KR20150029223A

KR20150029223A - endless Transmission

Info

Publication number: KR20150029223A
Application number: KR20130108100A
Authority: KR
Inventors: 이춘우
Original assignee: 주식회사 중정
Priority date: 2013-09-09
Filing date: 2013-09-09
Publication date: 2015-03-18

Abstract

In the present invention, both the driving gear and the driven gear are parallel to each other, and the driving shaft and the driven shaft are internally engaged with each other through a bearing, Way clutch is interposed between the drive shaft and the drive gear group or between the driven shaft and the driven gear group, and the drive chain base and the driven chain base of the driven / paired clutches using the ball screw in the drive shaft and the driven shaft, So that two driving gears of the plurality of driving gears and two driven gears meshed with the two driving gears are engaged with each other so that the driving force of the driving shaft is transmitted to the driven shaft, Even if a driving force is transmitted to the driven shaft through the driven gear by one of the plurality of driving gears, Only the driven gear engaged with the one drive gear among the plurality of driven gears transmits the driving force to the driven shaft and the other driven gears are idle or held at the position, So that it is possible to transmit the load to the driven shaft with a smaller driving force than in the prior art, thereby reducing manufacturing cost and maintenance cost.

Description

Endless Transmission

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an infinite transmission, and more particularly, to an infinite transmission having a continuously variable transmission that uses a retaining clutch and a one-way clutch to increase the number of transmissions without inflicting an impact on the engaged clutch and the one- Lt; / RTI >

The automatic transmission is a device in which the gear is automatically operated according to the speed at which the gear ratio is automatically selected and operated, regardless of the driver's operation. This automatic transmission automates the rudder operation and gear shifting required for the car to run.

In addition, depending on the speed set for each car and stepping on the accelerator, the appropriate gear is selected.

This automatic transmission is designed so that the gear ratio can be automatically selected by activating the fluid clutch, band or disc plate.

Typically, automatic transmissions include Ravigneaux or Simpson planetary gear units that include sun gear, planetary gears, ring gears, and planet gear carriers.

This planetary gear unit is required to have a complicated structure in which a sun gear, a planetary gear, a ring gear, and a planetary gear carrier are selectively engaged with an input shaft and an output shaft, respectively. The power of the input shaft is not instantaneously transmitted to the output shaft, and the driven object may fall freely when the driven object is receiving gravity.

Further, the conventional automatic transmission has a problem that it can provide a plurality of transmission stages, but can not provide infinitely many transmission stages.

An infinite transmission for solving such a problem is disclosed in Korean Patent No. 10-102968.

The above-described infinite transmission has a plurality of driven gears, each of which has a smaller diameter as it goes to one side, circumscribes the input shaft via a one-way clutch, and a plurality of driven gears, which are meshed with these driving gears, And a plurality of contact pressing members which are in contact with the inner circumferential surface of the plurality of driven gears by centrifugal force are mounted on the output shaft so as to be movable in the radial direction of the plurality of contact pressing members, And a loader of a support unit which is reciprocated by a translating portion in the output shaft so as to selectively support the contact pressing member so that power can be transmitted from the input shaft to the output shaft while being transmitted without loss of power transmission.

However, in the above-described automatic transmission, only when the plurality of contact pressure members are radially outwardly opened by the centrifugal force, the loader of the support unit enters between the two contact pressure members of the plurality of contact pressure members, So that the two contact pressing members contact and press the two driven gears among the plurality of driven gears to transmit the power transmitted from the driving gear to the two driven gears to be transmitted to the output shaft However, in a state in which the centrifugal force is not generated in the plurality of contact pressure members because the output shaft is not rotated, for example, in a state where the loader of the support unit is in the neutral position or the input shaft is stopped, A plurality of contact pressure members disposed above the contact pressure members are arranged in a radial direction So that the driven gears can not rotate and the power of the input shaft can not be transmitted to the output shaft even if the input shaft is restarted. Furthermore, since the left-right movement of the loader of the support unit is caused by gravity, The input shaft is driven to drive the driven shaft in order to constantly apply the centrifugal force to the plurality of contact pressure members because the shifting member can not enter between the contact pressing members which are obstructed by the pressure members, There is a problem in that it is impossible to realize a neutral state and there is a problem that a plurality of recesses are formed on the inner circumferential surface of the driven gear to cause a collision between the contact pressing member and the recessed portion due to the centrifugal force and noise is generated.

An automatic transmission for solving the above problem is disclosed in Patent Registration No. 10-0042099, which is patented and patent registered by the present inventor.

The above-described automatic transmission includes a ball screw fixedly inscribed on a tubular shaft; A chisel base portion which is fastened to the ball screw and slidably inserted in the tubular shaft; And a plurality of recesses are formed on the inner circumferential surface of the inner race of the one-way clutch at predetermined intervals along the circumferential direction of the one raceway clutch And a plurality of spur gears having a larger diameter toward an axial side; When the radially inner portion is seated in a plurality of through holes formed at predetermined intervals in the axial direction at the portions of the tubular shafts facing the plurality of spur gears and selectively pressed by the chain base portion in the radial outward direction to be pressed, And a plurality of spur gears fixedly circumscribed to the output shaft and meshing with the plurality of spur gears and having a smaller diameter toward the one axial side in the axial direction, And an automatic transmission having a length capable of contacting at least two protruding and retracting members including an driven gear portion and an axial length of the chain base portion in the axial direction.

In the above-described automatic transmission, when the chain base portion simultaneously engages two drive gears having different diameters, the two gears rotate equally by the tubular shaft, and the two driven gears, which are engaged with the two drive gears, The rotational force of the two driving gears having different circumferential speeds is applied to the gear, and the driven shaft fixedly inscribed on the two driven gears fixedly circumscribed to the driven shaft is subjected to the rotational forces of the peripheral speed, However, since the driving gears are rotatably circumscribed by the one-way clutch on the tubular shaft, only the driving gear of the larger diameter among the two driving gears is larger than the larger one of the two driven gears And transmits a rotational force to a small driven gear engaged with the drive gear, and a large driven gear of two driven gears fixedly circumscribed to the driven shaft The small drive gear is rotated in the same direction as the rotational direction of the tubular shaft by the peripheral speed of the tubular shaft, so that any p / drive gear, tubular shaft, and driven shaft are not damaged.

However, in the above-described automatic transmission, the driving force is transmitted to the driven shaft selectively by one of the plurality of driving gears by the engaging clutch in a state in which a plurality of driving gears are actually circumscribed via the bearings and the one- However, since a plurality of driven gears are fixedly circumscribed on the driven shaft, not only the driven gear engaged with the one drive gear among the plurality of driven gears rotates but also all of the driven gears rotate together with the driven shaft, There is a problem that a large power is required to transmit the driving force to the coaxial shaft.

The present invention has a problem in solving the above-mentioned problems.

In the present invention, both the driving gear and the driven gear are parallel to each other, and the driving shaft and the driven shaft are internally engaged with each other through a bearing, Way clutch is interposed between the drive shaft and the drive gear group or between the driven shaft and the driven gear group, and the drive chain base and the driven chain base of the driven / paired clutches using the ball screw in the drive shaft and the driven shaft, So that two driving gears of the plurality of driving gears and two driven gears meshed with the two driving gears are engaged with each other so that the driving force of the driving shaft is transmitted to the driven shaft, The above problems can be solved.

According to the present invention, even when a driving force is transmitted to a driven shaft through a driven gear by a driving gear of a plurality of driving gears, Only the driven gear engaged with the driving gear of the other driven gear is transmitted to the driven shaft and the other driven gears are idle or held in position to give a load in the rotating direction by the weight of the other driven gear to the driven shaft It is possible to transmit the driving force to the driven shaft with a smaller driving force than in the prior art, thereby reducing manufacturing cost and maintenance cost.

1 is a view showing an automatic transmission according to a first embodiment of the present invention,
2 is a view showing an automatic transmission according to a second embodiment of the present invention.

Hereinafter, an infinitely variable transmission according to an embodiment of the present invention will be described in detail with reference to FIG.

In Fig. 1, an infinite transmission is indicated by reference numeral 200.

The infinite transmission 200 includes an input shaft 10 fixedly inscribed in a driven gear 4 meshed with a drive gear 2 fixedly circumscribed to a drive shaft 1 of a drive motor M1 as a one-way drive, An input gear unit 210 rotatably circumferentially spaced apart from the input shaft 10 by a bearing B via a bearing B; a tubular output shaft 201 disposed parallel to the input shaft 10, An input clutch unit 220 selectively engaged with the input gear unit 210 and an input clutch unit 220 selectively engaged with the input gear unit 220. The input clutch unit 210 selectively engages the input clutch unit 210, And an output clutch (120).

The input device unit 210 includes a plurality of input gears 40 having a larger diameter toward one side in the axial direction. Each of the plurality of input gears 40 is circumscribed via the one-way clutch C to the bearing B circumscribed to the input shaft 10.

The output gear unit 220 includes a plurality of output gears 60 meshing with the plurality of input gears 40 and having a smaller diameter toward one axial side.

The input clutch 110 includes a input ball screw 112 through which a input screw shaft 111 is rotatably inserted via a bearing to the input shaft 10 as a translating portion, And an input wedge nut (113) which is coupled to the input shaft (10) by sliding in an axial direction so as to be slidably engaged with the input shaft (10) A plurality of input recessed portions 41 formed on the inner circumferential surface of the inner circumferential surface C1 at predetermined intervals along the circumferential direction; And a plurality of input shafts (41) of the inner race (C1) of the one-way clutch (C) of each of the plurality of input gears (40) When the radially inner portion is inserted into the input through holes 11 and is selectively pushed outward in the radial direction by the input wrench nut 113 and pressed, the plurality of input concave portions 41 are pushed outward in the radial direction, And an input / output member 115 such as a ball into which a part of the input recessed portion 41 is inserted.

The output clutch 120 includes an output ball screw 122 in which an output screw shaft 121 is rotatably inserted into the output shaft 201 via a bearing, And an output worm nut 123 which is coupled to an output screw shaft of the output gears 60 and slidably inserted in the axial direction of the output shaft 201. The output worm gears 123 are disposed on the inner circumferential surface of each of the plurality of output gears 60 along the circumferential direction A plurality of output recesses (61) spaced apart at a predetermined interval; And a plurality of output through holes (211) formed at predetermined intervals in the axial direction at a portion of the output shaft (201) facing the plurality of output recessed portions (61) of each of the plurality of output gears And is pushed outward in the radial direction by pushing in the radially outward direction selectively by the output worm nut 123 to partially insert into the output recessed portion 61 of the plurality of output recessed portions 61 And an output protruding and retreating member 125 such as a ball.

The detailed configurations of the input clutch 110 and the output clutch 120 are disclosed in Korean Patent Application Nos. 10-2013-0034059, 10-2013-0037481, 10-2013 -0038972, and 10-2013-0042260 and registered patent application No. 10-1267823, the detailed description of the retaining clutch 110 is omitted below.

The axial length of the input wedge nut 113 is set so that the axial length of the input wedge nut 113 is the same as or larger than two adjacent input and output-emitter members in the input shaft 10 at the time of shifting from the low speed end to the high speed end and from the high speed end to the low speed. I.e., a length capable of contacting the input / output member 115 such as at least two balls which are adjacent to each other in the axial direction.

In addition, the axial length of the output worm nut 123 is set such that the output shaft 201 has the same output as two or more balls in the output shaft 201 at the time of shifting from the low speed to the high speed end and from the high speed end to the low speed. Has a length capable of maintaining the pressure on the protruding / retracting member 125, that is, a length capable of contacting the output protruding / lowering member 125 such as at least two balls adjacent in the axial direction.

The input wedge nut 113 having the axial length as described above is moved relative to the input and output member 115 such as any one ball in the input shaft 10 when the input wedge nut 113 moves within the input shaft 10 for shifting. The power of the input shaft 10 can be transmitted to the output shaft without interruption at the time of shifting because of the pressure applied to the input and output member 115 and 115 such as at least two balls.

The output worm nut 123 having the above-described axial length has the same appearance as that of the output impeller member 125 in the output shaft 201 when it moves within the output shaft 201 for shifting. It is possible to transmit the power of the output shaft 201 to the output shaft without interruption at the time of shifting because the output is made to press against the output-side projecting / diving members 125, 125 such as at least two balls adjacent to each other.

The input wedge nut 113 presses the input and output member 115 and 115 such as two balls which are adjacent to each other in the axial direction so as to engage the two input gears 40 and 40, 123 abut the two adjacent output-side projecting / retracting members 125, 125 in the axial direction located in the output gears 60, 60 engaged with the two input gears 40, 40, Two input gears 40 and 40 having different numbers of teeth of the input gear unit 210 having the one-way clutch C pressed to the input / output member 115 and 115 such as the two balls move at the same angular speed, It is determined that the two output gears 60 and 60 having different numbers of teeth of the meshed output gear unit 220 move at different angular velocities and the output shaft 201 receives the twisting force and the gear teeth may be damaged. When one-way clutch C is interposed in each of input gears 40 and 40 The low speed side input gear 40 of the input device unit 210 is connected to the input gear unit 210 by the output gear 60 of the output device unit 2200 engaged with the low speed side input gear 40 of the input device unit 210. [ The input shaft 10 is rotated at a speed higher than the rotation speed of the input shaft 10 so as to match the angular speed of the output gear 60 of the output gear unit 220 engaged with the high speed single- The clutch is not in a stepped state, so that the low-speed short-side input gear 40 of the input unit 210 rotates in the direction of rotation of the input shaft 10 smoothly.

Although the one-way clutch C is described as being interposed between the plurality of input gears 40 of the input device unit 210 in the above embodiment, the present invention is not limited to this and the plurality of input gears 40 of the output device unit 220 Directional clutch C may be interposed between each of the output gears 60 and the output shaft 201. The direction of the one-way clutch C interposed in the output gear unit 220 may be a direction Is opposite to the direction in which the mouth direction clutch engaged in the fisher part (210).

Further, in the above embodiment, it is spatially limited that the engaging clutch 110 and the one-way clutch C are interposed in the input gear having a small diameter among the plurality of input gears of the input device unit 210, Way clutch (C) may be interposed in the output gear (60) of the output gear unit (220) which meshes with an input gear (40) having a small diameter among a plurality of input gears (40) At this time, the direction of the one-way clutch C interposed in the output gear 60 of the output gear unit 220 is opposite to the direction of the input direction clutch engaged in the input gear 40 of the input gear unit 210 to be.

1 and 2, the input wrench nut 113 of the input clutch 110 and the output wrench nut 123 of the output clutch 120 are connected to the input Can be moved simultaneously in both the axial direction by the wrench nut and the mode switching means for moving the output wrench nut.

The input wedge nut 113 of the input clutch 110 and the output wedge nut 123 of the output clutch 120 are connected to each other by a separate power source, For example, an input shaft and an output shaft), and one end of the input screw shaft and the one end of the output screw shaft may be respectively coupled to a shaft of the motors, Or may be simultaneously moved axially both sides by a single power source. At this time, for example, the cylinder body is fixed to the base, and the input screw shaft and the output screw shaft are changed to the input rod and the output rod, Wherein the input wedge nut and the output wedge nut are mounted on the input shaft and the output shaft so as to be movable in the axial direction so as not to rotate in the circumferential direction Wherein the input rod portion and the output rod portion are rotatably externally connected to the input rod portion and the output rod portion via bearings, respectively, and the input rod and the output rod are connected to the input rod portion and the output rod portion, respectively, It may be fixed to the main rod.

1, the position of the input wedge nut 113 and the output wedge nut 123 may be positioned at the same position in the axial direction of the input shaft 10, The one input gear 40 and the one input gear 40 engage with each other with the one input gear 40 interposed therebetween, The input worm nut 113 is positioned at a position where one input gear 40 can be engaged with the one input gear 40 at the same time and the one The output wedge nut 123 may be positioned at a position where the other output gear 60 having a smaller diameter than the output gear 60 of the output gear 60 can be engaged with the one output gear 60 at the same time, The wedge nut (113) and the output wedge nut (123) One input gear 40 and one output gear 60 which are engaged with each other and engage with each other are engaged with either one of the input wrench nut 113 and the output wrench nut 123 The diameter of the input gear 40 or the diameter of the other output gear 60 may be larger.

In the former case, the other input gears 40 not engaged with the input wedge nut 113 are not rotated during power transmission, and the other output gears 60, which are not engaged with the output wedge nut 113, When the input wedge nut 113 is moved to a smaller diameter or when the output wedge nut 123 is moved to a smaller diameter in a state in which the input wedge nut 113 is not engaged, The input wedge nut 113 is moved in the axial direction and is not held by the input wedge nut 113 so that the rotation of the input wedge nut 113 is transmitted to the output shaft 201. Therefore, Even when the output wedge nut 123 is moved in the axial direction and is not caught by the output wedge nut 123 so as to engage with the small output gear 60 which is not rotating, Way clutch (C) is interposed The small input gear 40 newly engaged is idle so that these gears are not involved in transmitting the driving force to the throwing shaft 201 while rotating so that the load of the driven object coupled to the output shaft at the time of deceleration The output shaft 201 is moved by the newly engaged small input gear 40 when the input wrench nut 113 is moved so as to engage with the smaller input gear 40, The input gear 40 and the output gear 60 meshing with the input gear 40 rotate while being engaged with each other to be in a driving force transmitting state to perform deceleration of the drum. However, since the input worm nut 113 has a diameter The input shaft 10 and the output shaft 20 which rotate in the input gear 40 or the output gear 60 having a large diameter which is not rotated are not rotated when the output wedge nut 123 moves to a larger diameter, 1 is instantaneously coupled by the input worm nut 113 and the output worm nut 123 to be in a driving force transmitting state so that the load of the load object is not directly rotated by the input gear 40 or the output gear The input clutch, the input shaft, the output shaft, the input gear, the output gear, and the like may be deformed or broken.

However, in the latter case, even if the input wedge nut 113 and the output wedge nut 123 move synchronously from one side to the other or from the axial direction during power transmission, the input wedge nut 113 and the output wedge 123, When any one of the nuts 123 moves to a gear having a smaller diameter so that any one of the input wrench nut 113 and the output wrench nut 123 moves toward a gear having a larger diameter to engage with a new gear having a larger diameter The large gear having a large diameter and the small gear meshed with the large gear are already rotated without transmitting the driving force to the output shaft so that the driving force is transmitted without a large impact force, The input gear, the output gear, and the like are prevented from being deformed or broken.

The mode switching means for synchronously moving the input wrench nut 113 of the input clutch 110 and the output wrench nut 123 of the output clutch 120 in the axial direction is provided on the drive shaft 1 A first forward driven gear 6 fixedly circumscribed to the output screw shaft 121 and a second forward driven gear 6 fixed to the output screw shaft 121. The first forward driven gear 6 and the first forward driven gear 6, A reverse intermediate gear 151 interposed between the forward driving gear 5 and the forward intermediate gear 151 so as to be rotatably mounted on the base and selectively interlocked with the forward driving gear 5 so that the driving shaft 1 and the forward driving gear 5 rotate together A third stopper 150 for preventing the reverse intermediate gear 151 from rotating by selectively engaging the reverse intermediate gear 151, a second stopper 150 fixedly attached to the output shaft 201, The second forward driven gear 7, the second forward driven gear 7, A first tubular shaft 9 rotatably housed in the inverted driven gear 8 and coupled to the input screw shaft 111, a first tubular shaft 9 coupled to the first tubular shaft 9, And a second stopper 140 for selectively rotating the reverse driven gear 8 to rotate the tubular shaft 9 and the reverse driven gear 8 together.

Further, the input screw shaft 111 has a left-handed thread and the output screw shaft 121 has a right-hand thread.

The first forward driven gear 6 is rotated at a higher speed or at the same speed as the speed at which the output shaft 201 rotates through the gear ratio of the forward drive gear 5 and the reverse intermediate gear 151 The first reverse driven gear 8 is set to a predetermined speed increase ratio (for example, the first forward driven state is 10) when the input shaft 10 is at a predetermined speed increase rate (for example, the input shaft is 1) Is set such that it can rotate with the reverse speed reduction ratio of the predetermined speed increasing ratio (for example, if the output shaft is 10, the first reverse driven gear is 1) through the gear ratio with the second forward driven gear 7.

The first and second stoppers (130, 140) are configured such that gears rotatably circumscribed by the tubular portion are rotatably connected to the tip of the rod of the cylinder fixed to the base via a bearing, It is preferable from the viewpoint of manufacturing and maintenance that the fluid is not supplied to the rotating body.

The infinite transmission having the mode switching means configured as described above can be operated as follows. In the following description, the forward direction is the clockwise direction and the reverse direction is the counterclockwise direction.

1. When the first to third stoppers 130, 140 and 150 are in a non-stepped state

In this case, the input wedge nut 113 and the input screw shaft 111 rotate together in the opposite direction at the same speed, and the output wedge nut 123 and the output screw shaft 121 rotate together at the same speed in the forward direction , The input wedge nut 113 and the output wedge nut 123 can not be moved in the axial direction and are held in place.

2. When the third stopper 150 is in the stepped state and the first and second stoppers 130 and 140 are in the non-stepped state

In this case, assuming that the drive shaft 1 rotates in the forward direction, the reverse intermediate gear 151 is rotated in the forward direction by the third stopper 150 The output screw shaft 121 is stopped and the output worm nut 123 fastened to the output screw shaft 121 having the right screw thread is moved in the unwinding direction, that is, in the left direction in FIG. 1 And the input shaft 10 and the input worm nut 113 are rotated together in the reverse direction so that the first reverse driven gear 8 is engaged with the first forward driven gear 7 via the gear ratio with the second forward driven gear 7, The first reverse direction driven gear 8 and the input screw shaft 111 rotate in the reverse rotation speed of the input shaft 10 and the input worm nut 113, Lt; RTI ID = 0.0 > slower < / RTI > The input wrench nut 113 and the output wrench nut 123 are moved in the unwinding direction, that is, in the left direction in Fig. 1, so that the input wrench nut 113 and the output wrench nut 123 The output worm nut 123 and the input worm axis 111 are rotated by the rotational speed of the output shaft 201 so that the input worm nut 113 and the output worm nut 123 rotate synchronously. Is moved to the left at the same speed.

That is, when the acceleration ratio is 10 and the reduction ratio is 0.1, the output shaft 201 is shifted in the forward direction, for example, to rotate 9, and the input spiral shaft 111 is rotated in the reverse direction by 0.9, Assuming that the output worm nut 123 is moved to the left by A distance when the output screw shaft 201 is stopped by the third stopper 150, the input spiral shaft 111 is rotated by the input worm nut 113 The state of the input screw shaft 111 and the input worm nut 113 is the same as that of the output shaft 111 because the state of the input screw shaft 111 and the input worm nut 113 is the same as the output So that the state of the screw shaft 121 and the output worm nut 123 becomes the same. As a result, the input worm nut 113 moves to the left by A distance.

3. When the third stopper 150 is in a non-stepped state and the first and second stoppers 130 and 140 are in a stepped state

In this case, assuming that the drive shaft 1 rotates in the normal direction, the first forward driven gear 6 is rotated in the normal direction while the output shaft 201 and the output worm nut 123 are rotating in the forward direction, The output shaft 201 is rotated at a speed higher than the speed at which the output shaft 201 rotates at the highest speed through the gear ratio between the gear 5 and the reverse intermediate gear 151 at a predetermined speed increasing ratio with respect to the input shaft 10 The first forward driven gear 6 rotates the output screw shaft 121 faster than the output shaft 201 and the output worm nut 123 in the forward direction and the output screw shaft 121 having the right screw thread is rotated, The output wedge nut 123 is moved in the tightening direction to the right in FIG. 1 and the input shaft 10 and the input wedge nut 113 are rotated in the reverse direction together. Wherein the gear (8) The first reverse directional drive gear 5 and the input screw shaft 111 rotate relative to the input shaft 10 because the reverse reverse gear 5 and the input shaft 10 are rotated at a slower speed than the input shaft 10, 10 and the input wedge nut 113 so that the input wedge nut 113 fastened to the input screw shaft 111 having the left wedge line moves in the fastening direction, that is, the rightward direction in Fig. 1, The output worm nut 113 and the output worm nut 123 move synchronously to the right together and rotate the output spiral shaft 121 at a predetermined speed increasing ratio with respect to the input shaft 10 and rotate the input spiral shaft 121 Is rotated at the reverse speed reduction ratio of the predetermined speed ratio with respect to the shifted output shaft 201, the input wrench nut 113 and the output wrench nut 123 are moved to the right at the same speed.

That is, when the speed ratio is 10 and the speed ratio is 0.1, when the input shaft 10 makes one rotation in the reverse direction, the output shaft 201 is shifted in the forward direction, for example, to rotate 9, 121 rotate in the forward direction by the speed ratio and the input spiral shaft 111 rotates in the reverse direction by 0.9 due to the reverse gear ratio so that the output spiral shaft 121 rotates 10, The nut 123 is rotated 9 and the input worm nut 10 rotates 1 and the input spiral shaft 111 rotates 1/9 so that the output spiral shaft 121 and the axial wax nut The state of the input screw shaft 111 and the state of the input wrench nut 113 are the same as those of the input wrench shaft 111 and the input wrench nut 113 because the relative speed difference between the input screw shaft 111 and the input wrench nut 113 is 10 times equally The state of the output screw shaft 121 and the output worm nut 123 become the same, And the output worm nut 123 and the output worm nut 123 move to the right at the same speed.

In the case where the speed ratio is such that the first forward driven gear 6 rotates as the speed ratio when the output shaft is shifted and rotates at the fastest speed, the input worm portion and the output worm nut are moved to the left side The input gear and the output gear disposed on the rightmost side and the input gear and the right gear disposed on the left side are dulled in an infinite transmission in which one of the input chain and the output chain nut is moved toward the small gear.

This is because the input screw shaft 111 and the input wrench nut 113 rotate in the same direction and speed and the output screw shaft 121 and the output wrench nut 123 rotate in the same direction and speed.

The infinitely-variable transmission as described above can arrange gears having different gear ratios in an axial direction in an infinite manner, so that it is possible to provide an operational effect of providing numerous speed-changing ratios.

Further, in the explanation of the infinitely variable transmission of the embodiment, although the input screw shaft 111 has a left-handed line and the output screw shaft 121 has been described and shown as having a right-handed screw, The input screw shaft 111 has a right screw thread and the output screw shaft 121 has a left screw thread. At this time, when the third stopper 150 is in the stepped state, (123) and the input wedge nut (113) move synchronously and at the same speed in the tightening direction (rightward direction).

In the description of the infinitely variable transmission according to the above embodiment, the first forward driven gear 6 is rotated at a constant speed with respect to the input shaft 10 so that the first forward driven gear 6 can rotate faster than the speed at which the output shaft 201 rotates as fast as possible And that the first reverse driven gear 8 is set to be able to rotate with the reverse speed reduction ratio of the predetermined forward speed ratio to the second forward driven gear 7 However, the present invention is not limited to this, and the second forward driven gear 7 may be rotated so that the first reverse driven gear 8 can rotate faster than the speed when the output shaft 201 rotates as fast as possible, And the first forward driven gear 6 is set so as to be able to rotate with the predetermined speed increasing ratio of the predetermined forward speed with respect to the input shaft 10 The output wedge nut 123 and the input wedge nut 113 can be synchronously rotated at the same speed when the first and second stoppers 130 and 140 are in a stepped state (In the leftward direction).

10; An input shaft, 110; An input clutch, 120; An output clutch, 200; Infinite transmission, 201; Output shaft

Claims

A plurality of input gears rotatably circumscribed by an input shaft of a tubular shape and arranged to have a larger diameter in a direction from the axial direction to the one side;
A plurality of output gears rotatably circumscribed by a tubular output shaft and engaged with the plurality of input gears and arranged to have a larger diameter toward the other side in the axial direction;
A plurality of one-way clutches interposed between any one of input gears and output gears meshing with each other and an input shaft or an output shaft inscribed in either one of the gears;
An input clutch for engaging two adjacent gears among a plurality of input gears rotatably circumscribed on an input shaft or for engaging the one-way clutch inscribed on the input gear; And
An output clutch that engages two adjacent gears among a plurality of output gears that are rotatably circumscribed on an output shaft, or engages the one-way clutch that is inscribed in the output gear,
Each of the input clutch and the output clutch
An input chaining section or an output chaining section which is movable in an axial direction by an input translating section or an output translating section in an input shaft or an output shaft;
A plurality of input recesses or output recesses spaced along the circumferential direction on the inner circumferential surface of each of the plurality of input gears or output gears or the inner circumferential surface of the inner race of the plurality of one-way clutches; And
A radial inner portion is inserted and seated in each of a plurality of through holes spaced apart axially from a portion of the input shaft or the output shaft facing the plurality of input concave portions or output concave portions, And an input / output projecting / retracting member or an output projecting / retreating member, which is partially inserted into the input recessed portion or the output recessed portion when pressed by being pushed outwardly,
Wherein each of the plurality of one-way clutches is a one-way clutch in a state of being engaged when a rotational driving force is transmitted to the driven object in one direction,
Wherein the input synchronizing portion of the input clutch and the output synchronizing portion of the output clutch move synchronously with each other in the same direction in the axial direction on the input shaft and the output shaft.

The method according to claim 1,
Wherein the input translating unit and the output translating unit are ball screws,
Wherein the input wedge portion and the output wedge portion are wedge nuts,
The input translating unit and the output translating unit include first and second forward and reverse motors for selectively rotating the screw shaft of the ball screw in the forward and reverse directions to move the wrench nut in the axial direction, Wherein the transmission mechanism comprises:

The method according to claim 1,
The input translating unit and the output translating unit
The body of the cylinder fixed to the base,
The input wedge portion and the output wedge portion inscribed in the axial direction so as not to rotate in the circumferential direction on the input shaft and the output shaft,
And an input rod and an output rod rotatably inscribed in the input choke section and the output choke section via a bearing,
Wherein the input rod and the output rod are fixed to a main rod of the cylinder.

The method according to claim 1,
Further comprising mode switching means for synchronously shifting the input wobbling portion and the output wobbler portion at the same speed in the axial direction by the power source of the infinite variable speed gear.

The method according to claim 1,
The axial length of the input wobbling portion has a length capable of maintaining the pressurization with respect to the two adjacent input / output members in the input shaft at the time of shifting from the low speed to the high speed end and from the high speed end to the low speed However,
The axial length of the output wobbling portion has a length capable of maintaining the pressure on two neighboring output mobiles in the output shaft at the time of shifting from the low speed to the high speed and at the speed changing from the high speed to the low speed Wherein the transmission mechanism comprises:

The method according to claim 1,
Wherein the position of the input wobbling portion and the output wobbler portion are positioned at the same position in the axial direction of the input shaft or the position of the output wobbler portion The input wrench nut 113 is positioned at a position capable of simultaneously engaging another input gear of a smaller diameter than the one input gear with the one input gear, The output wedge nut 123 is positioned at a position where the other output gear 60 having a smaller diameter than the immediately adjacent output gear 60 can be engaged with the one output gear 60 at the same time An input gear 40 and an output gear 60 which are simultaneously engaged by the input wrench nut 113 and the output wrench nut 123 are engaged with the input wrench nut 113, And the output worm nut 123 is arranged so as to have a diameter larger than the diameter of the other one of the input gears 40 or the other output gear 60 which is engaged with one of the worm nuts of the output worm nut 123. [ Infinite transmission.

5. The method of claim 4,
Wherein the mode switching means comprises:
A forward drive gear rotatably circumscribed by the drive shaft,
A first forward driven gear fixedly circumscribed to the output screw shaft,
A reverse intermediate gear interposed between the forward drive gear and the first forward driven gear and meshed with the forward drive gear and rotatably mounted on the base,
A first stopper for selectively driving the forward drive gear to rotate the drive shaft and the forward drive gear together,
A third stopper for selectively interlocking the reverse intermediate gear to prevent the reverse intermediate gear from rotating,
A second forward driven gear fixedly circumscribed to the output shaft,
A first reverse driven gear engaged with the second forward driven gear,
And a second stopper (140) for selectively rotating the input screw shaft and the first reverse driven gear together or only the first reverse driven gear with a driving force of the second forward driven gear,
Wherein the input screw shaft is one of a left-hand thread and a right-hand thread, and the output screw shaft is another one,
Wherein the first forward driven gear is set at a predetermined speed increase ratio with respect to the input shaft by a predetermined speed so as to rotate at a speed faster than or equal to the speed at which the output shaft rotates as fast as possible, Is set to be able to rotate with an inverse speed reduction ratio of the predetermined speed increasing ratio.

5. The method of claim 4,
Wherein the mode switching means comprises:
A forward drive gear rotatably circumscribed by the drive shaft,
A first forward driven gear fixedly circumscribed to the output screw shaft,
A reverse intermediate gear interposed between the forward drive gear and the first forward driven gear and meshed with the forward drive gear and rotatably mounted on the base,
A first stopper for selectively driving the forward drive gear to rotate the drive shaft and the forward drive gear together,
A third stopper for selectively interlocking the reverse intermediate gear to prevent the reverse intermediate gear from rotating,
A second forward driven gear fixedly circumscribed to the output shaft,
A first reverse driven gear engaged with the second forward driven gear,
And a second stopper (140) for selectively rotating the input screw shaft and the first reverse driven gear together or only the first reverse driven gear with a driving force of the second forward driven gear,
Wherein the input screw shaft is one of a left-handed screw and a right-handed screw, and the output screw shaft is another one,
The first reverse driven gear is set so as to rotate with the predetermined speed increasing ratio by a predetermined speed with respect to the second forward driven gear so that the first reverse driven gear can rotate faster than the speed at which the output shaft rotates as fast as possible And the first forward driven gear is set so as to be able to rotate with respect to the input shaft with an inverse speed reduction ratio of the predetermined speed increasing ratio.