the inner cable and the outer shell. The device 9 of the shift control has the usual construction, comprising a lever winder for winding the inner cable and release lever, which releases the wound made by winding lever, and releases the inner wire; the device as such is not described in detail here.

The drive unit 5 includes a gear lever (asterisk) 18 with pedals installed in the lower part (lower bracket) frame 2 frame, the chain 19, which encircles the sprocket with pedals, and the sleeve 10 with the inner PE with an internal gear is provided with a brake inertial movement of the sleeve with a three-stage transmission, including paths of power transmission to low gear, direct drive and high transmission. As shown in Fig.2, the sleeve 10 with the internal gear has an axle sleeve 21 fixed on the back of the dog 2A of the frame 2 of the Bicycle frame, the lead element 22 covering the outer surface of one end of the axis 21 of the sleeve body 23 of the sleeve covering the outer surface of the axis 21 of the sleeve and the leading element 22, the planetary gear mechanism (planetary gear) 24, the drive mechanism 25 to select the path of power transmission, the crank lever 26 for actuation of the drive mechanism 25, and the brake 27 inertial motion.

As shown in Fig.2 and 3, the axis 21 of the sleeve is an element in the form of a round rod having a larger diameter in the middle part and two ends of the smaller diameter coated with the thread. In the axis 21 of the sleeve internal axial channel 21A, which runs from its right end to the middle, as shown in Fig.2. A through slot 21b, which passes through the axis of the sleeve 21, is made near the high end of the inner working channel 21A. A through slot L passes through the axis 21 of the sleeve inclined at a certain angle to its axis (see Fig.5) and in aleve in Fig.5. This end-to-end slot 21b is accomplished by the use of certain diameter drill to drill through the axle holes, and then drill serves to center in the axial direction, at the same time slowly turning axis 21 of the sleeve in the forward direction of rotation. The result is a through slot 21b has the form of a continuous spiral, in which overlapping at both ends of the through hole is gradually rotated as the offset in the axial direction. The angle of the slits must lie in the range from 10 to 50o.

One end of a driving rotary element 22 is mounted on a shaft sleeve 21 by means of the balls 30 and the inner cone 31 of the bushing and the sprocket sleeve 32 mounted on one end of a driving element. At the other end of the lead element 22 on its inner surface made many passes in the axial direction of the internal sawtooth teeth 22A.

The housing 23 of the sleeve is made in the form of a tubular element, and in its internal cavity 23a posted by leading element 22 and the planetary mechanism 24. The housing sleeve 23 is mounted for rotation around the axis 21 of the sleeve supported on the balls 33 and 34 and the inner cone 35. The flanges 36 and 37 for fastening spokes 7a (see Fig.1) mounted near both to the output mechanism 24 includes a Central gear 40, which is made integral with the axis 21 of the sleeve coaxially her, drove 41, mounted on the axis of the sleeve 21, the three satellites 42 (only one shown in the drawing) included in mesh with the Central gear 40, and the holder 43.

Led 41 is a tubular member and installed on the axis of the sleeve 21 for rotation. In a drive rod 41 is made of three slots 41A located on the circumference and on the fingers 44 mounted for rotation satellites 42. At one end of the carrier 41 on its inner surface an internal sawtooth teeth 41b, and at the other end on the outer surface of the completed exterior of the sawtooth teeth 41p (see Fig.1).

The yoke 43 has a shape close to cylindrical and hosted from satellites 42 to the outer surface of the leading element 22. Internal teeth 43b is made on the inner surface of the casing at its end remote from the driving element 22. Satellites 42 engages with the Central gear 40, as already mentioned, as well as with internal teeth 43b clip 43.

At one end of the holder 43 is made socket 43A, and in this slot 43A on the finger 54 is installed to rotate the pawl 53 which forms part of the first one-way multistorey clutch 50 transmits a driving force of rotation from the carrier of the planetary mechanism 24 on the housing 23 of the sleeve only when the forward direction of rotation. The dog 53 is engaged with the teeth 23b ratchet located on the inner surface of the housing 23 of the sleeve only when the holder of the planetary gear 24 rotates in the forward direction. Even in the position of the transfer drive force, wherein the yoke planetary gear 24 rotates in the forward direction, the first one-way clutch 50 can be switched out of the circuit of the transmission, in which the dog 53 is entered in the teeth 23b of the ratchet, in the trip position of the transmission diverting from the teeth 23b ratchet by shifting the clutch, as will be described later.

The second one-way clutch 51, which transmits a driving force of rotation from the driving element 22 on the holder of the planetary gear 24 only in the front direction of rotation is established between the leading element 22 and the holder of the planetary mechanism 24. The third one-way clutch 52, which transmits the driving force of rotation from the carrier 41 on the housing 23 of the sleeve only in the forward direction of rotation, is located between the planet carrier 41 and the housing 23 of the sleeve. The third one-way clutch 52 has a tubular covering the housing 56 with an internal sawtooth teeth 56a located on the inner surface with the od of the carrier 41, and covers the body 56 of the clutch rotates with the planet carrier 41 as a whole. These two one-way clutches 51 and 52, in contrast to the first one-way clutch 50, can't switch to the position circuit transmission (transmission of drive force).

The design of the drive mechanism

The drive mechanism 25 is used to select a path of power transmission and includes the clutch 45 and clutch element 46 of the control switch.

The clutch 45 clutch switch lead element 22 and drove 41 between a position of mutual engagement and disengagement, and switches the first one-way clutch 50 between the positions of power transmission and disconnection of the transmission path capacity. The coupling 45 of the clutch installed on the outer surface of the axis 21 of the sleeve for rotation and displacement in the axial direction.

As shown in Fig.4, the clutch 45 clutch is made in the form of a tubular element having at one end the outer serrated teeth 45A, which can engage with the internal sawtooth teeth 22A. At the other end of the coupling 45 of the clutch is made part 45b of enlarged diameter with external sawtooth teeth 45C on the outer surface. External sawtooth teeth 45C Vicenza clutch 45 and part 45b of enlarged diameter provided with a tapered surface 45d. This tapered surface 45d is provided in order to lower the dog 53 first one-way clutch 50 from the raised position (the position of the power transmission, shown in Fig.4 by solid lines, in the space (outside) position, i.e. the position of the gap of the transmission path capacity shown dash-dotted line. When the clutch 45, the clutch is shifted from left to right in the low gear position, the dog 53 should conical surface 45d up on the part 45b of enlarged diameter and is omitted (unfold) in non-working position,

As shown in Fig.3, on the inner surface of the coupling 45 clutch made two ledge e and 45f, separated from each other in the axial direction. As shown in Fig.4, on the left ledge 45f made several Cam surfaces 47, spaced around the circumference. As shown in Fig.5, the Cam surface 47 has a flat surface 47A, dropping on one end, a curved surface 47b going down in the forward direction And from a flat surface 47A, and an inclined surface 47s, going up to a flat surface 47A in the same direction. The angle of the inclined surface 47s to the axis ranges from 20 to 70oand must be greater than angle a through the slits 21b.

the torque conversion efforts coupling 45 of the clutch to shift in the axial direction. The element 46 of the control contains the push rod 48, which is displaced in the working channel 21A along its axis, and the switch 49, which is pressed by the pushing rod 48 to the side of the carrier 41, as shown in Fig.3.

As shown in Fig.6, the push rod 48 has a control element 65 of a certain length, the actuating element 66 mounted on the remote end of the control element 65 so that it can be displaced in the axial direction, and the first coil spring (first bias element 60 between the control element 65 and the Executive element 66. The control element 65 includes a rod 68 and the plunger 69 mounted using the screw connections on the rod 68. The threaded shank 68A formed on the primary end of the rod 68 and at the other end is made the head 68b of enlarged diameter. The threaded shank 68A is connected to the plunger 69 by means of the threaded connection. Head 68b posted by slidable in the guide groove 66A inside element 66. Guide groove 66A is made with a reduced diameter at the end of element 66, which prevents it from slipping. The first coil spring 60 is installed in stressed condition between the control element 65 bias (pushing) force, so when the actuating element 66 transmits the pressure switch 49, the clutch 45, the clutch pressed to the side of the end of the carrier 41.

As shown in Fig.4, the switch 49 is made in the form of a rod of triangular cross-section, and when he transferred to the pressure, it moves through the slot 21b while turning in the opposite direction to the intended direction of rotation, i.e. with torsion. The contact surface 49b of the switch 49 in the slots 21b is made at an angle corresponding to the slits 21b. For example, if the angle a through the slits 21b 30othe angle of inclination of the contact surface 49b to the axis will also be about 30o. Movement of the switch 49 to the outside is limited by the internal coupling 45 of the clutch with the thrust ring 63 mounted on the inner surface of the other end of the coupling 45 of the clutch. Accordingly, the switch 49 may not come out of the clutches 45 clutch, as shown in Fig.4. As a result, the switch 49 under the action of the push rod 48 moves the sleeve 45 of the clutch to the left in Fig.3.

The switch 49 may also rest against a Cam surface 47 on the inside of the coupling 45 of the clutch. When the clutch 45 is face 47A of the Cam surface 47, when the switch 49 is pressed inclined surface 47s Cam surface 47 to the guide surface s side through the slits 21b, and its movement to the left in the axial direction is restricted, causing the displacement of the coupling 45 of the clutch to the right in the axial direction. Thus, the rotating force of the clutch 45, the clutch is converted into movement in the axial direction to operate the switch.

At both ends of the switch 49 is made grooves 49A to stop the second coil spring (second bias element) 61, which is the other end rests on the axis 21 of the sleeve. This second coil spring 61 constantly presses the switch 49 to the side of the clutch 45 clutch. The third coil spring (third bias element 62 is placed between the switch 49 and the sleeve 45 of the clutch. The third coil spring 62 is limited to a certain length and the compression pushes the switch 49 and the clutch 45 clutch from each other before the first hit the second. Due to this, the clutch 45, the clutch remains at a constant distance from the switch 49 during the move and has the exact positional installation.

In this example, bias the efforts of the coil spring is violence springs are reduced in this order. Thus, if the force of the first coil spring 60 is less than the force of the second coil spring 61, even if the switch 49 is transmitted to the pressure of the push rod 48, the first coil spring 60 will bend, and the switch 49 will not be shifted. If the force of the second coil spring 61 is less than the efforts of the third coil spring 62, even if the switch 49 will close the second coil spring 61, it does not fall on the Cam surface 47, and the control switch will not get ancillary effects.

The first coil spring 60 is placed in a relatively large space between the control element 65 and the Executive element 66 within the working channel 21A, so that you can increase the number of turns of the spring and thus to reduce the elastic force and the elastic spring stiffness. Accordingly, the force and the stiffness of the second and third coil springs 61 and 62 may be sequentially reduced, which will reduce the pressure on the push rod 48 during high transmission, that is, the operating force on the lever winding device 9 of the shift control. As a result, the tension of the inner cable will be less, and it is less likely to tear.

Design calendary lever 26 includes a supporting bracket 70, mounted on the end of the axis, and the link 71, mounted on a support bracket 70 can be rotated. The outer shell 73a cable 73 controls mounted with a focus on supporting bracket 70, and the inner cable 73b is installed with an emphasis on the link 71. The remote end of the link 71 hits on the basic end of the push rod 48. Thus, when the tension of the inner cable 73b through the device 9 controls the switching element 71 is rotated, passes the pressure on the push rod 48 and produces a shift in the direction of increased transmission. When the inner cable is released from tension, the sleeve 45 of the clutch is pressed the second coil spring 61 through switch 49 and switches in the direction of low transmission.

Brake design inertial movement

The brake 27 inertial motion is mounted on the housing 56 of the brake, as shown in Fig.2. The brake 27 inertial movement has mounted on the housing 56 of the brake roller 57, the outer Cam surface 41d on the other end of the carrier 41 and the brake pad 58, which transmits the braking on the inner surface at the other end of the housing sleeve 23. The design is such that during the rotation of the lead is the result of this displacement of the brake pad 58 is pressed against the inner surface of the housing sleeve 23 and applies the brakes.

When tightening the brake 27 inertial motion occurs tends to be jamming. This phenomenon is caused by the fact that when the first one-way clutch 50 is in a state of power transmission and cyclist pedalling backwards to slow down, drive force is transmitted in the same mode, which causes the actuation of the brake, and it cannot be released. In this example, the run to prevent this phenomenon for the first one-way clutch 50 is mounted to the housing 59 for dogs.

The housing 59 for dogs provides the creation of a particular corner of the free play between the teeth 23b ratchet on the housing sleeve 23 and the pawl 53 of the first one-way clutch 50 and allows you to release the brake until the yoke 43 is rotated by this angle free running. In particular, the housing 59 of the dog or prevents the lifting pawl 53 for rotation by a specific angle, or even if it rises, allows her rise to a position where it cannot lock the teeth 23b ratchet for rotation at a certain angle, and when the initial power-on of the drive provides a time delay until the dog 53 will rest against the teeth 23b ratchet at the initial moment of the drive.

Per sleeve 10 with the internal gear has:

- a tract of low power transmission, including a leading element 22, the yoke 43, the planetary gear mechanism 24, the led 41 and the housing 23 of the sleeve;

- the direct path of power transmission, including a leading element 22, the yoke 43 and the housing 23 of the sleeve; and

- a tract of high power transmission, including a leading element 22, the clutch 45 clutch, drove 41, planetary gear 24, the ferrule 43 and the housing 23 of the sleeve.

Gear shifting is performed by actuating the push rod 48 by a wire 73 to the control switch through the medium of a crank arm 26.

Shifting from low to high transmission

In the position shown in Fig.3, in which the push rod 48 is not moved inside, the clutch 45, the clutch is in the right end position low gear, and the rotation is transmitted from the driving element 22 on the housing 23 of the sleeve after lowering speed through a tract of low power transmission. In particular, applied to the leading element 22, the rotation is transmitted to the holder 43 through the second one-way clutch 51. To do this, the dog 53 first one-way clutch 50 is deployed coupling 45 of the clutch in the non-operating position shown in Fig.4, the dash-dotted line, and the first one-way clutch 50 is located is cut planetary gear 24, led 41 and the third one-way clutch 52. In this case, the input rotation speed is reduced in accordance with the gear ratio, which is determined by the number of teeth of the Central gear, satellites 42 and the shell 43.

When actuates the lever winding device 9 controls the switching element 71 of the crank arm 26 rotates and pushes the push rod 48 by one step (step). As a result of this action, because the force of the first coil spring 60 more force of the second coil spring 61, the switch 49 under the action of the pushing force from the link 71 through the push rod 48 is directed through the slot 21b and is shifted to the left as shown in Fig. 3, while turning around the axis of the sleeve, and the sleeve 45 of the clutch is also shifted to the position of the direct transmission under the action of the pushing force through the thrust ring 63. As soon as the clutch 45, the clutch is installed in the position of direct transmission, shown in Fig.7, the pawl 53 of the first one-way clutch 50, which was taken off the conical surface 45d, the return helical spring 55 in the raised position, shown in Fig.4 solid lines. In this state, the first one-way clutch 50 SPE) from the driving element 22 is transmitted to the casing 23 of the sleeve on the direct path of power transmission. In particular, transmitted to the leading element 22, the rotation is transmitted to the holder 43 through the second one-way clutch 51, and then on the housing 23 of the sleeve through the first one-way clutch 50, that is, the rotation of a driving element 22 is directly transmitted to the housing 23 of the sleeve over the ferrule 43. When this rotation from the carrier 43 is also transmitted and drove 41 through the planetary gear 24, and the carrier 41 rotates at a reduced speed, but due to the fact that the housing 23 of the sleeve rotates faster than the carrier 41, the transmission of rotation from the carrier 41 on the housing 23 of the sleeve through a third one-way clutch 52 is not happening.

When the winding lever is actuated from the position of the direct transmission and the push rod 48 is pushed further, the switch 49 is moved farther to the left, and the clutch 45 clutch respectively translated to a position of increased transmission. In this position, shown in Fig.8, external serrated teeth 45C coupling 45 of the clutch are engaged with the internal sawtooth teeth 41b carrier 41. In the process of translation coupling 45 of the clutch in the position of high transmission, when the outer teeth 45C and the internal teeth 41b are in such relative position that can engage, the clutch 45, the clutch is moved to direct ahadada in this position, they cannot engage in the moment of contact of the coupling 45 of the clutch with the planet carrier 41, the switch 49 and the clutch 45 clutch temporarily stop its movement to the left. When this occurs, the actuating element 66 of the push rod 48 moves backwards, compressing the first coil spring 60 and transmitting the pressure switch 49. After the coupling 45 of the clutch will rotate to the position when the teeth 45C and 41b can engage, elastic (bias) force of the first coil spring 60 through switch 49 pushes the clutch 45, the clutch is on, and the teeth 45C and 41b engages.

This position is transmitted to the leading element 22, the rotation is transmitted to the casing 23 of the sleeve on the path of increased power transmission. In particular, it is transmitted from the driving element 22 through the sleeve 45 of the clutch on the carrier 41 and forth from him on the body 23 of the sleeve through the planetary gear mechanism 24, the ferrule 43 and the first one-way clutch 50. In this case, the input rotation speed increases output in accordance with the gear ratio, which is determined by the number of teeth of the Central gear 40, satellites 42 and the shell 43. There is an attempt to transmit rotation from the driving element 22 on the holder 43 through the second unilateral who Yuyu clutch 51, the rotation is not transmitted.

Because in the process of switching from a lower to a higher gear rotation is transmitted directly from the driving element 22 on the holder 43, it is best to provide the offset coupling 45 of the clutch in the unloaded state. Accordingly, the force of the first coil spring 60, the clamping sleeve 45 of the clutch can be reduced, and furthermore, since the force of the second coil spring 61 even less, can be achieved by switching with little effort.

The gear change from high to low with ancillary effects

When the release lever of the control device 9 is actuated in the position of high transmission, as shown in Fig.8, the bias force of the first coil spring 60 is removed, and a second coil spring 61 presses the switch 49, causing the withdrawal of the push rod 48 by one step (step) to the right. When this switch 49 transmits the pressure to the clutch 45 through a third clutch coil spring 62 and is trying to shift the sleeve 45 of the clutch in the position of direct transmission. If the cyclist does not push on the pedal and the driving force is not transmitted, the clutch 45 is separated from the led 41 and shifts in the position of direct transmission. However, if the rider works the pedals, because of obraznye internal teeth 41b and the outer teeth 45C. In this case, one of the efforts of the second coil spring 61 is not enough to shift the clutch 45 to the right in Fig.8. In this state, when the switch 49 rests against a flat surface 47A of the Cam surface 47 of the coupling 45 of the clutch, as shown in Fig.5, the switch 49 is pressed against the guide surface s along the entire length of its part contained in the slot 21b, and is held by the friction force from the output in the axial direction. As a result, when the switch 49 it up on the inclined surface 47s, the clutch 45, the clutch is moved to the right. After sawtooth internal teeth 41b and the outer teeth 45C disengages the clutch 45 of the clutch under the action of the pressure of the second coil spring 61 through the switch 49 is shifted to the position of the direct transmission. Thus, the contact between the Cam surface 47 of the coupling 45 of the clutch and switch 49 contributes to the switch by converting the rotational motion of the coupling 45 of the clutch in the shift along the axis.

Thus, as mentioned, the switch 49 cannot easily deviate to the left in the axial direction, as he pressed the second coil spring 61, and a through slot 21b tilted and passes through the spiral otnositel the pressing force of the second coil spring 61 and the friction between the switch 49 and the guide surface s. However, in the case where the driving force is higher than the above-mentioned power switch 49 may overcome the bias force of the second coil spring 61 and the frictional force of contact with the rail surface s and to move to the left in the axial direction without displacement of the coupling 45 of the clutch. Mentioned frictional force is defined here by the angle of inclination of the slot. If this angle is set too large, the switch 49 will be difficult to move to the left under the pressure of the push rod 48. If the angle is set too small, then less will be the resistance to displacement of the push rod 48, but will also decrease the frictional force. Accordingly, the angle of the slits must lie in the range from 10 to 50o. The ultimate driving force, when the switch 49 is rejected during the specified auxiliary exposure can be adjusted by selection of the angle of inclination of the slot, the angle of inclination of the inclined surface 47s Cam surface 47 and the efforts of the three coil springs 60, 61 and 62.

Further, even when the driving force is greater than the set limit, and the switch 49 is deflected in the axial direction without displacement of the coupling 45 of the clutch, as soon as the sprocket 18 with pedals will reach the region in the receiving auxiliary pressure switch 49. Thus, the switching will not occur in the transmission of excessively high drive force, for example, on a steep incline, which reduces shock loads when switching and helps to prevent breakage of the power transmission elements, such as sawtooth teeth and one-way clutches.

When the clutch 45, the clutch is moved, the switch 49 is held from contact with the Cam surface 47 through a third coil spring 62. Accordingly, there will be no noise from contact with the switch 49, even if the coupling 45 of the clutch rotates. In the position of direct transmission, shown in Fig.7, the rotation is transmitted from the driving element 22 on the housing 23 of the bushing through the direct path of power transmission in the manner described above.

Upon actuation of the release lever device 9 controls the switch in position direct transmission clutch 45 clutch push rod 48 moves further, and the switch 49 transmits the pressure to the clutch 45 clutch. When this tapered surface 45d coupler 45 clutch comes in contact with the dog 53 first one-way clutch 50 and tends to lower the dog from the raised working position in the designated outside. However, because the dog 53 transmits the force from the clip 43 n is when the shock switch contact 49 with the Cam surface 47 of the clutch 45, the clutch is created helper impact as described above, so that the clutch 45, the clutch is shifted in the axial direction, and the pawl 53 may be omitted.

It should be noted that since the rotation is transmitted directly to the yoke 43 without the participation of the clutch 45, the clutch requires less force when switching to a higher gear from low gear. Further, since the rotating force of the clutch 45, the clutch has a supporting effect by converting to an offset in the axial direction when switching from a position of increased transmission in a low gear position, the rider can shift gears with little effort, pedal, even to a higher gear.

The second example run

In the described first exemplary embodiment, the lower elastic efforts was achieved in the process of switching to a higher gear through the installation of the first coil spring 60 by pushing the rod, but instead of pushing rod 48 on the first execution can be used the rod 48A, made in the form of a rod-like element shown in Fig.9. In this case, the first coil spring 60 is placed in a tensioned state between the coupling 45 of the clutch inner and Conoco is 61, then the third coil spring 62, and then the first coil spring 60. Thus, if the bias force of the second coil spring 61 is less than the force of the third coil spring 62, even if the switch 49 is transmitted to the pressure at the tap of the push rod 48A in the direction of low transmission, the switch 49 will not have any impact on the sleeve 45 of the clutch, and an auxiliary force will not be obtained. Further, if the bias force of the third coil spring 62 will be less than the efforts of the first coil spring 60, when the push rod 48A aside low gear and the second coil spring 61 transmits the pressure switch 49, the third coil spring 62 is bent, will only shift the switch 49, and the switch 49 and the clutch 45, the clutch will not be able to move apart from each other, so that the clutch 45, the clutch will not be able to be positioned. The switch 49 shifts the clutch 45 clutch only in the direction of low transmission, and in the direction of increased transmission they move independently. In other words, the clutch 45, the clutch is not provided in the retaining ring. The total length of the third coil spring 62 is limited to a certain length limiting element (not shown), and the distance between the clutches is of steel construction does not differ from the first exemplary embodiment and is not described.

Shifting from low to high

In the second exemplary embodiment in the position shown in Fig.9, when the push rod 48A is not under pressure, the clutch 45 clutch is located in the right end position in the low gear position, and the rotation from the driving element 22 is transmitted to the casing 23 of the sleeve with the lower speed through a tract of low power transmission, as in the first exemplary embodiment. In particular, the rotation applied to the leading element 22, is transmitted further to the holder 43 through the second one-way clutch 51.

When actuates the lever winding device 9 controls the switching element 71 of the crank arm 26 is rotated, and the push rod 48A is moved up one step (step). As a result of this action the switch 49 is transmitted to the pressure of the push rod 48A, and he shifts to the left, while turning around the axis of the sleeve, and the sleeve 45 of the clutch, which is under the action of the first coil spring 60, followed by the switch 49 and moves to the position of direct transmission. As soon as the clutch 45, the clutch will be in the position of direct transmission, the dog 53 first one-way clutch 50, which was transferred outside paloposki lines, and the rotation from the driving element 22 is directly transmitted to the housing 23 of the sleeve, as in the first example.

When the winding lever is actuated from the position of the direct transmission and the push rod 48A moves on, the switch 49 is moved farther to the left, and the clutch 45 clutch follows him and goes to the position of high transmission. In this position the outer serrated teeth 45C clutch 45, the clutch engages with the internal sawtooth teeth 41b carrier 41. During this movement the clutch 45 clutch) to a position of increased transmission when the shock of contact of the coupling 45 with the planet carrier 41 sawtooth outer teeth 45C and the internal teeth 41b are in such relative position that can engage, the clutch 45, the clutch is translated directly into a position of increased transmission to the left. However, if these teeth are in such a position that they could not engage, when the shock of contact of the coupling 45 of the clutch with the planet carrier 41, the clutch 45 is temporarily suspending its movement to the left. However, due to the fact that the coupling 45 of the clutch is pressed by the force of the first coil spring 60, after rotation of the coupling 45 of the clutch to the position when the teeth 45C and 41b can engage, it moves the and the housing 23 of the sleeve on the path of high power transmission, as in the first example of execution.

Because in the process of switching from the lowered position to the elevated position of the transmission, the rotation is transmitted directly from the driving element 22 on the holder 43, it is best to provide the movement of the coupling 45 of the clutch in the unloaded state. Accordingly, the force of the first coil spring 60, the clamping sleeve 45 of the clutch can be reduced, and the switching can be done with little effort.

Shifting from high to low with ancillary effects

When the transmission elements are in positions of increased transmission, and the release lever device 9, the control switch is actuated, the switch 49 is transmitted to the pressure of the second coil spring 61, and the push rod 48A is moved to the right one step. When this switch 49 transmits the pressure to the clutch 45 of the clutch and try to shift it to the position of the direct transmission. However, if the rider works the pedals, because of the transfer drive force from the clutch 45 clutch on the carrier 41, due to the friction forces sawtooth internal teeth 41b and the outer teeth 45C may remain in engagement. In this case, the generated auxiliary force, and it even in the case where the driving force is greater than the set limit, and the switch 49 is moved in the axial direction without displacement of the coupling 45 of the clutch, as soon as the sprocket 18 with the pedal reaches the upper or lower dead point, and the driving force decreases, the clutch 45, the clutch will be shifted under the action of the supporting force from the switch 49. Thus, in this second exemplary embodiment, the switching will not occur in the transmission of excessively large drive force, which reduces the shock load when switching and helps to prevent breakage of the power transmission elements, such as sawtooth teeth and one-way clutches.

When the clutch 45, the clutch is moved to the right, the switch 49 is held from contact with the Cam surface 47 of the third coil spring 62. Accordingly, there will be no noise from contact with the switch 49, even if the coupling 45 of the clutch rotates. When the clutch 45 clutch holds the position of direct transmission, the rotation is transmitted via the direct path of power transmission.

Upon actuation of the release lever device 9 controls the switch to position direct transmission clutch 45 clutch push rod 48A moves dividing it comes in contact with the dog 53 first one-way clutch 50 and tries to drop a dog from a raised working position in the designated outside. However, due to the fact that the dog 53 transmits power from the carrier 43 on the housing 23 of the sleeve, it is not so easy to drop into the non-working position by one force of the second coil spring 61. And here at shock switch contact 49 with the Cam surface 47 of the clutch 45, the clutch is created of the subsidiary force, and the clutch 45, the clutch is moved in the axial direction, as described above.

Here produces the same advantages as in the first exemplary embodiment, and also simplifies the design of the push rod 48. However, in this case, the greatest bias force has a second coil spring 61 located in a relatively narrow space, and if it is provided with sufficient strength, to reduce the rigidity of the second coil spring 61 is difficult, and when the bending force increases sharply. Accordingly, it requires a larger work force when shifting gears compared to the first example of execution.

The third example implementation

In the above-described second exemplary embodiment, the clutch was in the low gear position (shown in Fig.9) without transmitting pressure pushing rod; in this third exemplary embodiment, the coupling 45 clutch pokazaniyam the rod 48. The first coil spring 60 is located between the sleeve 45 and clutch cone sleeve 31. Bias the efforts of three coil springs 60, 61 and 62 are also reduced in order: the second coil spring 61, the third coil spring 62, and then the first coil spring 60. The reasons for such order bias efforts springs are the same as in the second example of execution.

As shown in Fig.10, the working channel 21A is made along the axis of the sleeve from its left end, which has a brake inertial motion, to the middle. A bell crank (not shown) mounted on the left end of the axis 21 of the sleeve. Since the push rod 48 passes impact on the triangular top of the switch 49A, in the center of the switch 49A is made a groove having a surface 49b for contact with the push rod 48. The first coil spring 60 is placed in a tensioned state between the sleeve 45 and clutch cone sleeve 31, as in the second exemplary embodiment. In other respects the construction is the same as the second exemplary embodiment and will not be here described.

Shifting from high to low with ancillary effects

In the third exemplary embodiment in Fig.10 shows a state of transmission in positions of high transmission, when the pushing is the group of the switch 49A is transmitted to the pressure of the push rod 48, and the sleeve 45 of the clutch moves toward the low gear against the bias of the efforts of the first coil spring 60. In this case, if the driving force is not transmitted, the switch 49A transmits the pressure to the clutch 45 through a third clutch coil spring 62, and the clutch 45, the clutch is moved to the position of the direct transmission. When the driving force is transmitted, the switch 49A strikes the Cam surface 47, flexing third coil spring 62 or the second coil spring 61, and moves the sleeve 45 of the clutch using the above-mentioned auxiliary efforts. When the transfer is made from the position of direct transmission in a low gear position, if you pass the driving force and there is the challenge of translating pawl 53 outside the allotted position, the clutch 45, the clutch moves the auxiliary force, the dog 53 is translated in the designated position, and the clutch 45, the clutch goes into the low gear position.

Further, even when the driving force is greater than the set limit, and the switch 49A moves in the axial direction without displacement of the coupling 45 of the clutch, as soon as the sprocket 18 with pedals will reach the region very, and it will move under the action of supporting the efforts of the switch 49A. Thus, in this third exemplary embodiment, the switching will not occur in the transmission of excessively large drive force, which reduces the shock load when switching and helps to prevent breakage of the power transmission elements, such as sawtooth teeth and one-way clutches.

Shifting from low to high

When in the lowered position of the transmission is driven by the release lever device 9 controls the switching clutch 45 clutch is pressed in the direction of low transmission bias force of the first coil spring 60, the push rod 48 is moved, and the coupling 45 of the clutch means in position to direct transmission. When the clutch 45, the clutch will be in the position of direct transmission, the dog 53 first one-way clutch 50, which was allocated outside of the position of the conical surface 45d, is returned by the force of the coil spring 55 in the raised position, shown in Fig.4 by solid lines, and the rotation from the driving element 22 is directly transmitted to the housing 23 of the bushing through the direct path of power transmission, as in the first and second examples.

When the lever asvab the transmission force of the first coil spring 60, the push rod 48 is moved, and the clutch 45, the clutch is moved to the position of high transmission. In this position of increased transmission exterior sawtooth teeth 45C coupling 45 of the clutch are engaged with the internal sawtooth teeth 41b carrier 41. In the process of moving to a position of increased transmission, if the sawtooth outer teeth 45C and the internal teeth 41 b are in such relative position that can engage, the clutch 45 is moved directly to the position of high transmission left after the shock of contact of the coupling 45 of the clutch with the planet carrier 41. However, if these teeth are in such a position that they could not engage in a moment of shock contact coupling 45 of the clutch with the planet carrier 41 is temporarily suspends its movement to the left. However, due to the fact that the clutch 45 clutch applied bias force of the first coil spring 60, after rotation of the coupling 45 of the clutch to the position when the teeth 45C and 41b can engage, it moves further and teeth 45C and 41b engages. In this position the rotation applied to the leading element 22, are transmitted to the body 23 of the bushing through the path of high power transmission, as in the first and second examples.

P is carried out directly from the driving element 22 on the holder 43, it is best to provide the offset coupling 45 of the clutch in the unloaded state. Accordingly, the force of the first coil spring 60, the clamping sleeve 45 of the clutch can be reduced. In addition, since the largest is the bias force of the second coil spring 61, which has a large space to accommodate the total elastic force can be reduced and the switching can be done with little effort in the process of movement with the transfer of drive force.

Other examples run

Pushing the rod in the third exemplary embodiment may be a rod in the form of a rod-like element, as in the second example. In this case, since the push rod limits the movement of the switch in the direction of the end axis of the sleeve, a through cut can be made along the axis. When you shifting can be performed at any time, as an auxiliary force will be generated even when a large drive force. Here, however, the rod will be subjected to higher loads, and internal cable management. Shock loads when switching will also be significant, so that the transmission elements should be strengthened.

In opisannogo movement, however, if the brake is not set, then in this case there is no need.

The mechanism for transmitting rotation is not limited to the planetary gear mechanism, instead it can be a planetary roller mechanism.

Advantages of the invention

As described above, in a Bicycle hub with an internal gear in accordance with the invention, the relationship of the clutch control switch during movement of the clutch in the position of low transmission converts the rotating force of the clutch in force offset in the axial direction and creates an auxiliary force, so that the movement of the clutch easier, and it can be removed with less effort even while driving. The clutch can be shifted by the application of a small effort and also because during her move to the position where high transmission is not passed on to any power. Accordingly, the shifting can be performed in both directions with the application of a small load even in the position of the transfer drive force during the movement.

1. Domestic transmission cycle of the sleeve containing the axis (21) of the sleeve for Zac axis (21) of the sleeve, output element (23) mounted for rotation about an axis (21) of the sleeve, a planetary mechanism (24) includes a Central gear (40) placed on the axis (21) of the sleeve carrier (41) is mounted rotatably about an axis (21) of the sleeve satellite (42) mounted on the drive rod (41) rotatably and included in mesh with the Central gear (40) and the holder (43) mounted rotatably about an axis (21) sleeve and member engages the satellite (42), the first one-way clutch (50) located in the path of power transmission between the ferrule (43) and the output element (23) and installed with the ability to switch between the provisions of the power transmission and disconnection of the power transmission in position under load transmitted power, the clutch (45) clutch mounted on the axis for selective switching of the path of power transmission between the leading element (22) and the output element (23), and element (46) of the control switch, characterized in that that it further comprises a second one-way clutch (51) located in the path of power transmission between the leading element (22) and the holder (43), and the third one-way clutch (52) located in the path of power transmission between the si in accordance with rotation of a driving element (22) and move in the axial direction relative to the axis (21) of the sleeve, and the element (46) of the control switch is arranged to move the clutch (45) clutch in the direction of the axis of the sleeve and interaction with coupling (45) clutch for converting the rotational motion of the clutch (45) clutch in moving the clutch (45) clutch in the axial direction of the sleeve.

2. Internal transfer sleeve under item 1, characterized in that the element (46) switching control is executed in the form of a guide surface adjacent to the axis (21) of the sleeve switch (49) that is moved along the guide surface to move the clutch (45) clutch in the axial direction of the axis of the sleeve and element (48, 61, 66) displacement of the switch to move the switch (49).

3. Internal transfer sleeve under item 2, characterized in that the clutch (45) clutch provided with a Cam surface (47) located in the axial direction of the sleeve, and a switch (49) is pressed against the Cam surface (47) to convert the rotational motion of the clutch (45) clutch in motion coupling (45) clutch in the axial direction of the axis of the sleeve.

4. Internal transfer sleeve under item 2 or 3, characterized in that the axis (21) of the sleeve provided with a spiral slot (21b), and a guide surface formed this spiral p is a surface inclined to the axis of the sleeve at an angle of between 10 to 50o.

6. Internal transfer sleeve on one of the PP. 3-5, characterized in that the Cam surface (47) is inclined to the axis of the sleeve at an angle of 20 to 70o.

7. Internal transfer sleeve on one of the PP. 4-6, characterized in that a spiral cut (21b) is made through the axis (21) of the sleeve.

8. Internal transfer sleeve on one of the PP. 4-7, characterized in that the part of the switch (49) is performed with a triangular cross-section and placed inside the spiral slots (21b) perpendicular to the axis of the sleeve.

9. Internal transfer sleeve under item 8, characterized in that the part of the triangular cross-section was put into contact with the rail surface.

10. Internal transfer sleeve on one of the PP. 2-9, characterized in that the clutch (45) clutch selectively introduced in engagement with the planet carrier (41) for transmitting the rotational motion of a driving element (22) on the carrier (41).

11. Internal transfer sleeve on one of the PP. 2-10, characterized in that the element (48) shift switch is set to move switch (49) to the cage (41).

12. Internal transfer sleeve on one of the PP. 2-11, characterized in that it is equipped with the first searchlocate (49) to the coupling (45) clutch and the third shifting element (62) to offset switch (49) from coupling (45) clutch.

13. Internal transfer sleeve on one of the PP. 2-12, characterized in that the switch (49) is installed with the possibility of pressure on the clutch (45) clutch in the opposite axial directions of the axis of the sleeve.

14. Internal transfer sleeve under item 12 or 13, characterized in that the element displacement switch is made in the form element (66) contact switch (49), and item (68b) control that is installed with the possibility of sliding in the Executive element (66), and at least one of the above-mentioned first, second and third shifting elements (60-62) is mounted for displacement element (66) and item (I) management in opposite directions.

15. Internal transfer sleeve under item 14, characterized in that the actuating element (66) is installed with the possibility of the clamp switch (49) to the cage (41).

16. Internal transfer sleeve under item 14 or 15, characterized in that the first shifting element (60) is mounted for displacement element (66) and item (68b) management in opposite directions, and the bias force of the first bias element (60) is greater than the second shifting element (61), and the internal transfer sleeve on p. 14, characterized in that the actuating element (66) is installed with the possibility of pressing the switch (49) from the carrier (41).

18. Internal transfer sleeve under item 17, characterized in that the second shifting element (61) is mounted for displacement element (66) and item (68b) management in opposite directions, and the bias force of the second shifting element (61) is greater than the third shifting element (62), and the bias force of the third shifting element (62) is greater than the first bias element (60).

19. Internal transfer sleeve under item 12, wherein the bias force of the second shifting element (61) is greater than the third shifting element (62), and the bias force of the third shifting element (62) is greater than the first bias element (60).

 

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Bicycle // 2463194

FIELD: transport.

SUBSTANCE: invention relates to bicycle with pedal drive incorporating reciprocating levers. On drive wheel axle (22), outer part of telescopic lever is installed. Gear (23) is installed on outer part of telescopic lever. Arc-shaped pinion rack (24) is mounted on bicycle frame. Gear (25) is linked with one-way rotation clutch (27). Gear (23) is engaged with arc-shaped pinion rack (24) and with gear (25).

EFFECT: elimination of chain gear.

2 cl, 6 dwg

FIELD: transport.

SUBSTANCE: invention relates to gearshift actuators in planetary transmissions in wheel hub. Pair of sun gears has fixing projections (23b) for engagement with axle (10) via pawls (12b, 13b). Sun gears disengagement from axle (10) is provided by pawl control ring. This ring has casing (16) with hold-down elements (18) in the form of rollers. Splined grooves (27b) are created on inner circumference of carrier (20) or on separate body (29) capable to slip relative to carrier (20). Carrier (20) rotation provides gradual pushing out of hold-down elements (18) from deep section of splined grooves (27b) with corresponding holding down pawls (12b) and their disengagement from fixing projections (23b) of one of sun gears.

EFFECT: solution is intended to use impelling force of pedal and/or motor as auxiliary force to facilitate shifting.

10 cl, 36 dwg

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