KR102343462B1 - Transmission apparatus with one-way bearing and reverse clutch - Google Patents

Abstract

The present invention relates to a transmission apparatus with a one-way bearing and a reverse clutch. The present invention aims to provide a transmission apparatus with a one-way bearing and a reverse clutch, in which a low-end gear is bound and installed on an input shaft by the one-way bearing, and which has the reverse clutch connected to the input shaft and the low-end gear, thereby allowing the normal/reverse rotation of the low-end gear. According to the present invention, the transmission apparatus with the one-way bearing and the reverse clutch comprises: an input shaft whose one side end is connected to a power unit, and in which the low-end gear is connected by a one-way bearing, and in which a high-end gear is installed to be supported by the bearing; a transmission clutch installed on the other side end of the input shaft and connected to the high-end gear; the reverse clutch installed on one side of the input shaft and connected to the low-end gear; and an output shaft rotated and driven as the rotary driving force of the low-end gear and the high-end gear is transferred by a reducing unit. The normal-directional rotary driving force (forward driving force) of the input shaft is transferred to the output unit through the low-end gear and the reducing unit or is transferred to the output unit through the transmission clutch, the high-end gear, and the reducing unit. The reverse-directional rotary driving force (backward driving force) of the input shaft is transferred to the output unit through the reverse clutch, the low-end gear, and the reducing unit.

Description

Transmission apparatus with one-way bearing and reverse clutch

The present invention relates to a transmission having a unidirectional bearing and a reverse clutch. In a transmission in which a driving force of an input shaft is transmitted to an output shaft by a unidirectional bearing, a reverse clutch is installed at one end of the input shaft so that the forward rotation driving force of the input shaft is It relates to a transmission having a one-way bearing and a reverse clutch that is transmitted to an output shaft through a lower gear constrained by a one-way bearing, and a reverse rotational driving force of an input shaft is transmitted to an output shaft through a reverse clutch and a lower gear.

Recently, energy saving policies are being promoted due to the depletion of energy resources and the protection of the global environment due to problems such as air pollution and global warming caused by automobile exhaust. To solve these problems, electric vehicles, hybrid electric vehicles, fuel cell electricity Interest in eco-friendly vehicles such as automobiles is increasing.

In general, an electric vehicle uses electricity as a fuel, unlike a gasoline engine, and uses an electric motor as a power source. A power transmission structure that drives the driving wheels by decelerating has been mainly used, but recently, research on a shift system that extends the driving range of a vehicle and improves driving performance by transmitting power from an electric motor to the driving wheels more efficiently is being actively pursued.

Conventional electric vehicles have excellent motor characteristics and thus a reducer having a single gear ratio is widely used. Two-speed gearboxes are widely used.

Conventional two- or three-speed gearboxes have a large number of external gears, locking devices, shift mechanisms, etc., so their structure is very complicated, assembling is deteriorated, the number of components increases, and complicated connections are made. Due to the relationship, a power loss phenomenon occurred in which the power of the power source could not be transmitted to the output shaft quickly, and there was a problem in that the shift performance was deteriorated.

In order to solve the complex configuration of the conventional transmission as described above and the resulting power loss, a transmission having a one-way bearing installed, that is, a transmission installed on the input shaft so that a lower gear is constrained by the one-way bearing, is being developed.

However, when the driving force of the input shaft is transmitted to the output shaft by the lower gear constrained by the unidirectional bearing on the input shaft, the number of gear parts for transmitting the driving force is reduced, so the structure is simple and the setting and assembly of the gear ratio are easy. However, since the unidirectional bearing rotates idling when the input shaft rotates in the reverse direction, there is a problem in that the reverse rotation force of the input shaft is not transmitted to the output shaft, that is, the reverse rotation is not performed.

Registered Patent Publication No. 10-1805109 (2017.11.29) Registered Patent Publication No. 10-1805100 (2017.11.29) Registered Patent Publication No. 10-1843032 (2018.03.22) Registered Patent Publication No. 10-1952775 (2019.02.21)

An object of the present invention is to provide a transmission in which a lower gear is constrained to an input shaft by a one-way bearing, and a reverse clutch is connected to the input shaft and the lower gear to provide a one-way bearing and a reverse clutch capable of performing forward/reverse rotation of the lower gear. It is to provide an equipped transmission device.

The present invention relates to an input shaft having one end connected to a power unit, a lower gear being connected and installed by a unidirectional bearing, and a higher gear being supported by a bearing; a shift clutch installed at the other end of the input shaft and having a high gear connected thereto; a reverse clutch installed on one side of the input shaft and connected to a lower gear; The forward rotational driving force (forward driving force) of the input shaft, including; an output shaft to which rotational driving force of the lower gear and the upper gear is transmitted by the reduction unit, is transmitted to the output unit, or transmitted to the output unit through the lower gear and the reduction unit It is transmitted to the output unit through the gear and reduction unit, and the reverse rotational driving force (reverse driving force) of the input shaft is configured to be transmitted to the output unit through the reverse clutch, the lower gear and the reduction unit.

According to the present invention, the low gear is installed to be constrained to the input shaft by a unidirectional bearing, and a reverse clutch is connected to the low gear and the input shaft. While being easily accomplished, there is an effect that the reverse function is achieved by the reverse clutch.

That is, in the present invention, when the input shaft is driven in the forward direction, the forward rotational driving force is transmitted to the output shaft through the low or high gear of the input shaft. By being coupled to the latch engaging groove of the inner rotating body, the outer rotating body and the inner rotating body to which the lower gear is connected and installed are rotated in the reverse direction integrally, so that the reverse rotational driving force is transmitted to the output shaft, thereby making forward and backward movements.

In the present invention, since the latch of the reverse clutch is operated by centrifugal force to release the restraints of the inner and outer rotors, when the input shaft rotates in the forward direction at high speed, the inner/outer rotor rotates without interference, and noise caused by the contact of the latch And there is an effect that the impact does not occur.

In the present invention, the rotational driving force of the input shaft is automatically transmitted to the output shaft by the centrifugal rocker part of the speed change clutch, and when power is transmitted from the input shaft to the output shaft, the shock and vibration in the rotational direction are absorbed and buffered (attenuated) by the power transmission buffer part. ), which has the effect of improving power transmission and marketability.

In the present invention, an auxiliary locking unit is further installed in the shift clutch, and when power is transmitted from the input shaft to the output shaft by the centrifugal rocker unit, even if the rotational speed of the input shaft is lowered, the operating state of the centrifugal rocker unit is an auxiliary set value by the auxiliary locking unit , so that a sudden change in power transmission efficiency is prevented.

1 is an exemplary view showing a configuration according to the present invention;
2 is another exemplary view showing a configuration according to the present invention;
3 is an exemplary view showing an exploded configuration of the reverse clutch according to the present invention;
4 is an exemplary view showing the configuration of the inner rotating body of the reverse clutch according to the present invention;
5 is an exemplary view showing the configuration of the outer rotating body of the reverse clutch according to the present name;
6 is an exemplary view showing an operating state of the reverse clutch according to the present invention;
7 is an exemplary view showing the overall configuration of a transmission according to the present invention;
8 is an exemplary view showing the connection relationship of the transmission according to the present invention;
9 is another exemplary view showing a simplified configuration of a transmission according to the present invention;
10 is an exemplary view showing the configuration of a shift clutch according to the present invention;
11 is an exemplary view showing an exploded configuration of a shift clutch having a torsion spring type centrifugal rocker unit according to the present invention;
12 is an exemplary view showing the configuration of a torsion spring type centrifugal rocker unit according to the present invention;
13 is an exemplary view showing a non-operating state of a torsion spring type centrifugal rocker unit according to the present invention;
14 is an exemplary view showing an operating state of a torsion spring type centrifugal rocker unit according to the present invention;
15 is another exemplary view showing the operating state of the torsion spring type centrifugal rocker unit according to the present invention;
16 is an exemplary view showing an exploded configuration of a shift clutch having a coil spring type centrifugal rocker unit according to the present invention;
17 is an exemplary view showing the configuration of a coil spring type centrifugal rocker unit according to the present invention;
18 is an exemplary view showing a non-operating state of a coil spring type centrifugal rocker unit according to the present invention;
19 is an exemplary view showing the operating state of the torsion spring type centrifugal rocker unit according to the present invention;
20 is an exemplary view showing the configuration of the clutch first rotor of the shift clutch according to the present invention;
21 is an exemplary view showing the configuration of the clutch second rotor of the shift clutch according to the present invention;
22 is an exemplary view showing the configuration of a centrifugal rocker unit having a power transmission buffer (spring-type buffer) according to the present invention;
23 is an exemplary view showing an operating state by the present invention power transmission buffer (spring-type buffer)
24 is another exemplary view showing an operating state by the present invention power transmission buffer (spring-type buffer)
25 is an exemplary view showing the configuration of a centrifugal rocker unit having a power transmission buffer (friction pad type buffer) according to the present invention;
26 is another exemplary view showing the configuration of a centrifugal rocker unit having a power transmission buffer (friction pad type buffer) according to the present invention;
27 is an exemplary view showing the configuration of the back plate and the rotating body of the power transmission buffer (friction pad type buffer) according to the present invention
28 is an exemplary view showing the configuration of the pad portion of the power transmission buffer (friction pad type buffer) according to the present invention
29 is an exemplary view showing the operation of the pad portion and the pressing member of the power transmission buffer (friction pad type buffer) according to the present invention
30 is an exemplary view showing the configuration of the pressing member of the power transmission buffer (friction pad type buffer) according to the present invention

1 is an exemplary diagram showing a configuration according to the present invention, FIG. 2 is another exemplary diagram showing a configuration according to the present invention, FIG. 3 is an exemplary diagram showing an exploded configuration of a reverse clutch according to the present invention, FIG. 4 is an exemplary view showing the configuration of the inner rotating body of the reverse clutch according to the present invention, Figure 5 is an exemplary view showing the configuration of the outer rotating body of the reverse clutch according to the name of the present invention, Figure 6 is the operating state of the reverse clutch according to the present invention 7 is an exemplary view showing the overall configuration of the transmission according to the present invention, FIG. 8 is an exemplary diagram showing the connection relationship of the transmission according to the present invention, and FIG. 9 is a transmission according to the present invention As another example diagram showing the simplified configuration of

Transmission device 800 according to the present invention,

an input shaft 810 having one end connected to the power unit 860, a lower gear 811 connected by a unidirectional bearing 813, and a higher gear 812 installed such that the bearing 814 is supported;

a shift clutch 100 installed on the other end of the input shaft 810 and having a high gear 812 connected thereto;

a reverse clutch 200 installed on one side of the input shaft 810 and having a low gear 811 connected thereto;

Including;;

The forward rotational driving force (forward driving force) of the input shaft 810 is transmitted to the output shaft 840 through the low gear 811 and the reduction unit 830, or the shift clutch 100 and the high gear 812 and the reduction unit ( 830) is transmitted to the output shaft 840, and the reverse rotational driving force (reverse driving force) of the input shaft 810 is transmitted to the output shaft 840 through the reverse clutch 200, the lower gear 811 and the reduction unit 830. is structured to be

That is, in the present invention, the rotational driving force of the input shaft 810 axially connected to the power unit 860 is transmitted to the output shaft 840 through the lower gear 811 constrained to the input shaft 810 by the unidirectional bearing 813, or In the transmission device (800) supported by a bearing on the input shaft (810) and transmitted to the output shaft (840) through a high gear (812) connected to the shift clutch (100);

A reverse clutch 200 is connected and installed to the input shaft 810 and the lower gear 811,

The reverse clutch 200,

A plurality of latch receiving grooves ( 212) and an outer rotating body 210 provided with,

The inner rotor is provided with a play in the receiving groove 211 of the outer rotating body so as to be driven integrally with the input shaft 810, the bearing 250 is supported, and the inner rotating body is provided with a plurality of latch engaging grooves 221 on the outer circumferential surface 220a. (220) and;

a latch 230 having one side coupled to a pin 260 in the latch receiving groove 212 of the outer rotating body;

The other side of the latch 230 has an elastic force so that it is moved into the receiving groove 211 of the outer rotating body, and the outer rotating body 210 and the other side of the latch 230 include an actuating spring 240 having both ends connected and supported. So,

When the input shaft 810 and the inner rotor 220 are integrally rotated in the reverse direction (reverse direction) by the power unit 860 , the latch rotates around the pin 260 by the elastic force of the operation spring 240 . (230) is inserted into the latch engaging groove 221 of the inner rotor 220 is coupled, the outer rotation body 210 is driven in the reverse rotation by the coupling of the inner rotor 220 and the latch 230, The lower gear 811 is rotated in the reverse direction together with the input shaft 810 by the reverse rotational driving of the outer rotor 210 to transmit the reverse driving force of the power unit 860 to the output shaft 840 .

The power unit 860 means a driving means for generating power, such as a motor, an electric motor, and the like, and is shaft-coupled to the input shaft 810 as shown in FIGS. 2 and 7 .

As shown in FIG. 2, one end of the input shaft 810 is shaft-coupled to the power unit 860, and when the input shaft 810 is rotated in the forward direction, a lower gear ( 811 is constrained by a unidirectional bearing 813 , and a high gear 812 spaced apart from the low gear 811 by a predetermined distance and connected to the shift clutch 100 is connected and installed by a bearing 814 .

As shown in FIG. 2 , the lower gear 811 is constrained by a one-way bearing 813 to be integrally rotated with the input shaft 810 when the input shaft 810 is driven in a forward direction (forward driving). That is, the lower gear 811 is rotated in the forward direction integrally with the input shaft 810 by the unidirectional bearing 813, the input shaft 810 is rotated in reverse, or the rotation speed of the lower gear 811 is the input shaft 810. When it becomes faster than the rotational speed of , the unidirectional bearing 813 is connected to the input shaft 810 to be in an idling state with respect to the input shaft 810 .

The unidirectional bearing 813 is a bearing that transmits power in only one direction, and since a known one is used, a detailed description of its configuration will be omitted.

As shown in FIG. 2 , the high gear 812 receives the rotational force of the input shaft 810 through the shift clutch 100 when the input shaft 810 is rotated in the forward direction (forward driving) to receive the input shaft 810. It is rotationally driven integrally with the shift clutch, and is integrally connected to the shift clutch, and the bearing 814 is supported so as to be rotatable with respect to the input shaft 810 .

The reverse clutch 200, as shown in FIGS. 1 to 3, when the input shaft 810 is rotated in the reverse direction (reverse direction), the inner rotor 220 connected to the input shaft and the lower gear 811. The connected outer rotating body 210 is integrally coupled by the latch 230 operated by the elastic force of the actuating spring 240, so that the reverse rotation of the input shaft 810 is transmitted to the lower gear 811. have.

The inner rotor 220 is supported by the outer rotor 210 and the bearing 250 , and is integrally connected to the input shaft 810 so as to be driven concentrically with respect to the input shaft 810 .

As shown in FIG. 4 , the inner rotating body 220 has a plurality of latch locking grooves 221 to which the latches 230 are coupled are formed in a sawtooth phenomenon provided along the outer circumferential surface 220a, and the The latch locking groove 221 has a tapered shape that gradually increases in depth from the outer peripheral surface 220a to the forward rotation A of the input shaft.

That is, the latch engaging groove 221 is formed at the end of the inclined surface 221b, which gradually increases in depth from the outer circumferential surface 220a to the forward rotation A of the input shaft, and the support surface to which the latch is engaged. It is formed so as to include (221a).

In this case, the support surface 221a is preferably formed so that the latch 230 is in surface contact. In addition, the support surface (221a) is preferably configured to be perpendicular to the reverse rotation (A') of the inner rotating body (220).

As shown in FIG. 5, the outer rotating body 210 includes a receiving groove 211 in which the inner rotating body 220 and the bearing 250 are accommodated, and a receiving groove 221 in the inner circumferential surface 211a of the receiving groove. A plurality of latch accommodating grooves 212 communicating with, a pinhole 213 formed on one side of the latch accommodating groove 212 to which the latch is pin-coupled, and a spring formed in the accommodating groove 211 to connect and support an actuating spring hole 214 .

In addition, the outer rotating body 210 has a central hole 215 through which the input shaft 810 is inserted is formed in the receiving groove 211, and the actuating spring 240 is connected and supported in the spring hole 214. A connecting ring 214a is provided.

In addition, bearing holes 222 and 216 for installing the bearing 250 are formed in the inner rotating body 220 and the outer rotating body 210 , and the bearing 250 may be provided with a thrust bearing.

The latch 230 is rotationally driven into the receiving groove 211 around the pin 260 by the elastic force (tensile force) of the actuating spring 240 to be inserted and coupled into the latch engaging groove 221 of the inner rotating body. , the pin 260 is coupled to the pin hole 213 provided in the latch receiving groove 212 of the outer rotating body on one side, and the actuating spring is connected (entangled) and supported on the other side.

The actuating spring 240 is installed between the inner rotating body 220 and the outer rotating body 210, that is, installed in the receiving groove 211 of the outer rotating body, and one end is connected to the latch 230 ( is supported, and the other end is connected and supported to the outer rotor 210 , and the latch 230 is operated to rotate in the direction of the inner rotor 220 around the pin 260 .

As the actuating spring 240, a tensile spring may be used, and the tensile force of the actuating spring 240 is set in consideration of the centrifugal force that operates the latch. That is, the tensile force of the actuating spring is set so that, when the outer rotating body 210 is rotationally driven below the set backward actuating force, the centrifugal force generated in the latch 230 is smaller than the tensile force of the actuating spring, and the outer rotating body 210 When is rotationally driven in excess of the set backward actuating force, the centrifugal force generated in the latch may be set to be greater than the tensile force of the actuating spring.

For example, when the reverse set operating force is set to the rotational force of the outer rotor 210 at 1,000 rpm, when the outer rotational body 210 is rotationally driven at less than 1,000 rpm, the operation spring 240 is latched by the elastic force of the When the 230 is rotated in the direction of the inner rotator 220 and the outer rotator 210 is rotationally driven at 1,000 rpm or more, the latch 230 is the latch of the outer rotator by the centrifugal force generated in the latch 230 . Rotation of the outer rotating body 210 may be made in the state inserted into the receiving groove 212 .

The setting of the tensile force of the actuating spring 240 can be set irrespective of the forward/reverse rotation of the input shaft, and preferably, the rotational speed of the input shaft at which the shift clutch is operated, that is, the shift set value (first set rotational force to be described later). (S1)) is set to be smaller than

In the reverse clutch 200 configured as described above, when the input shaft is rotated in the forward direction (forward direction, A) by the power unit, the latch 230 is not coupled to the latch engaging groove 221 provided in the inner rotating body. Therefore, the inner rotor 220 is driven integrally with the input shaft 810, but the outer rotor 210 is not rotationally driven.

That is, when the input shaft is rotated in the forward direction (forward direction) by the power unit, the latch engaging groove 221 has the support surface 221a rotates more than the inclined surface 221b with respect to the forward rotation A of the inner rotating body. The rotation of the inner rotating body 220 is made to be located at the front end of the direction.

In this way, when rotation is driven by the forward rotation (A) of the inner rotor, the latch 230 is brought into contact with the outer peripheral surface of the inner rotor 220 by the elastic force (tensile force) of the actuating spring 240, and the latch is caught. When the groove 221 reaches the latch 230 installation site, the pin 260 is rotated to insert the latch 230 into the latch engaging groove 221 .

At this time, one side of the latch 230 inserted into the latch engaging groove 221 comes into contact with the inclined surface 221b of the latch engaging groove 221, and then the inclined surface 221b and the outer peripheral surface 220a by rotation of the inner rotating body. will come into contact with That is, since the latch 230 does not engage and contact the support surface 221a of the latch engaging groove, the outer rotor 210 is not rotationally driven and only the inner rotor 220 is integrally rotated with the input shaft 810 . do.

In addition, in the reverse clutch 200, when the input shaft is rotated in the reverse direction (reverse direction, A`) by the power unit, the latch 230 is coupled to the latch engaging groove 221 provided in the inner rotating body. Therefore, the input shaft 810, the inner rotating body 220 and the outer rotating body 210 are rotationally driven in the reverse direction (reverse direction).

That is, when the input shaft is rotated in the reverse direction (reverse direction) by the power unit, the latch engaging groove 221 has a support surface 221a more inclined than the inclined surface 221b with respect to the reverse rotation A` of the inner rotating body. Rotation of the inner rotating body 220 is made to be located at the rear end.

As such, when rotation is driven by the reverse rotation (A') of the inner rotor, the latch 230 is brought into contact with the outer peripheral surface of the inner rotor 220 by the elastic force (tensile force) of the actuating spring 240, and the latch When the locking groove 221 reaches the latch 230 installation site, the pin 260 is rotated to insert the latch 230 into the latch locking groove 221 .

At this time, one side of the latch 230 inserted into the latch engaging groove 221 comes into contact with the inclined surface 221b of the latch engaging groove 221 as shown in FIG. `), the latch 230 and the latch engaging groove 221 are engaged with the support surface 221a, and thus the latch 230 is engaged with the support surface 221a of the latch engaging groove. Therefore, the inner rotating body 220 and the outer rotating body 210 are reversely rotated (A`) by the latch 230 , and the lower gear 811 is the input shaft 810 by the reverse rotation of the outer rotating body 210 . ) and the reverse rotation (A`) is made.

The shift clutch 100 transmits the forward high-speed rotation of the input shaft 810 to the high gear 812 so that the high-speed rotation of the output shaft 840 is achieved, and an electronically controlled clutch or a centrifugal clutch may be installed.

As the shift clutch 100, a known electromagnetic clutch or centrifugal force clutch applied to a transmission device may be used. Preferably, after shifting from a low stage to a high stage, even if the rotational force is reduced, the shift state is up to a certain rotational force. It is preferable that a centrifugal clutch that can be maintained is applied.

For example, the shift clutch 100 includes, as shown in FIGS. 15 to 19 , a clutch first rotor 110 installed to rotate integrally with the input shaft 810 ; a centrifugal rocker unit 190 connected to the clutch first rotor 110 and operated by centrifugal force; It may be configured to include; a clutch second rotor 120 integrally connected to the high gear 812 and installed.

10 is an exemplary view showing the configuration of a shift clutch according to the present invention, FIG. 11 is an exemplary view showing an exploded configuration of a shift clutch having a torsion spring type centrifugal rocker part according to the present invention, and FIG. An exemplary view showing the configuration of a torsion spring type centrifugal rocker unit, FIG. 13 is an exemplary view showing a non-operational state of a torsion spring type centrifugal rocker unit according to the present invention, and FIG. 14 is an operational state of a torsion spring type centrifugal rocker unit according to the present invention 15 is another exemplary view showing the operating state of the torsion spring type centrifugal rocker unit according to the present invention, and FIG. 16 is an exploded configuration of a shift clutch having a coil spring type centrifugal rocker unit according to the present invention 17 is an exemplary view showing the configuration of the coil spring type centrifugal rocker unit according to the present invention, FIG. 18 is an exemplary view showing the non-operational state of the coil spring type centrifugal rocker unit according to the present invention, and FIG. 20 is an exemplary view showing the operation state of the torsion spring type centrifugal rocker part according to the present invention, FIG. 20 is an exemplary view showing the configuration of the clutch first rotor of the shift clutch according to the present invention, and FIG. 22 is an exemplary view showing the configuration of the clutch second rotor, FIG. 22 is an exemplary view showing the configuration of a centrifugal rocker unit having a power transmission buffer (spring-type buffer) according to the present invention, FIG. 23 is a power transmission buffer of the present invention An exemplary view showing the operating state by the part (spring-type buffer), Figure 24 is another exemplary view showing the operating state by the present invention power transmission buffer (spring-type buffer), Figure 25 is in the present invention 26 is an exemplary view showing the configuration of a centrifugal rocker unit having a power transmission buffer unit (friction pad type buffer unit) according to the present invention, and FIG. 27 is an exemplary view showing the configuration of the back plate and the rotating body of the power transmission buffer (friction pad type buffer) according to the present invention, FIG. 28 is a power transmission buffer according to the present invention 29 is an exemplary view showing the configuration of the pad part of the part (friction pad type buffer part), FIG. is an exemplary view showing the operation of the pad portion and the pressing member of the power transmission buffer (friction pad type buffer) according to the present invention, Figure 30 is the pressurization of the power transmission buffer (friction pad type buffer) according to the present invention An exemplary view showing the member configuration is shown.

The centrifugal rocker unit is installed in the first installation hole of the clutch first rotor, and when the rotational force of the first clutch rotor is greater than or equal to the first set rotational force S1, the centrifugal force is rotated so that the rocker is coupled to the clutch second rotor. rocker part;

a support rocker part installed in a second installation hole formed in communication with the first installation hole of the first clutch rotor, the support rocker being rotated by centrifugal force when the rotational force of the clutch first rotor is equal to or greater than the second set rotational force S2; including,

The first set rotational force (S1) is set to be greater than the second set rotational force (S2),

When the rotational force of the clutch first rotor is equal to or greater than the first set rotational force S1, the rotational force of the first clutch rotor is transmitted to the upper gear through the second rotor of the clutch by the rocker, and the shift from the lower stage to the higher stage is performed. ,

When the rotational force of the first rotor of the clutch is greater than or equal to the second set rotational force S2 and less than the first set rotational force S1, the position of the locker is supported by the support locker, and the rotational force of the clutch first rotor is transferred through the second rotor of the clutch. The high shifting state transmitted to the high gear is maintained.

When the rotational force of the first clutch rotor is lowered to less than the second set rotational force S2, the locker and the support locker are respectively inserted into the first and second installation holes of the first clutch rotor in the clutch second rotor to which the high gear is connected. The rocker part is separated (spaced apart) so that the shift from the high stage to the low stage is made.

At this time, the first set rotational force S1 is an arbitrary rotational force (number of revolutions) of the clutch first rotor set so that the rocker of the rocker part is rotated by centrifugal force, and the second set rotational force S2 is the support rocker of the support rocker part. denotes an arbitrary rotational force (number of rotations) of the clutch first rotor set to rotate in the direction of the rocker.

That is, the first set rotational force S1 corresponds to the rotational force of the clutch first rotor at the shift point for transmitting the rotational force of the input shaft to the output shaft, that is, for shifting from the low stage to the high stage, and the second setting The rotational force S2 may correspond to the rotational force of the clutch first rotor at the time when the shift is released, that is, the shift from the high stage to the low stage.

In addition, the second set rotational force (S2) is smaller than the first set rotational force (S1), it is preferable to be set to have 1/5 or more of the first set rotational force (S1).

For example, when the first set rotational force S1 is set to 3,000 rpm, when the rotational force of the clutch first rotor is 3,000 rpm or more, a shift (power transmission) from a low stage to a high stage is performed, and the second When the set rotational force S2 is set to 1,000 rpm, the high-speed shifting state is maintained until the rotational force of the clutch first rotor reaches 1,000 rpm or more, and when the rotational force of the clutch second rotor decreases to less than 1,000 rpm, Shifting from high to low is performed.

That is, the centrifugal rocker unit 190 of the present invention includes the locker units 130 and 170 that are operated when the rotational force of the clutch first rotor 110 is greater than or equal to the first set rotational force S1, and the clutch first rotor 110 . ) to include the support rocker parts 140 and 180 that support so that the operating state of the rocker parts 130 and 170 is maintained when the rotational force of the second set rotational force S2 or more is provided, so that the rotational force of the clutch first rotor is set to the first setting When the rotational force (S1) falls below the rotational force (S1), shift release (shift from high to low) does not occur immediately, but the position of the rocker is supported by the support locker up to the second set rotational force (S2) or more, so the high-speed shifting state is maintained, When the rotational force of the clutch first rotor falls below the second set rotational force S2, the support of the rocker by the support locker is released, so that the shift (disengagement) from the high stage to the low stage is performed.

As described above, the present invention is configured so that precise shift control (setting control to the number of rotations required by the user) is performed by binary setting of the first and second set rotational forces S1 and S2.

In the shift clutch 100 according to the present invention, the centrifugal rocker part 190 is torsion operated by the centrifugal force and the elastic force (torsion force) of the torsion spring as shown in FIG. A spring-type centrifugal rocker part 190a and, as shown in FIG. .

The torsion spring type centrifugal rocker part 190a includes a rocker part 170 and a support rocker part 180, as shown in FIGS.

One side of the locker unit 170 is pin-coupled in the first installation hole 113 of the clutch first rotor 110 and rotationally moves around the pin 173 by centrifugal force so that the engaging surface 171a is made of the clutch. A torsion unit such that the locker 171 supported in contact with the second rotor 120 and the moving end 172a are connected and supported on the other side of the rocker 171 and the fixed end 172b is connected to and supported by the clutch first rotor 110 . (172c) includes a torsion spring 172 is supported connected to the pin 173,

The support locker unit 180 has one end coupled to a pin 183 in the second installation hole 114 of the clutch first rotor 110, and is rotated around the pin 183 by centrifugal force to be mounted on the rocker 171. The support locker 181 to which the first support 181a is in contact, and the moving end 182a are connected and supported to the second support 181b of the support locker 181 , and the fixed end 182b is connected to the clutch first rotor 110 . ) may be configured to include a support torsion spring 182 connected to the supported torsion part 182c to the pin 183 so that the connection is supported.

The support locker 181 is composed of a first support 181a on which the rocker 171 is contacted and supported, and a second support 181b on which the moving end 181a of the support torsion spring 182 is connected and supported, As shown in FIGS. 14 and 15 , the first support 181a is rotated about the pin 183 by centrifugal force and is supported by a stopper 114a provided in the second installation hole in contact with the rocker. When the 171 is in contact, as shown in FIG. 15 , a force F is generated in the radial direction with respect to the rotation radius R of the first support 181a and is integrally formed with the second support 181b. has been

In addition, a support protrusion 171b to which the first support 181a of the support locker is contacted and supported may be formed on the rocker 171 , and the support protrusion 171b and the first support 181a are in point contact (points). contact) or is configured to be in surface contact in the tangential direction of the support locker rotation radius R, and is preferably configured to be in point contact.

In addition, the elastic force (torsion force) of the torsion spring 172 is set in consideration of the first set rotational force S1 and the centrifugal force at which the rocker 171 operates, and the elastic force (torsion force) of the supporting torsion spring 182 . may be set in consideration of the second set rotational force S2 and the centrifugal force at which the operation of the support rocker 181 is made. That is, the first and second set rotational forces S1 and S2 may be adjusted by adjusting the elastic force (torsion force) of the torsion spring 172 and the supporting torsion spring 182 .

As an example, the elastic force (torsion force) of the torsion spring 172 is generated in the rocker 171 when the input shaft 810 and the clutch first rotor 110 are rotationally driven less than the first set rotational force S1. When the centrifugal force is set to be smaller than the elastic force (torsional force) of the torsion spring, and the input shaft and the clutch first rotor are rotationally driven by more than the first set rotational force (S1), the centrifugal force generated in the rocker 171 is generated by the torsion spring ( 172) may be set to be greater than the elastic force (torsion force).

When the elastic force (torsion force) of the torsion spring 172 is set in this way, the centrifugal force generated in the rocker 171 according to the rotation of the clutch first rotor is smaller than the elastic force (torsion force) of the torsion spring 172, the torsion The rocker 171 is located in the first installation hole 113 by the elastic force (torsional force) of the spring, so that the rotational force of the clutch first rotor is not transmitted to the higher gear through the second rotor of the clutch, and the clutch first rotor rotates. When the centrifugal force generated in the rocker 171 according to the 171), the rotational force of the first rotor of the clutch is transmitted to the high gear 812 through the second rotor of the clutch.

In addition, the elastic force (torsion force) of the support torsion spring 182 is applied to the support locker 181 when the input shaft 810 and the clutch first rotor 110 are rotationally driven with less than the second set rotational force S2. When the generated centrifugal force is set to be smaller than the elastic force (torsion force) of the support torsion spring 182, and the input shaft and the clutch first rotor are rotationally driven by more than the second set rotational force S2, generated in the support locker 181 The centrifugal force used may be set to be greater than the elastic force (torsion force) of the support torsion spring 182 .

In this way, when the elastic force (torsion force) of the support torsion spring 182 is set, the centrifugal force generated in the support rocker 181 according to the rotation of the clutch first rotor is greater than the elastic force (torsion force) of the support torsion spring 182 . If it is small, the support rocker 181 is located in the second installation hole 114 by the elastic force (torsion force) of the support torsion spring, so that the rocker 171 is not contacted by the support locker 181, and the clutch release 1 When the centrifugal force generated in the support rocker 181 according to the rotation of the rotor is greater than the elastic force (torsion force) of the support torsion spring 182, the support torsion spring 182 is relaxed and the rotational movement of the support rocker 181 is will be done

In addition, the first and second set rotational forces S1 and S2 are elastic force (torsion force) of the torsion spring 172 and the support torsion spring 182, in addition to the rotational force of the clutch first rotor, the weight of the rocker and the support locker And, considering the rotation radius of the clutch first rotor, the locker and the support locker, the clutch operation time (shift time), etc., the set value required for the user or the target application is calculated and set by the known technology. Detailed description will be omitted.

The torsion spring type centrifugal rocker part 190a configured as described above,

When the clutch first rotor 110 is rotationally driven by the input shaft 810 at a first set rotational force S1 or more, as shown in FIG. 14 , by centrifugal force according to the rotation of the clutch first rotor 110 , The rocker 171 of the rocker unit 170 is rotated around the pin 173, and is caught in contact with one side of the clutch second rotor 120, so that the rotational force of the clutch first rotor 110 is applied to the clutch second rotor ( 120) and has a function to operate the high gear 812 (shift from low to high).

In addition, even if the rotational force of the clutch first rotor 110 is lowered to less than the first set rotational force S1 after the shift, as shown in FIG. 15 , the support rocker unit 180 is up to the second set rotational force S2 or more. Since the rocker part 170 is supported by the It has a function to be transmitted to the clutch second rotor 120 by the

That is, the torsion spring type centrifugal rocker part (190a) is,

When the clutch first rotor 110 is rotationally driven by the input shaft 810 at a predetermined first set rotational force S1 or more, the rocker 171 of the rocker unit 170 rotates the torsion spring 172 by centrifugal force. While overcoming the elastic force and rotationally moving around the pin 173, the other side of the locker is inserted into the locking groove 150 provided in the clutch second rotor 120, and the locking surface 171a of the locker is moved to the clutch second rotor. It is contacted (coupled) to the contact surface 151 of 120 and transmits the rotational force of the clutch first rotor 110 to the high gear 812 by the clutch second rotor 120 (shift from low to high) will do

In addition, since the first set rotational force S1 is set to be greater than the second set rotational force S2, the clutch first rotor 110 rotates by the input shaft 810 at an arbitrary first set rotational force S1 or more. When driven, the support rocker 181 of the support locker part also overcomes the elastic force of the support torsion spring 182 by centrifugal force and is rotated in the direction of the rocker 171 around the pin 183 . At this time, as shown in FIG. 14 , the first support 181a of the support locker is spaced apart from the support protrusion 171b of the locker by a predetermined distance and is positioned with a gap G2.

In addition, after the shift from the low stage to the high stage, when the rotational force of the clutch first rotor is reduced and is lower than the first set rotational force S1 and the second set rotational force S2 or more, the rocker of the rocker unit 170 ( 171) is rotated so as to be moved into the first installation hole 113 of the first clutch rotor by the elastic force (torsion force) of the torsion spring 172, but the support locker 181 of the support locker part is operated by centrifugal force 15, the support protrusion 171b of the rocker is supported in contact with the first support 181a of the support locker according to the rotational movement of the rocker, and the rocker 171 is connected to the first installation hole ( 113) direction is prevented, and for this reason, the operating state of the rocker unit 170 is maintained, and the rotational force of the clutch first rotor 110 is transferred to the clutch second rotor 120 by the rocker 171 . It will continue to be transmitted (shifted). At this time, since the direction of the force F according to the contact between the support protrusion 171b of the rocker and the first support 181a of the support locker is made in the radial direction, the rocker 171 is stable by the support locker 181 will be supported by

In addition, when the rotational force of the clutch first rotor 110 is reduced to less than the second set rotational force S2, the support rocker 181 by the elastic force (torsion force) of the support torsion spring 182 of the clutch first rotor Since it is rotated to move into the second installation hole 114 and the contact support between the rocker 171 and the support locker 181 is released, the rocker 171 is also clutched by the tine force (torsion force) of the torsion spring 172 . By rotationally moving into the first installation hole 113 of the first rotor, the coupling between the clutch first rotor 110 and the clutch second rotor 120 is released, so that the shift from the high stage to the low stage is performed.

At this time, since the support protrusion 171b of the rocker and the first support 181a of the support locker are in surface contact with the point contact or in the tangential direction of the support locker rotation radius R, the rotational force of the clutch first rotor is the second When the set rotational force (S2) is lowered below the set rotational force (S2), the support locker 181 is rotated around the pin 183 by the elastic force (torsion force) of the support torsion spring 182, and the second installation hole 114 of the clutch first rotor. ) to move easily.

In addition, the coil spring type centrifugal clutch 190b includes a rocker part 130 and a support rocker part 140 as shown in (b) of FIG. 10 and FIGS. 16 to 19 ,

One side of the locker part 130 is pin-coupled in the first installation hole 113 of the clutch first rotor 110, and rotationally moves around the pin 133 by centrifugal force, so that the engaging surface 131a is made of the clutch. 2 It includes a rocker 131 supported in contact with the rotor 120, and a rocker spring 132 having one end connected and supported to the other side of the rocker 131 and the other end connected and supported to the clutch first rotor 110, and ,

The support rocker unit 140 includes a ball spring 142 inserted and installed into a second installation hole 114 formed to communicate with one side of the first installation hole 113 having a pinhole 115, and a ball spring 142 ) may be configured to include a support ball 141 that is supported in contact with one side of the rocker 131 by being elastically supported so that a part protrudes into the first installation hole 113 by the elastic force of the .

As shown in FIG. 17 , one end of the locker 131 is coupled with a pin 133 to a pinhole 115 provided in the first installation hole 113 of the first clutch rotor, and the second rotor 120 of the clutch ) is provided on the other side, and the other side provided with the engaging surface 131a is connected to and supported by the rocker spring 132 . In addition, the locker 131 is provided with a support groove 131b in which the support ball 141 of the support locker part is inserted and supported on one side to which the pin is coupled.

As shown in FIGS. 18 and 19, the rocker spring 132 is connected to the rocker 131 and the first clutch rotor 110, and the rocker 131 is connected to the first clutch by elastic force (tensile force). The rocker 131 is elastically supported so as to be located in the first installation hole 113 of the rotor. That is, one end of the rocker spring 132 is connected to and supported by the rocker 131 and the other end of the first installation hole 113 communicates with the first installation hole 113 of the clutch first rotor 110 . It is installed to be connected in the spring hole 116 formed on the other side, and has a function of pulling the other side of the locker 131 provided with the locking surface 131a in the direction of the spring hole 116 .

In addition, the ball spring 142 is provided with a predetermined elastic force (compression force) so that the support ball 141 is pressed into contact with one side of the rocker 131, and is inserted and installed in the second installation hole 114.

For example, a tension coil spring may be used for the rocker spring 132 , and a compression coil spring may be used for the ball spring 142 .

The elastic force (tensile force) of the rocker spring 132 is set in consideration of the first set rotational force S1 and the centrifugal force at which the rocker 131 operates, and the elastic force (compressive force) of the ball spring 142 is set to the second setting. It may be set in consideration of the rotational force S2 and the frictional support force by the support ball 141 . That is, the first and second set rotational forces S1 and S2 may be adjusted by adjusting the elastic force of the rocker spring 132 and the ball spring 142 .

For example, the elastic force (tensile force) of the rocker spring 132 is such that, when the input shaft and the clutch first rotor are rotationally driven less than the first set rotational force S1, the centrifugal force generated in the rocker is smaller than the tensile force of the rocker spring. is set, and when the input shaft and the clutch first rotor are rotationally driven by the first set rotational force S1 or more, the centrifugal force generated in the rocker may be set to be greater than the tensile force of the rocker spring.

In this way, when the elastic force of the rocker spring 132 is set, when the centrifugal force generated in the rocker 131 is smaller than the tensile force of the rocker spring 132, the length of the rocker spring 132 does not change, so the first insertion of the insertion hole The rocker 131 is positioned in the hole 113', so that the rotational force of the clutch first rotor is not transmitted to the clutch second rotor.

In addition, when the centrifugal force generated in the rocker 131 is greater than the tensile force of the rocker spring 132 , a tensile load is generated in the rocker spring 132 to increase the length of the rocker spring 132 and rotate the rocker 131 . This is achieved, when the locker is in contact with the second rotor of the clutch, the rotational force of the first rotor of the clutch is transmitted to the second rotor of the clutch by the rocker.

In addition, the elastic force of the ball spring 142 is, when the input shaft 810 and the clutch first rotor 110 are rotationally driven with less than the second set rotational force S2, the rocker 131 by the elastic force of the rocker spring 132. ) is rotationally moved into the first installation hole 113, and when the input shaft and the clutch first rotor are rotationally driven by more than the second set rotational force S2, the position of the rocker is caused by the friction support force by the support ball and the centrifugal force of the rocker. may be set to be supported.

In addition, the first and second set rotational forces S1 and S2 are adjusted by the elastic force adjustment setting of the rocker spring 132 and the ball spring 142 .

That is, in the coil spring type centrifugal clutch 190b, the first and second set rotational forces S1 and S2 are, in addition to the elastic forces of the rocker spring 132 and the ball spring 142, the rotational force of the clutch first rotor, and support with the rocker. Considering the weight of the ball, the rotation radius of the clutch first rotor and rocker, the clutch operation time (shift time), etc., the set value required by the user or the target application is calculated and set by known technology, Detailed description will be omitted.

As described above, the centrifugal rocker unit 190 comprising the torsion spring type centrifugal rocker unit 190a or the coil spring type centrifugal rocker unit 190b,

While the clutch first rotor 110 and the clutch second rotor 120 are integrally rotationally driven (shifted) by the centrifugal rocker unit 190, the rotational force of the clutch first rotor 110 is the first set rotational force S1. ) or a phenomenon in which the rotational force of the second clutch rotor 120 connected to the high gear 812 is greater than the rotational force of the clutch first rotor 110 connected to the input shaft 810 (downhill driving or generation of regenerative braking force, etc.) ) is generated, the centrifugal rocker part 190 is separated from the clutch second rotor 120 at the second set rotational force S2 or more, that is, the clutch first rotor 110 and the clutch second rotor 120 . A sudden loosening phenomenon (shift release phenomenon) is prevented.

In addition, the centrifugal rocker unit 190 configured and operated as described above transmits the forward rotational force of the clutch first rotor 110 to the clutch second rotor 120 to achieve a speed change. made of, or

A forward centrifugal rocker part 190c for transferring the forward rotational force of the clutch first rotor 110 to the clutch second rotor 120 to achieve a speed change, the clutch first rotor 110 and the clutch second rotor 120 It may be made of a reverse centrifugal rocker part 190d to prevent a change in the relative speed of the .

That is, the forward centrifugal rocker unit 190c has a shift function that allows the clutch first rotor 110 and the clutch second rotor 120 to rotate integrally, and the reverse centrifugal rocker unit 190d is provided with a regenerative braking force, etc. When a difference occurs between the rotational speeds of the clutch first rotor 110 and the clutch second rotor 120 by the 110) so that the clutch first and second rotors 110 and 120 are integrally rotated.

At this time, the forward rocker part 190c and the reverse rocker part 190d have the same configuration and are operated at the same rotational force (rpm), and the clutch first and second rotors 110 and 120 are operated by the forward rocker part 190c. When integrally rotated, as shown in FIGS. 14 and 19 , the locker of the rotationally operated reverse rocker part 190d is spaced apart from the clutch second rotor 120 by a predetermined distance with respect to the rotational direction to form a gap G1. It is located so as to be provided, or is in contact with the locking groove provided in the clutch second rotor 120 , and is preferably positioned to be spaced apart by a predetermined distance.

As shown in FIGS. 11, 16, and 20, the clutch first rotor 110 has a shaft hole 111 to which the input shaft 810 is connected, and the shaft hole 111 from the outer circumferential surface 110a. It includes a plurality of installation holes 112 to which the rocker unit 190 is connected and installed.

The shaft hole 111 has a concentric circle with respect to the input shaft 810 so that the clutch first rotor 110 is integrally rotated, that is, the input shaft 810 and the clutch first rotor 110 are spline-coupled or keyed. It is formed so that /keyway coupling or concave-convex coupling is made.

The installation hole 112 is formed in communication with the first installation hole 113 to which the locker parts 130 and 170 are rotatably pin-coupled, and the first installation hole 113, and the support locker parts 140 and 180 are installed. It includes an installation hole 114 .

In addition, the installation hole 112 is formed so that the first installation hole 113 and the second installation hole 114 have one hole as shown in (a) of FIG. 20, or ( As shown in b), the second installation hole 114 may be formed in communication with one side of the first installation hole 113 . (The virtual line in FIG. 20 is for explaining the first and second installation holes, and is not actually configured.)

In addition, when the centrifugal rocker part 190 of the clutch first rotor 110 is formed of a coil spring type centrifugal rocker part 190b, as shown in (b) of FIG. 20, the first installation hole 113 A spring hole 116 in which the rocker spring is installed is further formed in communication with the .

In addition, the installation hole 112 provided in the clutch first rotor 110 is a type of the centrifugal rocker part 190 connected and installed to the clutch first rotor, that is, a torsion spring type centrifugal rocker part 190a or a coil spring type. According to the centrifugal rocker portion 190b, there are differences in the shapes of the first and second installation holes 113 and 114, but such differences do not depart from the gist of the present invention, and thus correspond to various modified implementations of the present invention.

As shown in Figs. 11, 16 and 21, the clutch second rotor 120 includes a flange 121 having an accommodation hole 123 in which the clutch first rotor 110 is accommodated, and the flange ( It is formed on one side of the 121 and is connected to the high gear 812 and includes a hub 122 having a shaft hole 124 in which an input shaft 810 is inserted and supported by a bearing.

In addition, a locking groove 150 through which the lockers 131 and 171 of the locker parts 130 and 170 are engaged may be formed on the inner surface of the receiving hole 123 in the flange 121 .

The locking groove 150 has the inner surface 120a of the clutch second rotor so that the lockers 131 and 171 that are rotated by centrifugal force can be easily inserted and no impact noise is generated due to contact with the clutch second rotor 120 . ) in the direction of rotation (A, A`), the inclined surface 152 gradually deepens in depth, and the locking surfaces 131a and 171a of the rocker at the end of the inclined surface 152, the locking contact surface 151 which is supported by locking contact. It consists of a tapered shape provided.

At this time, the engaging contact surface 151 is preferably formed to be in surface contact with the engaging surfaces 131a and 171a of the locker, and the engaging groove 150 corresponds to the lockers 131 and 171 on the inner surface of the clutch second rotor ( At least one is formed in 120a).

In addition, when the centrifugal rocker part 190 is provided with the forward centrifugal rocker part 190c and the reverse centrifugal rocker part 190d, the installation hole 112 and the locking groove 150 are formed with the forward centrifugal rocker part 190a and To match the operation of the reverse centrifugal rocker part 190b, that is, the installation holes in which the forward centrifugal rocker part 190a and the reverse centrifugal rocker part 190b are respectively installed are formed to be symmetrical to each other in the clutch first rotor, In the second rotor, the locking grooves 150 in which the forward centrifugal rocker part 190c and the reverse centrifugal rocker part 190d are latched are formed to be mutually symmetrical, respectively.

In addition, as shown in FIGS. 22 to 26 , the present invention is installed between the centrifugal rocker part 190 and the clutch second rotor 120 and acts in the rotational direction by engaging contact with the centrifugal rocker part 190 . It may be configured to further include a; power transmission buffer unit 300 for transmitting the rotational force of the clutch first rotor 110 to the clutch second rotor 120 while buffering shock and vibration.

The power transmission buffer 300 may include a spring-type buffer 310 and a friction pad-type buffer 320 .

As shown in FIGS. 22 to 24 , the spring-type shock absorber 310 has a clearance with the clutch first rotor 110 and the clutch second rotor 120 , and includes the clutch first rotor 110 and the clutch. The rotation plate 311 accommodated between the second rotor 120 and the rotation plate 311 and the clutch second rotor 120 are accommodated, both ends of the rotation plate 311 and the clutch second rotor 120 . This elastically supported, can be configured to include a buffer spring 312 that is operated in the circumferential direction.

At this time, the rotation plate 311 is formed with a locking groove 150 to which the centrifugal rocker part 190 is engaged, and the clutch second rotor 120 has a support protrusion 125 for elastically supporting the buffer spring 312 . is formed

That is, when the spring-type shock absorber 310 is further installed between the clutch first rotor 110 and the clutch second rotor 120, the locking groove 150 to which the centrifugal rocker part 190 engages is formed by the clutch. It is formed on the rotation plate 311 of the spring-type buffer part 310 that can contact the rockers 131 and 171 rather than the second rotor 120 , and the rotation force of the first rotor of the clutch is applied to the second rotor 120 of the clutch. A support protrusion 125 for supporting the buffer spring 312 to transmit is formed.

As shown in FIG. 22, the rotation plate 311 is formed in a ring type, the clutch first rotor 110 is positioned with a play on the inside, and the clutch second rotor 120 has play on the outside. is provided and is installed between the clutch first rotor 110 and the clutch second rotor 120 so as to be operated concentrically with the first and second rotors 110 and 120 of the clutch. That is, the rotation plate 311 has a radial play with the clutch first rotor 110 in which the centrifugal rocker part 190 is installed, and is installed to surround it in a concentric circle shape.

The rotation plate 311 has a locking groove 150 in which the lockers 131 and 171 of the centrifugal rocker part operated by centrifugal force are inserted into the locking contact with the inner surface 311a of the rotation plate to a predetermined depth, and a buffer spring ( An outer protrusion 313 on which one side of the 312 is supported is formed to protrude from the outer surface 151b.

The locking groove 150 has an inclined surface 152 that gradually increases in depth in the rotational directions (A, A`), and the locking surfaces 131a and 171a of the rocker at the ends of the inclined surface 152 are in contact with and supported. It has a tapered shape provided with the engaging contact surface 151, and the configuration of the engaging groove 150 is described above, so a detailed description will be omitted.

The outer protrusion 313 has a function of supporting the buffer spring 312 accommodated between the rotation plate 311 and the clutch second rotor 120 to be operated in the circumferential direction, and the clutch by the elastic force of the buffer spring 312 . It is supported in contact with one side of the second rotor and has a function of supporting the position of the rotating plate.

In addition, the outer protrusion 313 has a function of allowing the rotation plate 311 to rotate concentrically within the clutch second rotor 120 . That is, the outer protrusion 313 is formed to protrude from the outer surface 311b of the rotation plate so as to be assembled with an assembly tolerance with respect to the inner surface 120a of the second rotor of the clutch, and the rotation plate 311 and the second rotor of the clutch. (120) has a function of concentrically actuated.

In addition, at least one of the outer protrusions 313 is formed to protrude to correspond to the installed number of the buffer springs 312 .

The buffer spring 312 is a clutch second rotor ( 120) has a function to transmit.

As shown in FIGS. 23 and 24, one side of the buffer spring 312 is supported in contact with the outer protrusion 313 of the rotation plate 311, and the other side is supported on the support protrusion 125 of the second rotor of the clutch. One or more, preferably two or more, a plurality of buffer springs are installed to be symmetrical with each other so as to be supported in contact.

The spring-type buffer unit 310 configured as described above, as shown in FIGS. 23 and 24 , the lockers 131 and 171 of the centrifugal rocker unit are rotationally moved by centrifugal force to provide a locking groove 150 provided in the rotating plate 311 . ), when the clutch first rotor 110 and the rotating plate 311 are rotated integrally with the engaging contact surface 151 of the 120), the rotation of the clutch first and second rotors 110 and 120, ie, shift (shift from low to high), is made while shock and vibration acting in the rotational direction are buffered.

In addition, according to the present invention, when the spring-type shock absorber 310 is further installed, as shown in FIG. 22 , the clutch second rotor 120 , that is, the flange 121, has the clutch product inserted into the receiving hole 123 . 1 The cover 160 for preventing separation of the rotor 110 and the buffer spring 322 is further fixedly installed.

The friction pad type buffer 320, as shown in FIGS. 24 to 30, a back plate 321 provided with a pad pin 325 on one side and an extension pin 326 on the other side, The rotation body 322 is integrally fixed to the back plate 321 so as to have a play with the clutch first rotor 110 and the lockers 131 and 171 of the centrifugal rocker part are in contact contact with each other, and the pad pin 325 of the back plate. One side is connected and supported and the other side is supported connected to the extension pin 326, and is installed symmetrically on one side surface 321a of the back plate so as to have a clearance with the rotating body 322, and is in contact with the clutch second rotor 120 The pad part 323 and the other side surface 321b of the back plate are installed to be connected to the expansion pin 326 and rotate the expansion pin 326 so that the pad part 323 is in close contact with the clutch second rotor 120 . It may be configured to include an expanding portion 324 that presses.

At this time, the locking groove 150 in which the lockers 131 and 171 of the centrifugal rocker part 190 are engaged are formed in the rotating body 322 .

That is, when the friction pad type shock absorber 320 is further installed between the clutch first rotor 110 and the clutch second rotor 120 , the locking grooves in which the lockers 131 and 171 of the centrifugal rocker part 190 are in contact contact. Reference numeral 150 is not formed in the second rotor 120 of the clutch, but in the rotation body 322 of the friction pad type cushioning unit 320 in which the contact of the rockers 131 and 171 can be made.

As shown in FIG. 27 , the rotating body 322 has a locking groove 150 into which the lockers 131 and 171 of the centrifugal rocker unit operated by centrifugal force are inserted and in contact with the locking groove 150 is formed on the inner surface 322a to a predetermined depth, In addition, the locking groove 150 has an inclined surface 152 that gradually increases in depth in the rotational direction of the rotary body from the inner surface 322a of the rotary body, and locking surfaces 131a and 171a of the locker at the ends of the inclined surface 152 ) is made of a tapered shape provided with a locking contact surface 151 supported by locking contact, and since the configuration of such a locking groove 150 is described above, a detailed description thereof will be omitted.

The rotating body 322 configured as described above has a radial play with the clutch first rotor 110 in which the centrifugal rocker part 190 is installed, and is installed to surround it in a concentric circle shape.

As shown in FIG. 27 , the back plate 321 has a rotating body 322 integrally installed at the center of one side 321a, and a pad pin 325 and an extension pin around the rotating body 322 . (326) is installed to be symmetrical to each other.

The pad pin 325 is formed of a circular pin type, that is, a cylindrical type, so that one side of the pad part 323 is supported in contact and rotated.

In addition, a rotation support groove 325a to which one side of the pad part 323 is connected and supported may be formed in the pad pin 325 to a predetermined depth along the outer circumferential surface to prevent smooth contact rotation and separation of the pad part.

The extension pin 326 is formed of a circular pin type, that is, a cylindrical type, in which contact planes 326a on which the other side of the pad part 323 is supported in contact are formed on both sides.

In addition, the extension pin 326 has a pin head (326a) to protrude from the contact plane 326a to prevent smooth contact rotation of the pad part 323 centering on the pad pin 325 and the separation of the pad part 323. 326b) is formed.

Preferably, the pad part 323 is installed in a pair so as to be symmetrical with respect to the pad pin 325 and the extension pin 326 .

As shown in FIG. 28 , the pad part 323 is provided with a friction pad 323a that is in frictional contact with one side of the clutch second rotor 120 to cushion the rotational shock and vibration according to the shift, and one end of the pad part 323 is installed. A semicircular contact groove 323b is provided in contact with the outer circumferential surface of the pad pin 325 to enable rotation, and a contact surface 323c supported in contact with the contact plane 326a of the extension pin is provided at the other end.

The extension part 324 is installed on the other side surface 321b of the back plate where the rotation body 322 and the pad part 323 are not installed, and the pad part 323, that is, friction, is provided on one side of the clutch second rotor. The pad 323a is always in contact, so that the friction force between the second clutch rotor and the pad part 323 is constantly maintained.

As shown in FIGS. 27 and 30 , the extension part 324 includes a rotation lever 324a integrally connected to the extension pin 326 , one side of which is supported by a back plate 321 , and a rotation lever 324a ) is supported on the other side and includes a pressing member (324b) for rotating the rotary lever (324a) around the expansion pin (326).

The pressing member 324b is installed so that both ends are supported by the support bracket 321c and the rotary lever 324a provided on the back plate 321, and the rotary lever 324a is elastic with respect to the support bracket 321c. In order to operate, that is, the rotary lever 324a is provided with a predetermined elastic force to rotate integrally with the expansion pin 326 .

Also, the pressing member 324b may be a spring or a hydraulic cylinder having a predetermined elastic pressing force.

For example, the pressing member 324b is screwed with a coil spring 324c, a first guide pin 324d fitted to one end of the coil spring 324c, and a first guide pin 324d, An elastic adjustment bolt 324f fixed to the support bracket 321c of the back plate by a fixing nut 324e, and a second guide pin fitted to the other end of the coil spring 324c and supported by the rotation lever 324a (324 g) is configured to contain,

The position of the first guide pin 324d is adjusted by the adjustment of the elastic adjustment bolt 324c and the nut 324e, and the coil spring 324c is pressed and compressed by the position change of the first guide pin 324d, The rotation lever 324a and the extension pin 326 may be configured to rotate by the elastic force of the coil spring 324c.

The friction pad type buffer 320 configured as described above, as shown in FIG. 29, the expansion pin 326 is rotated by the expansion part 324, and the contact plane ( When 326a) presses the contact surface 323c of the pad part, the contact groove 323b of the pad part is rotated in contact along the pad part 323, and the pad part 323 is operated outwardly around the pad pin 325 ( P), and the friction pad 323a of the pad part is in close contact with the inner surface 120a of the clutch second rotor by the outward operation (P) of the pad part 323. That is, the friction pad type shock absorber 320 is pressed into contact with the clutch second rotor 120 to be connected and installed.

At this time, when the pair of pad parts are operated outwardly (P), one end of the symmetrically installed pad part is configured not to contact each other, and the friction pad of the pad part is always on the inner surface of the clutch second rotor by the extension part. A state of close contact is maintained.

As such, in the friction pad type buffer unit 320, when the lockers 131 and 171 of the centrifugal rocker unit are rotationally moved by centrifugal force and contacted with the engaging groove 150 provided in the rotating body, the rotating body 322 and the pad unit 323 is rotated integrally with the clutch first rotor 110 . At this time, since the pad part 323 of the friction pad type shock absorber 320 is press-adhered to the inner surface 120a of the second clutch rotor by the expansion part 324 , the pad part 323 and the clutch second Although a slip phenomenon (sliding of the pad part) occurs between the inner surface 120a of the rotor, the frictional force between the pad part 323 and the inner surface 120a of the second clutch rotor 120 causes the clutch second rotor 120 to be a friction pad type. The buffer unit 320 is integrally rotated, that is, the shift is made. At this time, the shock and vibration acting in the rotational direction are buffered by the slip phenomenon and frictional force between the pad part 323 and the inner surface 120a of the second clutch rotor.

The reduction unit 830 is configured to transmit the rotational driving force of the input shaft to the output shaft by a plurality of reduction gears, and may be configured to perform single-stage deceleration or multi-stage deceleration. In addition, the configuration of the reduction unit 830 is not particularly limited, and may be variously changed according to an application target and needs.

For example, as shown in FIG. 9 , the reduction unit 830 includes a first reduction gear 831 meshed with a low gear 811 of the input shaft, and a second reduction gear meshed with a high gear 812 . It may be formed to include a reduction gear shaft 834 provided with 832 and a third constraint gear 833 for transmitting power to the output shaft 840 .

At this time, since the gear ratio of the reduction unit 830 is made by a known technique, a detailed description thereof will not be provided. For example, both ends of the reduction gear shaft 834 are supported by bearings on the gear housing 820 so as to be parallel to the input shaft 810, and the gear ratio (reduction ratio) of the lower gear 811 and the first reduction gear 831 is , may be formed to be larger than a gear ratio (reduction ratio) of the high gear 812 and the second reduction gear 832 .

In addition, as shown in FIG. 8 , the reduction unit 830 includes a first rotation gear 835 meshed with the low gear 811 and a second rotation gear 836 meshed with the high gear 812 . A rotating shaft 837 provided integrally, and

A first reduction gear shaft 838 provided with a first reduction input gear 838a meshed with the first rotary gear 835 of the rotary shaft;

A second reduction input gear 839a meshed with the first reduction output gear 838b of the reduction gear shaft 838 and a second reduction output gear 839b for transmitting power to the output shaft 840 are provided. It may be formed to have a reduction gear shaft (839).

At this time, since the gear ratio of the reduction unit 830 is made by a known technique, a detailed description thereof will not be provided.

The output shaft 840 is driven by receiving the rotational driving force of the input shaft 810 through the reduction unit 830. As shown in FIGS. 7 to 9 , the output shaft 840 is connected to the reduction unit 830 to be rotated. A gear 841 is provided, and a driving wheel 850 is installed at one end or both ends.

In addition, the output shaft 840 may be configured such that a differential gear unit (not shown) is further installed to control the rotational speed of the driving wheels 850 provided at both ends. As such, the configuration of the output shaft 840 having the differential gear unit is a known configuration, and thus a detailed description thereof will be omitted. In addition, the input shaft 810 , the output shaft 840 , the reduction gear shaft 834 , and the rotation shaft 837 are all bearing-supported in parallel to the gear housing 820 .

The transmission 800 of the present invention configured as described above,

When the input shaft 810 is driven by the power unit 860 to rotate at a low speed with less than the first set rotational force (S1, for example, 1,500 rpm) in the forward direction, the low gear 811 constrained to the input shaft by the unidirectional bearing is used. The driving force of the power unit 860 is transmitted to the output shaft 840 .

At this time, the inner rotation body 220 of the reverse clutch is rotationally driven integrally with the input shaft 810, and the exterior rotation body 210 is rotationally driven integrally with the lower gear 811, so the reverse clutch 200 is the input shaft ( 810) and is rotated in the forward direction.

In addition, when the input shaft 810 is rotated at a high speed above the first set rotational force (S1, for example, 3,000 rpm) in the forward direction by the power unit 860, the shift clutch 100 is operated to move the high gear 812. The driving force of the power unit 860 is transmitted to the output shaft 840 through, and as such, when the driving force of the power unit 860 is transmitted to the output shaft 840 through the high gear 812, the rotational force of the low gear 812 is Since it is faster than the rotational force of the input shaft 810 , the lower gear 812 is in an idling state with respect to the input shaft 810 by the one-way bearing 813 .

In addition, since the outer rotating body of the reverse clutch is rotationally driven by a reverse set operating force (for example, 1,000 rpm) or more, the latch 230 is inserted into the latch receiving groove 212 of the outer rotating body by centrifugal force, so that the outer rotating body and the inner side Rotating bodies are driven to rotate in the forward direction without mutual interference.

In addition, when the input shaft 810 is rotated in the reverse direction by the power unit 860 at a low speed less than the reverse set operating force (for example, 1,000 rpm), the latch is operated by the operation spring and the inner rotor and the lower gear connected to the input shaft Since the outer rotating body connected to the is integrally coupled and rotationally driven in the reverse direction, the lower gear constrained by the one-way bearing on the input shaft is rotationally driven in the reverse direction to transmit the reverse vibration force to the output shaft.

In addition, when the rotational force of the clutch first rotor by the input shaft is less than the second set rotational force (S2, for example, 2,000rpm) in the forward direction, the centrifugal rocker unit or the centrifugal rocker unit is returned to its original position (non-operational state) and the clutch first rotor and the clutch second rotor are separated (separated), so that the shift from the high stage to the low stage is made,

When the input shaft 810 by the power unit 860 in the forward direction is less than the first set rotational force (S1, for example, 3,000 rpm) and the second set rotational force (S2, for example, 2,000rpm) or more, the operation of the shift clutch 100 The state is maintained, and the driving force of the power unit 860 is transmitted to the output shaft 840 through the high gear 812 .

The present invention is not limited to the specific preferred embodiments described above, and various modifications can be made by anyone with ordinary skill in the art to which the invention pertains without departing from the gist of the invention as claimed in the claims. Of course, such modifications are intended to be within the scope of the claims.

In addition, the terms described in the present invention are for distinguishing one component from other components and helping the understanding of the present invention, so the components of the present invention are not limited by the described terms.

(100): shift clutch (110): clutch first rotor
(110a): outer peripheral surface (111): shaft hole
(112): installation hole (113): first installation hole
(114): second installation hole (115): pinhole
(116): spring hole (120): clutch second rotor
(120a): inner surface (121): flange
(122): Hub (123): Receiving hole
(124): shaft hole (125): support protrusion
(130): rocker part (131): locker
(131a): locking surface (131b): support groove
(132): rocker spring (133): pin
(140): support rocker unit (141): support ball
(142): Ball spring (150): Locking groove
(151): locking contact surface (152): inclined surface
(160): cover (170): rocker unit
(171): locker (171a): locking surface
(171b): support surface (172): torsion spring
(172a): mobile end (172b): fixed end
(172c): torsion part (173): pin
(180): support locker part (181): support locker
(181a): the other end (182): support torsion spring
(182a): mobile end (182b): fixed end
(182c): torsion part (183): pin
(190): centrifugal rocker part (190a): torsion spring type
(190b): Coil spring type (190c): Forward coil spring type
(190d): Reverse coil spring type
(200): reverse clutch (210): outer rotating body
(211): receiving groove (211a): inner outer peripheral surface
(212): Latch receiving groove (213): Pinhole
(214): spring hole (215): central hole
(216): bearing hole (220): inner rotating body
(221): latch locking groove (221a): support surface
(221b): inclined surface (222): bearing hole
(230): latch (240): actuation spring
(250): Bearing (260): Pin
(300): power transmission buffer
(310): spring type buffer (311): rotating plate
(311a): Inner (311b): Outer
(312): buffer spring (313): outer projection
(320): friction pad type cushioning part (321): back plate
(321a): one side (321b): the other side
(321c): support bracket (322): rotating body
(322a): inner surface (323): pad portion
(323a): friction pad (323b): contact groove
(323c): contact surface (324): extension
(324a): rotary lever (324b): pressing member
(324c): coil spring (324d): first guide pin
(324e): Fixing nut (324f): Elastic adjustment bolt
(324g): second guide pin (325): pad pin
(325a): rotation support groove (326): expansion pin
(326a): contact plane (326b): pin head
(800): transmission (810): input shaft
(811): low gear (812): high gear
(813): one-way bearing (814): bearing
(820): gear housing (830): reduction part
(831): first reduction gear (832): second reduction gear
(833): 3rd reduction gear (834): reduction gear shaft
(835): first rotation gear (836): second rotation gear
(837): rotation shaft (838): first reduction gear shaft
(838a): first reduction input gear (838b): first reduction output gear
(839): second reduction gear shaft (839a): second reduction input gear
(839b): second reduction output gear (840): output shaft
(841): output gear (850): drive wheel
(860): power unit

Claims (13)

The rotational driving force of the input shaft 810 axially connected to the power unit 860 is transmitted to the output shaft 840 through the lower gear 811 constrained to the input shaft 810 by the unidirectional bearing 813 or transmitted to the input shaft 810. In the transmission device (800) supported by a bearing and transmitted to the output shaft (840) through a high gear (812) connected to the shift clutch (100);
A reverse clutch 200 is connected and installed to the input shaft 810 and the lower gear 811,
The reverse clutch 200,
A plurality of latch receiving grooves ( 212) and an outer rotating body 210 provided with,
The inner rotor is provided with a play in the receiving groove 211 of the outer rotating body so as to be driven integrally with the input shaft 810, the bearing 250 is supported, and the inner rotating body is provided with a plurality of latch engaging grooves 221 on the outer circumferential surface 220a. (220) and;
a latch 230 having one side coupled to a pin 260 in the latch receiving groove 212 of the outer rotating body;
The other side of the latch 230 is provided with an elastic force so as to be moved into the receiving groove 211 of the outer rotating body, both ends are connected and supported on the other side of the outer rotating body 210 and the latch 230, and an operation spring made of a tension spring. (240);
The latch engaging groove 221 of the inner rotating body 220 has an inclined surface 221b that gradually increases in depth from the outer peripheral surface 220a to the forward rotation A of the input shaft, and is formed at the end of the inclined surface 221b to latch Includes a support surface (221a) that is in contact with the locking,
The latch receiving groove 212 of the outer rotating body 210 is a spring hole provided with a pin hole 213 to which a latch is pin-coupled, and a connecting ring 214a formed in the receiving groove 211 to connect and support an operation spring. (214);
One end of the actuating spring made of a tension spring is connected and supported to the connection ring 214a of the spring hole, and the other end of the actuating spring made of the tensile spring is connected and supported to the other side of the latch,
When the input shaft 810 and the inner rotor 220 are integrally rotated in the reverse direction (reverse direction) by the power unit 860 , the latch rotates around the pin 260 by the elastic force of the operation spring 240 . (230) is inserted into the latch engaging groove 221 of the inner rotor 220 is coupled, the outer rotation body 210 is driven in the reverse rotation by the coupling of the inner rotor 220 and the latch 230, The lower gear 811 is rotated in the reverse direction together with the input shaft 810 by the reverse rotational driving of the outer rotating body 210, so that the reverse driving force of the power unit 860 is transmitted to the output shaft 840. A gearbox equipped with one-way bearings and a reverse clutch.
an input shaft 810 having one end connected to the power unit 860, a lower gear 811 connected by a unidirectional bearing 813, and a higher gear 812 installed such that the bearing 814 is supported; a shift clutch 100 installed on the other end of the input shaft 810 and having a high gear 812 connected thereto; a reverse clutch 200 installed on one side of the input shaft 810 and having a low gear 811 connected thereto; In the transmission 800 including; the output shaft 840 for rotationally driven by the rotational driving force of the low gear 811 and the high gear 812 is transmitted by the reduction unit 830;
The reverse clutch 200,
A plurality of latch receiving grooves ( 212) and an outer rotating body 210 provided with,
The inner rotor is provided with a play in the receiving groove 211 of the outer rotating body so as to be driven integrally with the input shaft 810, the bearing 250 is supported, and the inner rotating body is provided with a plurality of latch engaging grooves 221 on the outer circumferential surface 220a. (220) and;
a latch 230 having one side coupled to a pin 260 in the latch receiving groove 212 of the outer rotating body;
The other side of the latch 230 is provided with an elastic force so as to be moved into the receiving groove 211 of the outer rotating body, both ends are connected and supported on the other side of the outer rotating body 210 and the latch 230, and an operation spring made of a tension spring. (240);
The latch engaging groove 221 of the inner rotating body 220 has an inclined surface 221b that gradually increases in depth from the outer peripheral surface 220a to the forward rotation A of the input shaft, and is formed at the end of the inclined surface 221b to latch Includes a support surface (221a) that is in contact with the locking,
The latch receiving groove 212 of the outer rotating body 210 is a spring hole provided with a pin hole 213 to which a latch is pin-coupled, and a connecting ring 214a formed in the receiving groove 211 to connect and support an operation spring. (214);
One end of the actuating spring made of a tension spring is connected and supported to the connection ring 214a of the spring hole, and the other end of the actuating spring made of the tensile spring is connected and supported to the other side of the latch,
The forward rotational driving force (forward driving force) of the input shaft 810 is transmitted to the output shaft 840 through the low gear 811 and the reduction unit 830, or the shift clutch 100 and the high gear 812 and the reduction unit ( 830) is transmitted to the output shaft 840,
When the input shaft 810 and the inner rotor 220 are integrally rotated in the reverse direction (reverse direction) by the power unit 860 , the latch rotates around the pin 260 by the elastic force of the operation spring 240 . (230) is inserted into the latch engaging groove 221 of the inner rotor 220 is coupled, the outer rotation body 210 is driven in the reverse rotation by the coupling of the inner rotor 220 and the latch 230, The lower gear 811 is rotated in the reverse direction together with the input shaft 810 by the reverse rotational driving of the outer rotating body 210, so that the reverse driving force of the power unit 860 is transmitted to the output shaft 840. A gearbox equipped with one-way bearings and a reverse clutch.
delete delete delete The method according to claim 1 or 2;
The shift clutch 100,
a clutch first rotor 110 installed to rotate integrally with the input shaft 810;
a centrifugal rocker unit 190 connected to the clutch first rotor 110 and operated by centrifugal force;
A transmission having a one-way bearing and a reverse clutch, characterized in that it includes; a clutch second rotor (120) integrally connected to the high gear (812).
7. The method of claim 6;
The centrifugal rocker part 190 is made of a torsion spring type centrifugal rocker part 190a including a rocker part 170 and a support rocker part 180,
One side of the locker unit 170 is pin-coupled in the first installation hole 113 of the clutch first rotor 110 and rotationally moves around the pin 173 by centrifugal force so that the engaging surface 171a is made of the clutch. A torsion unit such that the locker 171 supported in contact with the second rotor 120 and the moving end 172a are connected and supported on the other side of the rocker 171 and the fixed end 172b is connected to and supported by the clutch first rotor 110 . (172c) includes a torsion spring 172 is supported connected to the pin 173,
The support locker unit 180 has one end coupled to a pin 183 in the second installation hole 114 of the clutch first rotor 110, and is rotated around the pin 183 by centrifugal force to be mounted on the rocker 171. The support locker 181 to which the first support 181a is in contact, and the moving end 182a are connected and supported to the second support 181b of the support locker 181 , and the fixed end 182b is connected to the clutch first rotor 110 . ), the torsion part (182c) is connected to the pin (183) is supported so as to include a support torsion spring (182) that is configured to support a one-way bearing and a reverse clutch transmission provided with a clutch.

8. The method of claim 7;
The rocker 171 is further formed with a support protrusion 171b to which the first support 181a of the support locker is supported in contact,
The transmission device having a one-way bearing and a reverse clutch, characterized in that the support protrusion (171b) and the first support (181a) are in point contact (point contact) or in surface contact in a tangential direction of the support locker rotation radius (R). .
7. The method of claim 6;
The centrifugal rocker part 190 is made of a coil spring type centrifugal rocker part 190b including a rocker part 130 and a support rocker part 140,
One side of the locker part 130 is pin-coupled in the first installation hole 113 of the clutch first rotor 110, and rotationally moves around the pin 133 by centrifugal force, so that the engaging surface 131a is made of the clutch. 2 It includes a rocker 131 supported in contact with the rotor 120, and a rocker spring 132 having one end connected and supported to the other side of the rocker 131 and the other end connected and supported to the clutch first rotor 110, and
The support rocker unit 140 includes a ball spring 142 inserted and installed into a second installation hole 114 formed to communicate with one side of the first installation hole 113 having a pinhole 115, and a ball spring ( A one-way bearing and a reverse clutch comprising a support ball 141 supported in contact with one side of the rocker 131 by being elastically supported so that a part protrudes into the first installation hole 113 by the elastic force of 142). Equipped gearbox.
7. The method of claim 6;
The shift clutch 100,
A power transmission buffer unit 300 is further installed between the centrifugal rocker unit 190 and the clutch second rotor 120;
The power transmission buffer 300 is made of a spring-type buffer 310,
The spring-type shock absorber 310 has a clearance with the clutch first rotor 110 and the clutch second rotor 120 , and the rotation is accommodated between the clutch first rotor 110 and the clutch second rotor 120 . The plate 311 and the rotary plate 311 and the clutch second rotor 120 accommodated between, both ends are elastically supported by the rotary plate 311 and the clutch second rotor 120, the buffer operated in the circumferential direction It includes a spring (312),
A locking groove 150 for engaging the centrifugal rocker part 190 is formed in the rotation plate 311 , and a support protrusion 125 for elastically supporting the buffer spring 312 is formed in the clutch second rotor 120 . A transmission having a one-way bearing and a reverse clutch, characterized in that.
7. The method of claim 6;
A power transmission buffer unit 300 is further installed between the centrifugal rocker unit 190 and the clutch second rotor 120;
The power transmission buffer 300 is made of a friction pad type buffer 320,
The friction pad type buffer 320 includes a back plate 321 having a pad pin 325 on one side and an expansion pin 326 on the other side, and a play with the clutch first rotor 110 . The rotating body 322 which is integrally fixedly installed on the back plate 321 and in contact with the lockers 131 and 171 of the centrifugal rocker part is connected to and supported on one side by the pad pin 325 of the back plate, and is supported on the extension pin 326. The other side is connected and supported and the pad part 323 is installed symmetrically on one side 321a of the back plate so as to have a play with the rotating body 322 and is in contact with the clutch second rotor 120, and the other side of the back plate. It is installed on the side surface 321b to be connected to the extension pin 326 and rotates the extension pin 326 to press the pad part 323 to be in close contact with the clutch second rotor 120. It includes an extension part 324,
A transmission having a one-way bearing and a reverse clutch, characterized in that the rotation body (322) is formed with a locking groove (150) through which the lockers (131, 171) of the centrifugal rocker part (190) are engaged.
12. The method of claim 11;
The pad pin 325 is made of a circular pin type so that one side of the pad part 323 is supported in contact and rotated,
The extension pin 326 is made of a circular pin type in which a contact plane 326a on which the other side of the pad part 323 is supported in contact is formed on both sides,
The pad part 323 is provided with a friction pad 323a that is in frictional contact with one side of the clutch second rotor 120 to cushion the rotational shock and vibration according to the shift, and one end of the pad pin 325 . One-way bearing and reverse clutch, characterized in that a semicircular contact groove (323b) is provided in contact with the outer circumferential surface to enable rotation, and a contact surface (323c) supported in contact with the contact plane (326a) of the extension pin is provided at the other end. gearbox equipped with
12. The method of claim 11;
The extension part 324 includes a rotary lever 324a integrally connected to the expansion pin 326, one side supported by the back plate 321 and the other side supported by the rotary lever 324a, the expansion pin 326) It includes a pressing member (324b) for rotating the rotary lever (324a) around,
The pressing member 324b includes a coil spring 324c, a first guide pin 324d fitted to one end of the coil spring 324c, and a first guide pin 324d and is screwed with a fixing nut ( 324e), an elastic adjustment bolt 324f fixed to the support bracket 321a of the back plate, and a second guide pin 324g fitted to the other end of the coil spring 324c and supported by the rotation lever 324a. is composed to include,
The position of the first guide pin 324d is adjusted by the adjustment of the elastic adjustment bolt 324c and the nut 324e, and the coil spring 324c is pressed and compressed by the position change of the first guide pin 324d, A transmission having a one-way bearing and a reverse clutch, characterized in that the rotary lever (324a) and the extension pin (326) are rotated by the elastic force of the coil spring (324c).

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