WO2014171722A1 - Automatic transmission - Google Patents

Automatic transmission Download PDF

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Publication number
WO2014171722A1
WO2014171722A1 PCT/KR2014/003285 KR2014003285W WO2014171722A1 WO 2014171722 A1 WO2014171722 A1 WO 2014171722A1 KR 2014003285 W KR2014003285 W KR 2014003285W WO 2014171722 A1 WO2014171722 A1 WO 2014171722A1
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WO
WIPO (PCT)
Prior art keywords
shaft
output
input
gear
idle
Prior art date
Application number
PCT/KR2014/003285
Other languages
French (fr)
Korean (ko)
Inventor
이춘우
Original Assignee
주식회사 칼라카나
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020130042099A external-priority patent/KR101267823B1/en
Priority claimed from KR1020130065616A external-priority patent/KR101533794B1/en
Priority claimed from KR20130110910A external-priority patent/KR20150031563A/en
Application filed by 주식회사 칼라카나 filed Critical 주식회사 칼라카나
Publication of WO2014171722A1 publication Critical patent/WO2014171722A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/083—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with radially acting and axially controlled clutching members, e.g. sliding keys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/04—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways with a shaft carrying a number of rotatable transmission members, e.g. gears, each of which can be connected to the shaft by a clutching member or members between the shaft and the hub of the transmission member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D28/00—Electrically-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/24—Concentric actuation rods, e.g. actuation rods extending concentrically through a shaft

Definitions

  • the present invention relates to an automatic transmission, and more particularly, to an automatic transmission that is capable of continuously shifting without engagement using a retaining clutch and a one-way clutch,
  • the present invention relates to an automatic transmission equipped with an automatic transmission.
  • 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 is designed so that the gear ratio can be automatically selected by activating the fluid clutch, band or disc plate.
  • 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.
  • the conventional automatic transmission has a problem that it can provide a plurality of transmission stages, but can not provide infinitely many transmission stages.
  • the automatic transmission includes a plurality of drive gears that are smaller in diameter toward one side than the other, and a plurality of driven gears that are meshed with the drive gear and increase in diameter toward the other side via a one- 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.
  • 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,
  • 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.
  • the present invention has a problem in solving the above-mentioned problems.
  • the present invention relates to a spinning machine, comprising: a chain base portion inserted into a tubular shaft so as to be translationally movable; 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
  • a driving gear portion including a plurality of driving gears having a larger diameter toward an axial side;
  • the present invention is characterized in that the chain base portion is moved in the axial direction of the plurality of drive gears in the tubular shaft at the time of shifting from the low speed to the high speed end and at the time of shifting from the high speed end to the low speed, At least two protruding and retracting members are pushed in and pressed outward in the radial direction to move the two drive gears having different numbers of teeth of the driver unit having the one-way clutch pressed against the two protruding and retracting members at the same angular speed, The two driven gears having different number of teeth of the synchronous fisher move at different angular speeds so that the output shaft receives the twisting force and the gear teeth may be broken.
  • the low speed single-side driving gear of the driving gear unit is driven by the driven gear of the driven gear engaged with the low-
  • the gear is adjusted to the angular speed of the driven gear of the driven gear engaged with the high-speed one-side drive gear of the drive gear unit So that the power of the input shaft can be transmitted without interruption to the output shaft at the time of shifting because the one-way clutch does not come into a stepped state.
  • the adjacent protruding and retreating members can be pushed into and pushed outward in the radial direction, so that the power of the input shaft can be directly transmitted to the output shaft Making it possible to transmit while shifting.
  • FIG. 1 is a view showing an automatic transmission according to a first embodiment of the present invention
  • Fig. 2 is a view showing the automatic transmission of Fig. 1 in the engaged state of the engaging clutch
  • FIG. 3 is a view showing an automatic transmission according to a second embodiment of the present invention.
  • Fig. 4 is a view showing an automatic transmission of another embodiment of Fig. 3,
  • FIG. 5 is a view showing an automatic transmission according to another embodiment of FIG. 3,
  • FIG. 6 is a view showing another embodiment of the projecting / retreating member provided in the engaging clutch shown in Fig. 1,
  • FIG. 7 is a view showing an arrangement pattern of through holes formed in the tubular shaft of the engaging clutch shown in Fig. 1, and Fig.
  • FIG. 8 is a view showing another embodiment of the projecting / retreating member provided in the engaging clutch shown in Fig.
  • the automatic transmission 200 includes an input device unit 210 which is a first gear unit rotatably circumscribed by a predetermined distance through a bearing B on a tubular input shaft 10 and is disposed parallel to the input shaft 10 An output gear unit 220 that is fixedly circumscribed to the output shaft 201 and meshed with the input gear unit 210 and an engagement clutch 100 that selectively engages the input gear unit 210 .
  • the input device unit 210 includes a plurality of input gears 40 circumscribed via a one-way clutch C to the bearing B circumscribed by the input shaft 10 and having a larger diameter toward one axial side .
  • the output gear unit 220 includes a plurality of output gears 60 meshed with the plurality of input gears 40 and smaller in diameter in the axial direction.
  • the engagement clutch 100 is configured such that a screw shaft is rotatably inserted into the input shaft 10 through a bearing and the case of the motor M is fixed to the input shaft 10 and rotated together with the input shaft 10 (Not shown in Figs. 1 and 2) fixed to the base (not shown in Figs.
  • a nut-shaped chain base portion 30 fastened to the screw shaft of the ball screw 20 and internally fitted on the input shaft 10 so as to be slidable in an axial direction;
  • a plurality of recessed portions 41 formed on the inner circumferential surface of the inner race C1 of the one-way clutch C of each of the plurality of input gears 40 at predetermined intervals along the circumferential direction;
  • a spacer (42) inserted through the plurality of recessed portions (41) via a spring (S) and elastically moving in the radial direction; And a plurality of recesses (41) of the inner race (C1) of the one-way clutch (C) of each of the plurality of input gears (40)
  • the recessed portion 41 has the enlarged diameter portion 41a and the reduced diameter portion 41a, which communicates with the enlarged diameter portion 41a.
  • the spacer 42 includes a large diameter body 42a which is inscribed in the large diameter hollow section 41a and movable in the radial direction and a small diameter body 42b which is inscribed in the small diameter shaft space section 41b and moves in the radial direction
  • Diameter portion 41b integrally includes a shaft body 42b as small as possible so that a part of the ball 50 can be inserted.
  • the axially shaft body 42b has a radial length that coincides with the inner circumferential surface of the inner race C1 of the one-way clutch C when the protruding member 50 is not pressed,
  • the radially inner end has the same curvature as the inner circumferential surface curvature of the inner race (C1) of the one-way clutch (C).
  • the one-way clutch C is in a stepped state when the inner race C1 of the one-way clutch C rotates in the normal direction and when the inner race C1 of the one-way clutch C rotates in the reverse direction, Way clutch in a stepped state.
  • the diameter of the through hole 11 in the radial direction is smaller than the diameter of the through hole 11 in a state in which the ball 50 is partially inserted and the entirety of the protruding and retracting member 50, And the inner diameter of the inner race (C1) of the one-way clutch (C) is in contact with the outer circumferential surface of the outer race (30) in a state in which the inner race (C1) The inner circumferential surface of the through hole 11 is in sliding contact with the protruding and retracting member 50 like the ball so that the protruding and retreating member 50 like the ball can not escape from the through hole 11.
  • the axially opposite side edges of the chain base 30 are cam surfaces so that the protruding and retracting members 50 such as the ball can smoothly ascend and descend along the cam surface of the wobbler 30, So that the protruding / retracting member 50 can be pressed smoothly without interruption, pressurized, and released.
  • the outer surface of the wedge base portion 30 is a polygonal shape when the inner surface of the input shaft 10 is a polygonal shape. And when the inner surface of the input shaft 10 is circular, the outer surface of the wedge base 30 becomes circular.
  • the axial length of the chain base 30 may be set to be shorter than that of two or more balls in the axial direction in the input shaft at the time of shifting from the low speed to the high speed and at the high speed to the low speed, (50) such as at least two balls which are axially adjacent to each other, that is, a length capable of maintaining the pressing force against the pressing member (50).
  • the wobbler portion 30 having the axial length as described above presses against the protruding and retreating member 50 such as any one ball in the input shaft 10 when it moves within the input shaft 10 for shifting (50, 50), such as at least two balls adjacent to each other, the power of the input shaft (10), which is an input shaft, can be transmitted to the output shaft without any interruption during shifting.
  • the protruding and retreating member 50 such as any one ball in the input shaft 10 when it moves within the input shaft 10 for shifting (50, 50), such as at least two balls adjacent to each other, the power of the input shaft (10), which is an input shaft, can be transmitted to the output shaft without any interruption during shifting.
  • Way clutch (C) that is pressed against the protruding and retreating members (50, 50) such as the two balls when the wobbler portion (30) presses the protruding and retreating members (50,
  • the two output gears 60 and 60 having different numbers of teeth of the output gear unit 220 engaged with the two input gears 40 and 40 move at different angular velocities, Since the one-way clutch C is interposed in each of the plurality of input gears 40 of the input device unit 210, the low gear end side of the input gear unit 210
  • the input gear 40 is connected to the high speed one side input gear 40 of the input device unit 210 by the output gear 60 of the output device unit 220 engaged with the low speed one side input gear 40 of the input device unit 210
  • the rotation of the input shaft 10 so as to match the angular speed of the output gear 60 of the engaged output gear unit 220
  • the low speed short side input gear 40 of the input unit 210 is rotated in the rotating direction of the input shaft 10 because the corresponding one-way
  • the ball screw 20 is a well-known ball screw having a spiral portion 30 coupled to a spiral portion coupled to an output shaft of a motor M and a spindle portion 30 And moves back and forth in the input shaft (10).
  • a cylinder, a linear motor, or the like may be applied instead of the ball screw 20, a cylinder, a linear motor, or the like.
  • the protruding and retreating members 50 like the plurality of balls are spaced apart from each other by a predetermined distance in the axial direction, but the present invention is not limited thereto,
  • a plurality of through holes 11 are formed at portions of the input shaft 10 opposed to the plurality of recessed portions 41 of the one-way clutch C at predetermined intervals in the circumferential direction to form the plurality of through holes 11,
  • the protruding and retracting members 50, such as the plurality of balls may be respectively seated in the through holes.
  • the protruding / retracting member is described and shown as being the protruding / retracting member 50 having a spherical shape in the description of the automatic transmission in the embodiment of the present invention, the present invention is not limited to this and the protruding / And may be replaced with a cylindrical upper portion, a dome-shaped upper portion, or the like which can be in sliding contact with the inner peripheral surface of the inner race C1 of the one-way clutch C while being fitted to the recessed portion 41 instead of the ball
  • the plurality of protruding and retracting members 50 are cylindrical in shape so as to be in sliding contact with the chain base 30, both ends of the cylindrical upper portion have cam surfaces, and in the case of the dome- Has a cam surface.
  • the protruding / retracting member 50 is elastically urged radially inward by the spacer 42, and the through hole 11 is cylindrical But the present invention is not limited to this. As shown in FIG.
  • the diameter in the radial direction of the through hole 11 is smaller than the diameter
  • the penetrating member 50 is partially inserted so that the entirety of the protruding member 50 can not penetrate therethrough so that the penetrating hole has a conical shape so that the penetrating hole 11 slides on the protruding member 50,
  • the size and shape of the projecting / retracting member 50 inserted into the plurality of through holes 11 of the input shaft 10 can be inserted into the plurality of through holes 11, The radial amount It may be given a rounded protrusion.
  • a plurality of balls having diameters different from each other may be inserted into the through-hole 11, and although not shown, the radial outer edge of the protruding / And a ball disposed radially inwardly of the through hole 11, in the radially outward position of the through hole 11.
  • the plurality of through holes 11 formed in the input shaft 10 are formed in a plurality of spirals P1 in a pitch P1 so as to have a plurality of spiral arrangement in the longitudinal direction of the input shaft 10, (Arranged in two in Fig. 7) with the same phase difference in the circumferential direction of the tubular axis (shown by a 180-degree phase shift in Fig. 7) ).
  • the through-holes arranged at regular intervals in the longitudinal direction of the input shaft which is the tubular shaft are formed at the positions of the tubular shafts different from each other in the circumferential direction of the tubular shaft, and the through holes formed in the input shaft are radially expanded
  • the load that the input shaft is repeatedly received by the protruding and retreating member is uniformly transmitted along the longitudinal direction of the input shaft in the circumferential direction of the input shaft and the load received by the protruding and retreating member on the inner circumferential surface side and the outer circumferential surface side of the input shaft So that the strength of the input shaft can be prevented from rapidly lowering.
  • the automatic transmission 200 configured as described above can be operated as follows.
  • the protruding / retreating member 50 is out of the recess 41 in a state in which the wedge 30 does not press the protruding / retreating member 50, No power is transmitted between the input gears 40 having the one-way clutch C and the input shaft 10 in which the projecting / retreating member 50 is not pressed,
  • the protruding member 50 is inserted into the recess 41 by pushing the protruding member 50 outward in the radial direction, the protruding member 50 is forcibly occupied in the recess 41, Any one of the input gears 40 of the plurality of input gears 40 having the one-way clutch C being pressed is integrally coupled with the input shaft 10 so that the power is transmitted therebetween.
  • the axially extending length of the chain base 30 is such that at least two protruding and retracting members adjacent to each other in the axial direction can be contacted with each other, so that the chain base 30 can be moved from the low speed end to the high speed end, (50) in the input shaft (10) at the time of a speed change from a low speed to a low speed and maintains the pressurization to at least two or more adjacent absorptive members (50) in the axial direction
  • the power of the input shaft 10 is transmitted to the output shaft 201 while maintaining the pressure on the other one of the concave / convex members 50 adjacent to the axial direction.
  • the wedge base 30 includes at least two axially adjacent The two input gears 40 and 40 having different numbers of teeth of the input device unit 210 having the one-way clutch C pressed to the two protruding members are maintained at the same angular speed
  • the low speed side input gear 40 of the input gear unit 210 is connected to the low speed side input gear 40 of the input gear unit even when the two output gears 60 and 60 having different numbers of teeth of the meshed output gear unit 220 move at different angular speeds.
  • the output gear 60 of the output gear unit 220 meshed with the input shaft 10 is engaged with the output gear 60 of the output gear unit 220 meshed with the high speed one side input gear 40 of the input gear unit 210.
  • the one-way clutch is not in a stepped state, so that the output shaft 201 receives the twisting force and the gear teeth are not broken, It is possible to transmit the power of the engine 10 to the output shaft 201 without interruption.
  • the input shaft 10 and the output shaft 201 can be increased and decreased without interruption, and when the automatic transmission according to the present embodiment is applied to an apparatus such as a winch or a crane that moves up and down a driven object under gravity, It is possible to reduce the energy by shifting the driving object which is lighter than the set weight, and at the same time, it is possible to provide an action and effect of rapidly moving up and down.
  • the plurality of protruding and retracting members 50 are forcibly inserted into the plurality of recesses 41 of the inner race C1 of the one-way clutch C while being supported by the wobbler 30 If the input gear 40 and the input shaft 10 rotate together and are not supported by the wobbler 30, the input gear 40 and the input shaft 10 are disengaged from the plurality of recesses 41 of the inner race C1 of the one- The input gear 40 or the input shaft 10 is rotated without being disturbed by the protruding and retreating member 50 such as the plurality of balls freely and held in the through hole 11 so that the input gear 40 and the input shaft 40 (10).
  • the output unit may include a one-way clutch and a catching clutch.
  • the input clutch having the smaller diameter among the input gears of the input unit portions interposes the clutch and the one-way clutch.
  • a one-way clutch may be interposed in the output gear of the output gear unit.
  • the direction of the one-way clutch interposed in the output gear of the output gear unit is opposite to the direction of the one-way clutch interposed in the input gear of the input gear unit.
  • the automatic transmission 200 includes a tubular input shaft 10 fixedly inscribed on a driven gear 4 coupled to a drive gear 2 fixedly circumscribed to a drive shaft 1 of a drive motor M1 as a one-
  • An input gear unit 210 which is rotatably circumscribed by a predetermined distance between the input shaft 10 and the bearing B; a tubular output shaft 201 disposed parallel to the input shaft 10 with a bearing interposed therebetween;
  • An input clutch unit 110 selectively engaged with the input gear unit 210, and an output gear unit 220 selectively engaged with the input gear unit 220.
  • the output gear unit 220 is selectively engaged with the input gear unit 210, And an output clutch 120 that engages with the 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 portion 113 that is a nut that is fastened to the screw shaft and is internally engaged with the input shaft 10 so as to be slidable in an axial direction.
  • a plurality of input recessed portions 41 formed on the inner circumferential surface of the inner race 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)
  • 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 wobbling portion 123 that is a nut fastened to an output screw shaft of the output gears 60 and internally engaged with the output shaft 201 so as to be slidable in an axial direction.
  • a plurality of output recesses 61 spaced apart from each other by a predetermined distance; 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 wobbling portion 123 so that a part of the output recessed portion 61 of the plurality of output recessed portions 61 is inserted And an output protruding and retreating member 125 such as a ball.
  • the basic configuration of the input clutch 110 and the output clutch 120 is the same as that of the engaging clutch of the first embodiment.
  • the output worm nut 123 is rotated in the state in which the input wobbler 113 presses the two input / output projecting / contracting members 115 and 115 adjacent to each other in the axial direction to engage the two input gears 40 and 40
  • the two input gears 40 and 40 having different numbers of teeth of the input gear unit 210 having the one-way clutch C pressed against the input and output projecting and contracting members 115 and 115 move at the same angular speed, It is determined that the two output gears 60 and 60 having different numbers of teeth of the input gear unit 220 move at different angular speeds so that the output shaft 201 receives the twisting force and the gear teeth may be broken.
  • Speed low-speed side input gear 40 of the input unit 210 is connected to the low speed side input gear 40 of the input gear unit 210 by the output gear 60 of the output gear unit 220 engaged with the low- Is rotated in the rotational direction of the input shaft (10) at a higher speed than the rotation 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 one- The low speed side input gear 40 of the input unit 210 is rotated in the rotation direction of the input shaft 10.
  • the present invention is not limited to this, and a plurality of the output device units 220 Way 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 input unit section 210 is operated.
  • 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)
  • 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.
  • 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 axial directions by the mode switching means (300) for moving the output base portion and the output base portion.
  • the positions of the input wobbler 113 and the output wobbler 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 wedge portion 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 portion 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, And the output wobbling portion 123 and the output wobbling portion 123 simultaneously And one input gear 40 and an output gear 60 which mate with each other are engaged with any one of the input wedge 113 and the output wedge 123, But may be arranged to have a larger diameter than the diameter of the gear 40 or the other output gear 60.
  • the output shaft 201 is rotated at a speed faster or slower than the rotational speed of the output shaft 201.
  • the output shaft 201 is rotated at a speed that is lower than the rotational speed of the output shaft 201
  • a relative speed difference transfer unit 330 for synchronously moving the input synchronizing portion 113 of the input clutch 110 and the output synchronizing portion 123 of the output engaging clutch 120 axially moves the input shaft 10
  • the output shaft 201 is rotated at a speed faster or slower than the rotational speed of the output shaft 201.
  • the output shaft 201 is rotated at
  • the tuning unit 310 includes a forward drive gear 301 fixedly connected to the drive shaft 1, a reverse oar gear 302 coupled to the forward drive gear 301, And a first planetary gear 304 meshed with the first sun gear 303 and the reverse planetary gear 302.
  • the first sun gear 303 is fixedly engaged with the first planetary gear 304,
  • the relative speed difference generator 320 includes first and second forward driven gears 321 and 322 fixedly circumscribed to the output shaft 201 and an output screw shaft fixedly circumscribed to the output screw shaft 121.
  • a second idle gear 327 rotatably circumscribed by the first idle shaft 324 and meshing with the second forward driven gear 322 via a first intermediate gear 326
  • an output screw shaft starting gear 328 which is fixedly circumscribed to the first idle shaft 324 and meshes with the output screw motion synchronizing gear 323.
  • the relative speed difference generator 320 may selectively include a first stopper 329A that engages the first idle gear 325 on the first idle shaft 324 to rotate or idle the first idle gear 325, And a second stopper 329B that engages the second idle gear 327 with the first idle shaft 324 and rotates or idles them together.
  • the relative speed difference difference transmission portion 2 speed increase / deceleration portion 330 includes third and fourth forward driven gears 331 and 332 which are fixedly circumscribed to the output shaft 201, fixed and inscribed in the first planetary gear 304 A second sun gear 333 meshing with the second planetary gear 306 fixedly circumscribed to the planetary gear shaft 305 and a second sun gear 333 disposed parallel to the output shaft 201 and fixed to the second sun gear 333 A third idle gear 335 rotatably circumscribed by the second idle shaft 334 and meshing with the third forward driven gear 331, And a fourth idle gear 337 rotatably circumscribed by the second intermediate gear 334 and meshing with the fourth forward driven gear 332 via a second intermediate gear 336.
  • the relative speed difference transfer unit 330 may further include a third stopper 339A that selectively engages the third idle gear 335 on the second idle shaft 334 to rotate or idle the third idle gear 335, And a fourth stopper 339B which engages the second idle gear 337 with the second idle shaft 334 and rotates or idles them together.
  • the first sun gear 303 is connected to the input shaft 10 through the gear ratio between the forward drive gear 301, the reverse internal and external ground gear 302, the first planetary gear 304 and the first sun gear 303. ) Can make one revolution in the reverse direction when making one revolution in the reverse direction.
  • the output screw shaft driving gear 323 is configured such that the output screw shaft 121 rotates several times faster or several times slower than the output shaft 201 through the gear ratio with the output screw shaft starting gear 328,
  • the first sun gear 303 is connected to the fourth forward driven gear 332 via the gear ratio between the third forward driven gear 331 and the third idle gear 335 or via the fourth forward driven gear 332, 4 idle gear 337 and through a gear ratio between the second sun gear 333, the second planetary gear 306, the first planetary gear 304 and the first sun gear 303, And can rotate at a speed corresponding to the rotational speed difference between the shaft 121 and the output shaft 201.
  • the output shaft 201 is coupled to the output screw shaft 121 to selectively rotate the output shaft 201 between the output screw shaft 121 and the output shaft 201 so as to rotate the output shaft 201 together,
  • a fifth stopper 351 for rotating the input shaft 10 and a fifth stopper 351 for selectively rotating the input shaft 10, and optionally the input shaft 10 is engaged with the input shaft shaft 111 so that they rotate together,
  • a sixth stopper 352 for turning is provided.
  • the configuration of the fifth stopper 351 is similar to that of the first to fourth stoppers.
  • a plurality of recesses spaced in the circumferential direction are formed on the inner circumferential surface of the output shaft 201,
  • a plurality of through holes are formed in a portion facing the plurality of recessed portions, and a protruding and retreating member projecting in a radial direction is planted in the plurality of through holes,
  • the chain base portion translationally moving by the motion is rotatably circumscribed by the rod 353 so that the chain base portion is forced to be inserted into the recess portion by pressing the protruding and retreating member,
  • the output shaft nut 121 is fixed to the output shaft 201 to prevent the output wrench nut 123 from moving in the axial direction when the mode switching means is not operated And the dragon.
  • the sixth stopper 352 has a structure similar to that of the first to fourth stoppers.
  • the sixth stopper 352 includes a plurality of recesses spaced in the circumferential direction on the inner circumferential surface of the input shaft 10, A plurality of through holes are formed in a portion facing the plurality of recesses, one end of the screw shaft 111 is made into a tubular portion, and a protruding and retreating member projecting in a radial direction is planted in the plurality of through holes, And the wedge base portion is forced to be inserted into the recessed portion by pressing the protruding and retreating member, and the wedge base portion may be configured to be forcedly inserted into the recessed portion, 6
  • the stopper 352 prevents the input wrench nut 113 from moving in the axial direction when the input screw shaft 111 is fixed to the input shaft 10 and the mode switching means is not operated. It acts.
  • the fifth and sixth stoppers 351 and 352 may be translationally moved by the rods of the different cylinders, and may be provided on the two rods provided on one cylinder, as shown in FIGS. 3 to 4 It is possible.
  • the first to fourth stoppers 329A, 329B, 339A, and 339B have first and second idle shafts 324,
  • a known clutch engaged to selectively engage gears rotatably circumscribed on the first and second idle shafts 324 and 334 while moving forward or backward on the first and second idle shafts 334 and 334, 334 are engaged with the first and second idle shafts 324, 334 to selectively engage gears rotatably circumscribed by the first and second idle shafts 324, 334 while moving back and forth
  • the automatic transmission of the second embodiment configured as described above can be operated as follows. In the following description, the operation will be described assuming that the forward direction is the clockwise direction and the reverse direction is the counterclockwise direction, the input screw shaft has the left screw thread, and the output screw shaft has the right screw thread.
  • the input shaft portion 113 and the input screw shaft 111 rotate in the opposite directions together at the same speed by the input shaft 10 and the output shaft portion 123 and the output screw shaft
  • the input and output chokes 113 and 123 are in a no-load state.
  • the fifth and sixth stoppers 351 and 352 rotate the output shaft 201 and the output screw shaft 121 are fixed to each other and the input shaft 10 and the input screw shaft 111 are fixed to each other so that the output wedge 123 and the input wedge 113 are not moved in the axial direction And can be held in position without fail.
  • the drive shaft 1 rotates once in the forward direction
  • the input shaft 10 and the input wobbler 113 are rotated together in the opposite direction, for example, and the output shaft 201 and the output shaft-
  • the output threaded spur gear 323 is engaged with the output screw shaft starting gear 328 at a gear ratio of 2;
  • the first forward driven gear 322 is rotated 18 times in the reverse direction by the second forward driven gear 322 rotating 9 times so that nine rotational differences are generated between the output worm 123 and the output screw shaft 121,
  • the output wedge 123 is moved by a distance A in the unwinding direction (the left direction in Fig.
  • the forward drive gear 301 moves the output wedge 123 in the reverse direction
  • the first planetary gear 304 is fixed once and the first sun gear 303 and the input screw shaft 111 are rotated once to rotate the input shaft 10
  • the fourth forward driven gear (the third forward driven gear) is rotated nine times in the forward direction by the output shaft 201 in a state in which one rotation of the input screw shaft 111 is canceled by one rotation and the input screw shaft 111 is in a no- 332) transmits the gear ratio between the fourth forward driven gear 332, the second intermediate gear 336 and the fourth idle gear 337
  • the first sun gear 303 is rotated nine times in the forward direction so that the input screw shaft 111 has the left screw thread and the input worm shaft portion 113 is rotated by a distance A in the releasing direction
  • the input wobbler 113 and the output wobbler 123 are moved synchronously to the left side along the same axial line by the speed difference between the output wobbler 123 and the output screw shaft 121 do.
  • the forward drive gear 301 moves the reverse output shaft
  • the first planetary gear 304 is fixed once and the first sun gear 303 and the input screw shaft 111 are rotated once to rotate the input shaft 10
  • a third forward driven gear rotated nine times in the forward direction by the output shaft 201 in a state in which one rotation of the input screw shaft 111 is canceled by one rotation and the input screw shaft 111 is in a no- 331 rotate the first sun gear 303 in the reverse direction nine times through the gear ratio between the third idle gears 335
  • the input wedge 113 is moved by a distance A in the fastening direction (rightward in Fig. 14), so that the input wedge 113 and the output wedge 113,
  • the bases 123 move synchronously with each other along the same axial length by the speed difference between the output wedge 123 and the output screw shaft 121 to the right.
  • the speed of the output screw shaft 121 is two times faster than the speed of the output wax 123.
  • the speed can be doubled or any multiple can be obtained, Various conditions can be satisfied.
  • the output screw shaft has a right screw thread and the input screw shaft has a left screw thread.
  • the present invention is not limited to this, and the output screw shaft may have a left-
  • the screw shaft may have a right-hand thread, or both may have the same thread.
  • the automatic transmission according to the second embodiment configured as described above can arrange gears having different gear ratios in an axial direction in an infinite manner, thereby providing an operational effect of providing numerous speed ratios.
  • the mode switching means 300 of the automatic transmission according to the second embodiment configured as described above may be configured as another embodiment as follows.
  • the mode switching means 300 of the automatic transmission is provided with a tuning means for turning the input screw shaft 111 in the rotational direction and the rotational speed such as the rotational direction and the constant speed of the input shaft 10,
  • the tuning unit 310 includes a forward drive gear 301 fixedly attached to the drive shaft 1 as in the second embodiment, a reverse oar gear 302 meshing with the forward drive gear 301, A first sun gear 303 fixedly circumscribed to the shaft 111 and a first planetary gear 304 meshing with the first sun gear 303 and the reverse outer gear 302.
  • the relative speed difference generator 320 includes a first forward driven gear 321 fixedly circumscribed to the output shaft 201, an output screw driven gear 323 fixedly connected to the output screw shaft 121, A first idle shaft 324 disposed parallel to the output shaft 201 and a second idle shaft 324 rotatably circumscribed by the first idle shaft 324 via a bearing and meshing with the first forwardly- An idle gear 325 and an output screw shaft starting gear 328 rotatably circumscribed by the first idle shaft 324 via a bearing and meshing with the output screw driven gear 323.
  • the relative speed difference generator 320 may selectively include a first stopper 329A that engages the first idle gear 325 on the first idle shaft 324 to rotate or idle the first idle gear 325, And a seventh stopper 329 that engages the output screw shaft starting gear 328 with the first idle shaft 324 and rotates or idles them together.
  • the linkage unit 340 includes a third forward driven gear 331 fixedly circumscribed to the output shaft 201 and a third forward driven driven gear 331 fixedly circumscribed to the planetary gear shaft 305 fixedly inscribed on the first planetary gear 304 A second idle gear 333 meshed with the second planetary gear 306 and a second idle shaft 334 disposed parallel to the output shaft 201 and fixedly inscribed in the second sun gear 333, A third idle gear 335 rotatably circumscribed by a second idle shaft 334 via a bearing and meshing with the third forward driven gear 331 and a third idle gear 335 rotatably circumscribed by the second idle shaft 334 And a fourth idle gear 337 meshing with the fourth forward driven gear 332 via a second intermediate gear 336.
  • the interlocking portion 340 may optionally include a third stopper 339A that engages the third idle gear 335 on the second idle shaft 334 to cause them to rotate or idle together, And a fourth stopper 339B that engages the second idle gear 337 on the idle shaft 334 and rotates or idles them together.
  • the first sun gear 303 is connected to the input shaft 10 through the gear ratio between the forward drive gear 301, the reverse internal and external ground gear 302, the first planetary gear 304 and the first sun gear 303. ) Can make one revolution in the reverse direction when making one revolution in the reverse direction.
  • the output screw shaft driving gear 323 can rotate the output screw shaft 121 several times faster or several times slower than the output shaft 201 through the gear ratio with the output screw shaft starting gear 328.
  • the first sun gear 303 is connected to the second sun gear 333 via the gear ratio between the fourth forward driven gear 332, the second intermediate gear 336 and the fourth idler gear 337,
  • the output shaft 201 rotates at a speed corresponding to the rotational speed difference between the output screw shaft 121 and the output shaft 201 through the gear ratio between the planetary gear 306, the first planetary gear 304 and the first sun gear 303 .
  • the first sun gear 303 is connected to the third forward gear 331 through the third forward gear 331 and the third idler gear 335 via the gear ratio between the third forward gear 331 and the third idler gear 335, 1 planetary gear 304 and the first sun gear 303 at the same rotational speed as that of the output shaft 201.
  • the input screw shaft 111 has a right screw thread
  • the output screw shaft 121 has a right screw thread as in the second embodiment.
  • the mode switching means 300 of the automatic transmission of the other embodiment is provided with an eighth stopper (not shown) for preventing the output screw shaft 121 or the output screw moving gear 323 from selectively rotating, 360).
  • the eighth stopper 360 when the eighth stopper 360 is magnetized, the eighth stopper 360 is engaged with the output screw motion synchronizing gear 323 so as not to rotate the output screw synchronizing gear 323 and is not magnetized
  • the output screw baseball gear 323 may be disengaged from the output screw baseball gear 323 so that the output screw baseball gear 323 may be rotated.
  • the remaining configuration of the mode switching means 300 of the automatic transmission of the other embodiment is the same as that of the mode switching means 300 of the second embodiment.
  • the automatic transmission of another embodiment configured as above can be operated as follows. In the following description, the operation will be described assuming that the forward direction is the clockwise direction and the reverse direction is the counterclockwise direction, the input screw shaft shown with the left-hand spiral in FIG. 5 has a right-hand thread and the output screw shaft has a right-hand thread.
  • the output wedge nut 123 and the input wedge nut 113 can not be moved in the axial direction and are reliably held in place.
  • the fifth and sixth stoppers 351 and 352 and the first, fourth and seventh stoppers 329A and 339B and 329 are in the non-engaged state and the third stopper 339A and the eighth stopper 360 ) Is in a stuck state
  • the reverse-direction external gear 302 is rotated once by the forward-direction drive gear 301, and the first planetary gear 304 is once fixed
  • the first sun gear 303 and the input screw shaft 111 rotate once, and the input shaft 10
  • the gear 331 is connected to the second sun gear 333, the second planetary gear 306 and the first planetary gear 304 via the gear ratio between the third forward driven gear 331 and the third idle gear 335
  • the first sun gear 303 is rotated nine times in the reverse direction through the gear ratio between the first sun gear 303 and the first sun gear 303 so that the input shaft 111 has a right-
  • the input wobbler 113 and the output wobbler 123 are synchronously moved to the left side together by the output wobbler 123 and the output
  • the fifth and sixth stoppers 351 and 352 and the third stopper 339A and the eighth stopper 360 are in the non-engagement state and the first, fourth and seventh stoppers 329A, 339B and 329 ) Is in a stuck state
  • the first planetary gear 304 is fixed once and the first sun gear 303 and the input screw shaft 111 rotate once so that the rotation of the input shaft 10
  • One fourth rotation of the input shaft of the input shaft is performed by one rotation and the fourth forward driven gear rotated nine times in the forward direction by the output shaft 201 in a state in which the input shaft is in a no- 332) transmits the gear ratio between the fourth forward driven gear 332, the second intermediate gear 336 and the fourth idle gear 337
  • the first sun gear 303 is rotated in the forward direction 9 times through the gear ratio between the second sun gear 333, the second planetary gear 306, the first planetary gear 304 and the first sun gear 303,
  • the input wedge 113 is moved by a distance A in the fastening direction (right direction in Fig. 16), so that the input wedge 113 and the input wedge 113 are moved
  • the output wobbling portion 123 moves synchronously with the output wobbling portion 123 and the output worm shaft
  • the output screw shaft 121 has a speed two times faster than the output worm 123, but it can be doubled or any other multiple, so that it is not industrially restricted Various conditions can be satisfied.
  • the output screw shaft has a right screw thread and the input screw shaft has a right screw thread.
  • the shaft may have a left-hand thread and the input screw shaft may have a right-hand thread, or the output screw shaft may have a right-hand thread and the input screw shaft may have a left-hand thread.
  • the automatic transmission of the second embodiment and another embodiment of the present invention is configured such that 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 gear transmits the driving force to the driven shaft and the other driven gears are idle or held in position so that the load in the rotational direction by the weight of the other driven gear is not given to the driven shaft,
  • the drive chain base and the driven chain base can be synchronously moved by their own power sources while reducing the manufacturing cost and maintenance cost by enabling the transmission to be transmitted to the driven shaft with a drive force smaller than that of the automatic transmission of the first embodiment
  • Mode switching means for shifting in the axial direction at the same speed makes it possible to freely adjust the gear ratio, There are a variety to be increased.

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  • Engineering & Computer Science (AREA)
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  • Structure Of Transmissions (AREA)

Abstract

The present invention relates to an automatic transmission and, more particularly, to an automatic transmission capable of a seamless gear change using an engaging clutch and a unidirectional clutch and capable of infinitely increasing the gear ratio without imparting a shock to the engaging clutch and the unidirectional clutch during a gear change.

Description

자동 변속기Automatic transmission
본 발명은, 자동 변속기에 관한 것으로서, 보다 상세하게는 물림클러치와 일방향클러치를 이용하여 끊김이 없이 변속하되 변속시에 물림클러치와 일방향클러치에 충격이 부여되지 않으면서도 무한이 변속단수를 증가시킬 수 있는 자동 변속기에 관한 것이다.BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission, and more particularly, to an automatic transmission that is capable of continuously shifting without engagement using a retaining clutch and a one-way clutch, The present invention relates to an automatic transmission equipped with an automatic transmission.
자동 변속기는 운전자의 조작에 의하지 않고 자동적으로 기어 비가 선택되어 달리는 속도에 따라 기어가 자동으로 조작되는 장치이다.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.
이 자동 변속기는 유체 클러치나 밴드 또는 디스크 판을 작동시켜 자동적으로 기어 비를 선택할 수 있는 것으로 되어 있다.This automatic transmission is designed so that the gear ratio can be automatically selected by activating the fluid clutch, band or disc plate.
통상적으로 자동 변속기에는 선기어, 유성기어, 링기어 및 유성기어캐리어를 포함하고 있는 라비뇨식 또는 심프슨식 유성기어유닛 등이 있다.Typically, automatic transmissions include Ravigneaux or Simpson planetary gear units that include sun gear, planetary gears, ring gears, and planet gear carriers.
이 유성기어유닛은 선기어, 유성기어, 링기어 및 유성기어캐리어 각각을 입력축과 출력축에 선택적으로 물리게 하는 복잡한 구조의 클러치가 필요되어 제조단가가 높다고 하는 문제점과 변속시에 순간적으로 클러치에 의한 물림해제가 발생되어 입력축의 동력이 출력축에 순간적으로 절달되지 않아, 구동대상물이 중력을 받고 있는 경우에는 구동대상물이 자유낙하될 수 있다고 하는 문제점을 가진다. 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.
또한, 종래의 자동변속기는 복수개의 변속단수를 제공할 수 있지만 무한이 많은 변속단수를 제공할 수 없다고 하는 문제점을 가진다.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.
이러한 문제점을 해결하기 위한 자동 변속기가 한국등록특허 제10-102968호에 개시되어 있다.An automatic transmission for solving such a problem is disclosed in Korean Patent No. 10-102968.
상기 개시된 자동 변속기는 일측으로 갈 수록 직경이 작아지는 복수개의 구동기어를 일방향클러치를 개재하여 입력축에 외접시키고, 이들 구동기어와 맞물리되 일측으로 갈 수록 직경이 커지는 복수개의 피동기어를 출력축에 미끄럼접촉시켜 외접시키고, 상기 출력축에 원심력에 의해 상기 복수개의 피동기어의 내주면과 접촉하는 복수개의 접촉가압부재를 반경방향으로 이동가능하게 장착하고, 상기 복수개의 접촉가압부재들 중 선택적으로 이웃하는 2개의 접촉가압부재를 선택적으로 지지하기 위해 상기 출력축 내에서 병진부에 의해 왕복이동되는 지지유닛의 로더를 포함하고서, 동력전달의 끊어짐 없이 입력축에서 출력축에 동력을 변속하면서 전달할 수 있는 것으로 되어 있다.The automatic transmission includes a plurality of drive gears that are smaller in diameter toward one side than the other, and a plurality of driven gears that are meshed with the drive gear and increase in diameter toward the other side via a one- 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.
하지만, 상기 개시된 자동변속기는 원심력에 의해 상기 복수개의 접촉가압부재가 반경바깥방향으로 벌어져야만 상기 지지유닛이의 로더가 상기 복수개의 접촉가압부재 중 어느 두개의 접촉가압부재에 사이로 들어가 상기 2개의 접촉가압부재를 지지하여 상기 두개의 접촉가압부재로 하여금 상기 복수개의 피동기어중 해당 2개의 피동기어와 접촉가압하게 하여 구동기어에서 전달되는 동력을 해당 2개의 피동기어에 전달하여 변속하여서 출력축에 전달할 수 있지만, 만약, 출력축이 회전되지 않아 상기 복수개의 접촉가압부재들에 원심력이 발생되지 않은 상태, 예를 들면, 상기 지지유닛의 로더가 중립위치에 있는 상태나, 입력축이 정지된 상태에서는, 상기 복수개의 접촉가압부재들 중 윗쪽에 배치된 복수개의 접촉가압부재들이 중력에 의해 반경안쪽방향으로 내려오게 되어, 아무리 상기 입력축을 재가동하여도 피동기어들이 헛돌게 되어 입력축의 동력을 출력축에 전달할 수 없게 되고, 더욱이 지지유닛의 로더의 좌우이동이 중력에 의해 반경안쪽방향으로 내려온 복수개의 접촉가압재들에 의해 가로막혀 이웃하는 접촉가압부재들 사이로 진입될 수 없어서, 변속도 불가능하여, 항상 상기 복수개의 접촉가압부재들에 원심력을 부여하기 위해 입력축을 가동하여 피동축을 구동하여만 하고, 중립상태의 구현도 불가능하다는 문제점을 가지며, 피동기어의 내주면에 복수개의 요부가 있어서 원심력에 의해 접촉가압부재와 요부간에 부딪침이 생겨 소음이 발생된다고 하는 문제점을 가진다.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.
본 발명은 상기된 문제점을 해결하는 것에 과제를 가진다.The present invention has a problem in solving the above-mentioned problems.
본 발명은, 관형축에 병진운동가능하게 삽입된 쇄기부; 상기 관형축에 베어링을 개재하여 일정 간격 이격되어 회전가능하게 외접된 복수개의 일방향클러치를 각각 개재하여 외접되어 있고 상기 일방향클러치의 인너레이스 내주면에 둘레방향을 따라 일정 간격 이격되어 복수개의 요부가 형성되어 있고, 축선방향 일측으로 갈수록 직경이 큰 복수개의 구동기어를 포함하는 구동기어부; 상기 복수개의 구동기어와 마주하는 관형축의 부위에 축선방향으로 일정 간격을 두고서 형성된 복수개의 관통구멍에 각각 방사상 안쪽 부위가 안착되어 선택적으로 상기 쇄기부에 의해 반경바깥방향으로 밀어져서 가압을 받게 되면 상기 복수개의 요부 중 마주하는 요부에 일부가 삽입되는 복수개의 볼과 같은 출몰부재, 및 출력축에 고정적으로 외접되어 상기 복수개의 구동기어와 치합되며 축선방향 일측으로 갈수록 직경이 작은 복수개의 피동기어를 포함하는 피동기어부를 포함하되, 상기 쇄기부의 축선방향 길이가 축선방향으로 인접한 적어도 2개의 출몰부재를 접촉할 수 있는 길이를 갖는 자동변속기를 제공함으로써 상기 과제를 해결할 수 있다.The present invention relates to a spinning machine, comprising: a chain base portion inserted into a tubular shaft so as to be translationally movable; 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 A driving gear portion including a plurality of driving gears having a larger diameter toward an axial side; When a radial inner portion is seated in a plurality of through holes formed at a certain interval in the axial direction at the portions of the tubular shafts facing the plurality of driving gears and is selectively pushed outward in the radial direction by the chord base portion, And a plurality of driven gears fixedly circumscribed to the output shaft and engaged with the plurality of driving gears and having a smaller diameter toward one axial side in the axial direction, The present invention can solve the above problems by providing an automatic transmission including a driven gear portion, the axial length of the chain base portion being capable of contacting at least two protruding and retracting members axially adjacent to each other.
본 발명은, 상기와 같은 과제해결수단에 의해 쇄기부가 저속단에서 고속단으로의 변속시에 그리고 고속단에서 저속으로의 변속시에 상기 관형축 내에서 복수개의 구동기어중 축선방향으로 이웃하는 적어도 2개 이상의 출몰부재를 밀고 들어가서 반경바깥방향으로 밀어내어 가압하여, 상기 2개의 출몰부재에 가압된 일방향클러치를 가진 구동기어부의 잇수가 다른 2개의 구동기어가 동일한 각속도로 운동하여 이들에 맞물린 피동기어부의 잇수가 다른 2개의 피동기어가 상이한 각속도운동하여서 출력축이 뒤틀림력을 받아서 기어이빨이 파손될 수 있지만, 구동기어부의 저속단측 구동기어가 구동기어부의 저속단측 구동기어에 맞물린 피동기어부의 피동기어에 의해 구동기어부의 고속단측 구동기어에 맞물린 피동기어부의 피동기어의 각속도에 맞출 수 있도록 관형부의 회전보다 관형부의 회전방향에서 고속으로 회전되게 되어 해당 일방향클러치가 걸음상태가 되지 않기 때문에, 변속시에 입력축의 동력을 끊김없이 출력축에 전달하는 것이 가능하게 된다.The present invention is characterized in that the chain base portion is moved in the axial direction of the plurality of drive gears in the tubular shaft at the time of shifting from the low speed to the high speed end and at the time of shifting from the high speed end to the low speed, At least two protruding and retracting members are pushed in and pressed outward in the radial direction to move the two drive gears having different numbers of teeth of the driver unit having the one-way clutch pressed against the two protruding and retracting members at the same angular speed, The two driven gears having different number of teeth of the synchronous fisher move at different angular speeds so that the output shaft receives the twisting force and the gear teeth may be broken. However, the low speed single-side driving gear of the driving gear unit is driven by the driven gear of the driven gear engaged with the low- The gear is adjusted to the angular speed of the driven gear of the driven gear engaged with the high-speed one-side drive gear of the drive gear unit So that the power of the input shaft can be transmitted without interruption to the output shaft at the time of shifting because the one-way clutch does not come into a stepped state.
또한, 본 발명은 쇄기부가 입력축의 정지시에도, 중립위치에 위치되어 있어도, 이웃하는 출몰부재를 밀고 들어가서 반경바깥방향으로 밀어내어 가압할 수 있기 때문에, 어느 상황에서도 바로 입력축의 동력을 출력축에 변속하면서 전달하는 것을 가능하게 한다.Further, even when the chain base portion is positioned at the neutral position even when the input shaft is stopped, the adjacent protruding and retreating members can be pushed into and pushed outward in the radial direction, so that the power of the input shaft can be directly transmitted to the output shaft Making it possible to transmit while shifting.
도 1은 본 발명에 따른 실시예1의 자동 변속기를 물림클러치의 비물림 상태에서 도시한 도면, Brief Description of Drawings Fig. 1 is a view showing an automatic transmission according to a first embodiment of the present invention,
도 2는 도 1의 자동 변속기를 물림클러치의 물림상태에서 도시한 도면,Fig. 2 is a view showing the automatic transmission of Fig. 1 in the engaged state of the engaging clutch,
도 3은 본 발명에 따른 실시예2의 자동 변속기를 도시한 도면, 3 is a view showing an automatic transmission according to a second embodiment of the present invention,
도 4는 도 3의 다른 실시예의 자동 변속기를 도시한 도면, Fig. 4 is a view showing an automatic transmission of another embodiment of Fig. 3,
도 5은 도 3의 또 다른 실시예의 자동 변속기를 도시한 도면, 5 is a view showing an automatic transmission according to another embodiment of FIG. 3,
도 6은 도 1의 물림클러치에 구비된 출몰부재의 다른 실시예를 도시한 도면, 6 is a view showing another embodiment of the projecting / retreating member provided in the engaging clutch shown in Fig. 1,
도 7은 도 1의 물림클러치의 관형축에 형성된 관통구멍의 배열 패턴을 도시한 도면, 및7 is a view showing an arrangement pattern of through holes formed in the tubular shaft of the engaging clutch shown in Fig. 1, and Fig.
도 8은 도 1의 물림클러치에 구비된 출몰부재의 또 다른 실시예를 도시한 도면.8 is a view showing another embodiment of the projecting / retreating member provided in the engaging clutch shown in Fig.
(실시예1)(Example 1)
이하, 본 발명에 따른 실시예의 자동 변속기가 도 1 및 도 2를 참조하여 상세히 설명될 것이다.Hereinafter, an automatic transmission according to an embodiment of the present invention will be described in detail with reference to Figs. 1 and 2. Fig.
도 1에는 자동 변속기가 부호 200으로서 지시되어 있다.1, the automatic transmission is indicated by reference numeral 200. In Fig.
상기 자동 변속기(200)는 관형의 입력축(10)에 베어링(B)을 개재하여 일정 간격 이격되어 회전가능하게 외접된 제1기어부인 입력기어부(210), 상기 입력축(10)에 대하여 평행하게 배치된 출력축(201)에 고정적으로 외접되어 상기 입력기어부(210)와 맞물리는 제2기어부인 출력기어부(220), 및 상기 입력기어부(210)에 선택적으로 물림하는 물림클러치(100)를 포함하고 있다. The automatic transmission 200 includes an input device unit 210 which is a first gear unit rotatably circumscribed by a predetermined distance through a bearing B on a tubular input shaft 10 and is disposed parallel to the input shaft 10 An output gear unit 220 that is fixedly circumscribed to the output shaft 201 and meshed with the input gear unit 210 and an engagement clutch 100 that selectively engages the input gear unit 210 .
상기 입력기어부(210)는 상기 입력축(10)에 외접된 상기 베어링(B)에 일방향 클러치(C)를 개재하여 외접되어 축선방향 일측으로 갈수록 직경이 큰 복수개의 입력기어(40)를 포함하고 있다. The input device unit 210 includes a plurality of input gears 40 circumscribed via a one-way clutch C to the bearing B circumscribed by the input shaft 10 and having a larger diameter toward one axial side .
상기 출력기어부(220)는 상기 복수개의 입력기어(40)와 각각 맞물리되 상기 축선방향 일측으로 갈 수록 직경이 작은 복수개의 출력기어(60)를 포함하고 있다. The output gear unit 220 includes a plurality of output gears 60 meshed with the plurality of input gears 40 and smaller in diameter in the axial direction.
상기 물림클러치(100)는 상기 입력축(10)에 베어링을 개재하여 나사축이 회전가능하게 삽입되어 있고 모터(M)의 케이스가 입력축(10)에 고정되어 상기 입력축(10)과 함께 회전되거거나(도 1 및 도 2에 도시됨) 또는 도시되지 않은 베이스에 고정되어 상기 입력축(10)과 함께 회전되지 않는(도 1 및 도 2에 도시되지 않음) 볼스크류(20); 볼스크류(20)의 나사축에 체결되어 상기 입력축(10)에 축선방향으로 미끄럼이동가능하게 내접된 너트형의 쇄기부(30); 상기 복수개의 입력기어(40) 각각의 일방향 클러치(C)의 인너레이스(C1)의 내주면에 둘레방향을 따라 일정 간격 이격되어 형성된 복수개의 요부(41); 상기 복수개의 요부(41)에 스프링(S)을 개재하여 삽입되어 탄성적으로 반경방향으로 이동하는 스페이서(42); 및 상기 복수개의 입력기어(40) 각각의 일방향 클러치(C)의 인너레이스(C1)의 상기 복수개의 요부(41)와 마주하는 입력축(10)의 부위에 축선방향으로 일정 간격을 두고서 형성된 복수개의 관통구멍(11)에 방사상 안쪽 부위가 삽입 안착되어 상기 쇄기부(30)에 의해 선택적으로 반경바깥방향으로 밀어져서 가압을 받게 되면 상기 스페이서(42)를 반경바깥방향으로 밀어서 상기 복수개의 요부(41) 중 마주하는 요부(41)에 일부가 삽입되는 볼과 같은 출몰부재(50)를 포함하고 있다.The engagement clutch 100 is configured such that a screw shaft is rotatably inserted into the input shaft 10 through a bearing and the case of the motor M is fixed to the input shaft 10 and rotated together with the input shaft 10 (Not shown in Figs. 1 and 2) fixed to the base (not shown in Figs. 1 and 2) or not shown and not rotated together with the input shaft 10; A nut-shaped chain base portion 30 fastened to the screw shaft of the ball screw 20 and internally fitted on the input shaft 10 so as to be slidable in an axial direction; A plurality of recessed portions 41 formed on the inner circumferential surface of the inner race C1 of the one-way clutch C of each of the plurality of input gears 40 at predetermined intervals along the circumferential direction; A spacer (42) inserted through the plurality of recessed portions (41) via a spring (S) and elastically moving in the radial direction; And a plurality of recesses (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 through hole 11 and is selectively pushed outward in the radial direction by the wobbling portion 30 to be pressed, the spacer 42 is pushed outward in the radial direction so that the plurality of recesses 41 And a protruding and retracting member 50 such as a ball into which the recessed portion 41 is partially inserted.
상기 요부(41)는 도 1 및 도 2의 확대도(요부를 축선방향에서 본 단면도)에 도시된 바와 같이, 확경공간부(41a)와 그리고 상기 확경공간부(41a)와 유통하는 축경공간부(41b)를 포함하고 있고, 그리고 상기 스페이서(42)는 상기 확경공간부(41a)에 내접되어 반경방향으로 이동가능한 확경체(42a)와 상기 축경공간부(41b)에 내접되어 반경방향으로 이동가능한 축경체(42b)을 일체로 포함하고 있으며, 상기 축경공간부(41b)는 상기 볼(50)의 일부가 삽입될 수 있는 크기를 가지고 있다.As shown in the enlarged view of FIG. 1 and FIG. 2 (the cross-sectional view of the recessed portion viewed from the axial direction), the recessed portion 41 has the enlarged diameter portion 41a and the reduced diameter portion 41a, which communicates with the enlarged diameter portion 41a. And the spacer 42 includes a large diameter body 42a which is inscribed in the large diameter hollow section 41a and movable in the radial direction and a small diameter body 42b which is inscribed in the small diameter shaft space section 41b and moves in the radial direction Diameter portion 41b integrally includes a shaft body 42b as small as possible so that a part of the ball 50 can be inserted.
상기 축경체(42b)는 상기 출몰부재(50)에 가압을 받지 않을 때 일방향클러치(C)의 인너레이스(C1)의 내주면과 일치되는 반경방향 길이를 가지고 있고, 그리고 상기 축경체(42b)의 반경방향 안쪽 단부는 상기 일방향클러치(C)의 인너레이스(C1)의 내주면 곡률과 같은 곡률로 되어 있다.The axially shaft body 42b has a radial length that coincides with the inner circumferential surface of the inner race C1 of the one-way clutch C when the protruding member 50 is not pressed, The radially inner end has the same curvature as the inner circumferential surface curvature of the inner race (C1) of the one-way clutch (C).
상기 일방향클러치(C)는 상기 일방향클러치(C)의 인너레이스(C1)가 정방향으로 회전할 시에 걸음상태에 있고 상기 일방향클러치(C)의 인너레이스(C1)가 역방향으로 회전할 시에 비걸음상태에 있는 일방향클러치이다.Wherein the one-way clutch C is in a stepped state when the inner race C1 of the one-way clutch C rotates in the normal direction and when the inner race C1 of the one-way clutch C rotates in the reverse direction, Way clutch in a stepped state.
상기 관통구멍(11)의 반경방향 안쪽의 구경이 상기 볼(50)이 일부만 삽입되고 상기 볼과 같은 출몰부재(50) 전체가 관통될 수 없는 크기로 되어 있는 상태에서, 상기 관통구멍(11)은 원통형으로 되어 상기 볼과 같은 출몰부재(50)와 미끄럼접촉하고 있으며, 상기 일방향클러치(C)의 인너레이스(C1)의 내경은 상기 쇄기부(30)에 의해 가압을 받지 않은 상태에서 인너레이스(C1)의 내주면이 상기 볼과 같은 출몰부재(50)와 미끄럼접촉하여 상기 관통구멍(11)에서 상기 볼과 같은 출몰부재(50)가 빠져나올 수 없는 크기로 되어 있다.The diameter of the through hole 11 in the radial direction is smaller than the diameter of the through hole 11 in a state in which the ball 50 is partially inserted and the entirety of the protruding and retracting member 50, And the inner diameter of the inner race (C1) of the one-way clutch (C) is in contact with the outer circumferential surface of the outer race (30) in a state in which the inner race (C1) The inner circumferential surface of the through hole 11 is in sliding contact with the protruding and retracting member 50 like the ball so that the protruding and retreating member 50 like the ball can not escape from the through hole 11. [
상기 쇄기부(30)의 축선방향 양측 테두리는 캠면으로 되어 있어서, 상기 볼과 같은 출몰부재(50)가 부드럽게 상기 쇄기부(30)의 캠면을 타고 올라가고 내려올 수 있어서, 상기 적어도 하나의 볼과 같은 출몰부재(50)를 끊김없이 부드럽게 밀어서 가압하고 빠져서 가압해제할 수 있게 되어 있다. The axially opposite side edges of the chain base 30 are cam surfaces so that the protruding and retracting members 50 such as the ball can smoothly ascend and descend along the cam surface of the wobbler 30, So that the protruding / retracting member 50 can be pressed smoothly without interruption, pressurized, and released.
또한 쇄기부(30)는 상기 입력축(10)의 내면에 형상적으로 끼워맞춤될 수 있는 외면형상을 가지고 있다, 즉, 상기 입력축(10)의 내면이 다각형이면 쇄기부(30)의 외면이 다각형이고, 상기 입력축(10)의 내면이 원형이면 쇄기부(30)의 외면이 원형이 된다. In other words, if the inner surface of the input shaft 10 is a polygonal shape, the outer surface of the wedge base portion 30 is a polygonal shape when the inner surface of the input shaft 10 is a polygonal shape. And when the inner surface of the input shaft 10 is circular, the outer surface of the wedge base 30 becomes circular.
또한, 상기 쇄기부(30)의 축선방향 길이는 저속단에서 고속단으로의 변속시에 그리고 고속단에서 저속으로의 변속시에 상기 입력축 내에서 축선방향으로 이웃하는 2개 이상의 볼과 같은 출몰부재(50)에 대한 가압을 유지할 수 있는 길이를, 즉, 축선방향으로 인접한 적어도 2개의 볼과 같은 출몰부재(50)를 접촉할 수 있는 길이를 가지고 있다.Further, the axial length of the chain base 30 may be set to be shorter than that of two or more balls in the axial direction in the input shaft at the time of shifting from the low speed to the high speed and at the high speed to the low speed, (50) such as at least two balls which are axially adjacent to each other, that is, a length capable of maintaining the pressing force against the pressing member (50).
상기와 같은 축선방향 길이를 가진 상기 쇄기부(30)는 변속을 위해 상기 입력축(10) 내에서 이동할 시에 상기 입력축(10) 내에서 어느 하나의 볼과 같은 출몰부재(50)에 대하여 가압을 하거나 또는 이웃하는 적어도 2개의 볼과 같은 출몰부재(50, 50)에 대하여 가압을 하기 때문에, 변속시에 입력축인 입력축(10)의 동력을 끊김없이 출력축에 전달하는 것이 가능하게 된다.The wobbler portion 30 having the axial length as described above presses against the protruding and retreating member 50 such as any one ball in the input shaft 10 when it moves within the input shaft 10 for shifting (50, 50), such as at least two balls adjacent to each other, the power of the input shaft (10), which is an input shaft, can be transmitted to the output shaft without any interruption during shifting.
상기 쇄기부(30)가 2개의 볼과 같은 출몰부재(50, 50)를 가압하고 있으면, 상기 2개의 볼과 같은 출몰부재(50, 50)에 가압된 일방향클러치(C)를 가진 입력기어부(210)의 잇수가 다른 2개의 입력기어(40, 40)가 동일한 각속도로 운동하여 이들에 맞물린 출력기어부(220)의 잇수가 다른 2개의 출력기어(60, 60)가 상이한 각속도운동하여서 출력축(201)이 뒤틀림력을 받아서 기어 이빨이 파손될 수 있다고 판단되지만, 상기 입력기어부(210)의 복수개의 입력기어(40) 각각에 일방향클러치(C)가 개재되어 있기 때문에, 입력기어부(210)의 저속단측 입력기어(40)는, 입력기어부(210)의 저속단측 입력기어(40)에 맞물린 출력기어부(220)의 출력기어(60)에 의해, 입력기어부(210)의 고속단측 입력기어(40)에 맞물린 출력기어부(220)의 출력기어(60)의 각속도에 맞출 수 있도록 입력축(10)의 회전보다 고속으로 입력축(10)의 회전방향으로 회전되게 되어 해당 일방향클러치가 걸음상태가 되지 않아, 원활하게 입력기어부(210)의 저속단측 입력기어(40)는 입력축(10)의 회전방향으로 회전하게 된다.Way clutch (C) that is pressed against the protruding and retreating members (50, 50) such as the two balls when the wobbler portion (30) presses the protruding and retreating members (50, The two output gears 60 and 60 having different numbers of teeth of the output gear unit 220 engaged with the two input gears 40 and 40 move at different angular velocities, Since the one-way clutch C is interposed in each of the plurality of input gears 40 of the input device unit 210, the low gear end side of the input gear unit 210 The input gear 40 is connected to the high speed one side input gear 40 of the input device unit 210 by the output gear 60 of the output device unit 220 engaged with the low speed one side input gear 40 of the input device unit 210 The rotation of the input shaft 10 so as to match the angular speed of the output gear 60 of the engaged output gear unit 220 The low speed short side input gear 40 of the input unit 210 is rotated in the rotating direction of the input shaft 10 because the corresponding one-way clutch is not brought into a stepped state by rotating at a higher speed in the rotating direction of the input shaft 10 do.
상기 볼스크류(20)는 공지된 것으로서 모터(M)의 출력축에 커플링된 나선부에 쇄기부(30)를 체결하고 모터(M)의 출력축이 정역방향으로 회전함에 따라 쇄기부(30)가 상기 입력축(10) 내에서 전후진운동하게 된다.The ball screw 20 is a well-known ball screw having a spiral portion 30 coupled to a spiral portion coupled to an output shaft of a motor M and a spindle portion 30 And moves back and forth in the input shaft (10).
본 발명은 상기 볼스크류(20) 대신에 병진부인 실린더, 선형모터 등이 적용될 수도 있다. In the present invention, instead of the ball screw 20, a cylinder, a linear motor, or the like may be applied.
또한, 본 발명에 따른 실시예의 자동변속기에 대한 설명에서 상기 복수개의 볼과 같은 출몰부재(50)가 축선방향으로 일정 간격 이격되어 있는 것으로 설명되어 있지만, 본 발명은 이에 한정되지 않으며, 상기 복수개의 일방향클러치(C) 각각의 상기 복수개의 요부(41)와 마주하는 입력축(10)의 부위에 둘레방향으로 일정 간격 이격되어 복수개의 관통구멍(11)을 형성시키고 상기 둘레방향으로 배열된 상기 복수개의 관통구멍에 각각 상기 복수개의 볼과 같은 출몰부재(50)가 안착될 수도 있다.In the description of the automatic transmission according to the embodiment of the present invention, it is described that the protruding and retreating members 50 like the plurality of balls are spaced apart from each other by a predetermined distance in the axial direction, but the present invention is not limited thereto, A plurality of through holes 11 are formed at portions of the input shaft 10 opposed to the plurality of recessed portions 41 of the one-way clutch C at predetermined intervals in the circumferential direction to form the plurality of through holes 11, And the protruding and retracting members 50, such as the plurality of balls, may be respectively seated in the through holes.
본 발명에 따른 실시예의 자동변속기에 대한 설명에서 출몰부재가 구형형상을 가진 출몰부재(50)인 것으로 설명 및 도시되어 있지만, 본 발명은 이에 한정되지 않으며, 출몰부재가 반경방향 양쪽이 둥근면으로 되어 있으면 되며, 예를 들면, 볼 대신에 상기 요부(41)에 끼워맞춤되면서 일방향클러치(C)의 인너레이스(C1)의 내주면과 미끄럼접촉할 수 있는 원통형상부, 돔형상부 등으로 대체될 수 있으며, 상기 쇄기부(30)와도 미끄럼접촉할 수 있도록 상기 복수개의 출몰부재(50)가 원통형상부인 경우에는 원통형상부의 양단 테두리가 캠면을 갖고 있고, 그리고 돔형상부인 경우에는 돔형상부의 그 밑면 테두리가 캠면을 갖고 있다.Although the protruding / retracting member is described and shown as being the protruding / retracting member 50 having a spherical shape in the description of the automatic transmission in the embodiment of the present invention, the present invention is not limited to this and the protruding / And may be replaced with a cylindrical upper portion, a dome-shaped upper portion, or the like which can be in sliding contact with the inner peripheral surface of the inner race C1 of the one-way clutch C while being fitted to the recessed portion 41 instead of the ball When the plurality of protruding and retracting members 50 are cylindrical in shape so as to be in sliding contact with the chain base 30, both ends of the cylindrical upper portion have cam surfaces, and in the case of the dome- Has a cam surface.
또한, 본 발명에 따른 실시예의 자동변속기에 대한 설명에서 출몰부재(50)가 스페이서(42)에 의해 탄성적으로 반경방향 안쪽으로 가압받는 것으로 설명되어 있고, 상기 관통구멍(11)이 원통형으로 된 것으로 설명되어 있지만, 본 발명은 이에 한정되지 않으며, 도 6에 도시된 바와 같이, 스프링(S)과 스페이서(42)가 배제된 상태에서, 상기 관통구멍(11)의 반경방향 안쪽의 구경이 상기 출몰부재(50)가 일부만 삽입되고 상기 출몰부재(50) 전체가 관통될 수 없는 크기로 되어 상기 관통구멍이 절두원추형의 형상을 갖고서, 상기 관통구멍(11)이 상기 출몰부재(50)와 미끄럼접촉될 수 있으며, 아울러, 상기 입력축(10)의 복수개의 관통구멍(11)에 삽입되는 출몰부재(50)가 상기 복수개의 관통구멍(11)에 삽입될 수 있는 크기와 형상을, 즉 절두형상부를 갖되, 반경방향 양단이 둥근 돌출부를 갖게 될 수도 있다.In the description of the automatic transmission of the embodiment of the present invention, it is explained that the protruding / retracting member 50 is elastically urged radially inward by the spacer 42, and the through hole 11 is cylindrical But the present invention is not limited to this. As shown in FIG. 6, in a state in which the spring S and the spacer 42 are excluded, the diameter in the radial direction of the through hole 11 is smaller than the diameter The penetrating member 50 is partially inserted so that the entirety of the protruding member 50 can not penetrate therethrough so that the penetrating hole has a conical shape so that the penetrating hole 11 slides on the protruding member 50, The size and shape of the projecting / retracting member 50 inserted into the plurality of through holes 11 of the input shaft 10 can be inserted into the plurality of through holes 11, The radial amount It may be given a rounded protrusion.
또한, 상기 출몰부재(50)는 도 8에 도시된 바와 같이, 상기 관통구멍(11)에 직경을 달리하는 복수개의 볼이 삽입될 수도 있고, 도시는 않되어 있지만, 반경방향 바깥 단이 둥근 돌출부를 갖는 상태에서 관통구멍(11)의 반경방향 외측에 배치된 절두형상부와 관통구멍(11)의 반경방향 내측에 배치된 볼을 포함할 수도 있다.8, a plurality of balls having diameters different from each other may be inserted into the through-hole 11, and although not shown, the radial outer edge of the protruding / And a ball disposed radially inwardly of the through hole 11, in the radially outward position of the through hole 11. In this case,
또한, 상기 입력축(10)에 형성된 복수개의 관통구멍(11)은 도 7에 도시된 바와 같이, 입력축(10)의 길이방향으로 복수개의 나선줄 배열을 갖도록 일 피치(P1) 내에서 복수개의 나선줄로 배치된 상태(도 7에는 2나선줄 배열을 갖도록 배치됨)에서, 관형축의 둘레방향으로 동일한 위상차(도 7에는 180도 위상차로 도시됨)를 가지고서 복수개의 배열(도 7에는 2개로 배열됨)될 수도 있다.7, the plurality of through holes 11 formed in the input shaft 10 are formed in a plurality of spirals P1 in a pitch P1 so as to have a plurality of spiral arrangement in the longitudinal direction of the input shaft 10, (Arranged in two in Fig. 7) with the same phase difference in the circumferential direction of the tubular axis (shown by a 180-degree phase shift in Fig. 7) ).
상기 물림클러치에서는 관형축인 입력축의 길이방향으로 일정 간격을 두고 배치된 상기 관통구멍들이 관형축의 둘레방향에서 서로 상이한 관형축의 위치에 형성되게 되고, 그리고 상기 입력축에 형성된 관통구멍이 방사방향으로 확경된 동일한 구경을 갖고 있어서, 출몰부재에 의해 입력축이 반복적으로 받게 되는 부하가 입력축의 길이방향을 따라 입력축의 둘레방향으로 골고루 전달됨과 동시에, 입력축의 내주면측과 외주면측이 상기 출몰부재에 의해 받는 부하가 거의 균등하게 되어, 상기 입력축의 강도가 급속하게 저하되는 것을 방지할 수 있다.The through-holes arranged at regular intervals in the longitudinal direction of the input shaft which is the tubular shaft are formed at the positions of the tubular shafts different from each other in the circumferential direction of the tubular shaft, and the through holes formed in the input shaft are radially expanded The load that the input shaft is repeatedly received by the protruding and retreating member is uniformly transmitted along the longitudinal direction of the input shaft in the circumferential direction of the input shaft and the load received by the protruding and retreating member on the inner circumferential surface side and the outer circumferential surface side of the input shaft So that the strength of the input shaft can be prevented from rapidly lowering.
상기와 같이 구성된 자동변속기(200)는 다음과 같이 작동될 수 있다. The automatic transmission 200 configured as described above can be operated as follows.
도 1에 도시된 바와 같이, 상기 물림클러치(100)는 상기 쇄기부(30)가 상기 출몰부재(50)를 가압하고 있지 않은 상태에서는 출몰부재(50)가 상기 요부(41)에서 벗어나 있어서 상기 출몰부재(50)가 가압되고 있지 않은 일방향클러치(C)를 가진 상기 복수개의 입력기어(40)와 상기 입력축(10) 간에는 동력이 전달되지 않고, 상기 쇄기부(30)가 상기 출몰부재(50)를 반경바깥방향으로 밀어서 상기 출몰부재(50)가 상기 요부(41)에 삽입되면, 요부(41)에 상기 출몰부재(50)가 강제적으로 점유하게 되어 쇄기작용을 하여서 상기 출몰부재(50)가 가압되고 있는 일방향클러치(C)를 가진 상기 복수개의 입력기어(40) 중 어느 한개의 입력기어(40)와 상기 입력축(10)은 일체적으로 결합되어 이들 간에는 동력이 전달되게 된다. 1, the protruding / retreating member 50 is out of the recess 41 in a state in which the wedge 30 does not press the protruding / retreating member 50, No power is transmitted between the input gears 40 having the one-way clutch C and the input shaft 10 in which the projecting / retreating member 50 is not pressed, When the protruding member 50 is inserted into the recess 41 by pushing the protruding member 50 outward in the radial direction, the protruding member 50 is forcibly occupied in the recess 41, Any one of the input gears 40 of the plurality of input gears 40 having the one-way clutch C being pressed is integrally coupled with the input shaft 10 so that the power is transmitted therebetween.
그리고 상기 쇄기부(30)의 축선방향 길이가 축선방향으로 인접한 적어도 2개의 출몰부재를 접촉할 수 있는 길이로 되어 있어서, 쇄기부(30)가 저속단에서 고속단으로의 변속시에 그리고 고속단에서 저속으로의 변속시에 상기 입력축(10) 내에서 하나의 출몰부재(50)에 대한 가압을 유지하고 있다가 축선방향으로 이웃하는 적어도 2개 이상의 출몰부재(50)에 대한 가압을 유지하고 나서 축선방향으로 이웃하는 다른 하나의 출몰부재(50)에 대한 가압을 유지하면서 출력축(201)에 입력축(10)의 동력을 전달하게 되며, 상기 쇄기부(30)가 축선방향으로 이웃하는 적어도 2개 이상의 출몰부재(50)에 대한 가압을 유지할 시에 상기 2개의 출몰부재에 가압된 일방향클러치(C)를 가진 입력기어부(210)의 잇수가 다른 2개의 입력기어(40, 40)가 동일한 각속도로 운동하여서 이들에 맞물린 출력기어부(220)의 잇수가 다른 2개의 출력기어(60, 60)가 상이한 각속도운동하여도, 입력기어부(210)의 저속단측 입력기어(40)가 입력기어부의 저속단측 입력기어(40)에 맞물린 출력기어부(220)의 출력기어(60)에 의해 입력기어부(210)의 고속단측 입력기어(40)에 맞물린 출력기어부(220)의 출력기어(60)의 각속도에 맞출 수 있도록 입력축(10)의 회전보다 입력축(10)의 회전방향에서 고속으로 회전되게 되어, 해당 일방향클러치가 걸음상태가 되지 않기 때문에, 출력축(201)이 뒤틀림력을 받아서 기어이빨이 파손되지도 않으면서 변속시에 입력축(10)의 동력을 끊김없이 출력축(201)에 전달하는 것이 가능하게 된다.The axially extending length of the chain base 30 is such that at least two protruding and retracting members adjacent to each other in the axial direction can be contacted with each other, so that the chain base 30 can be moved from the low speed end to the high speed end, (50) in the input shaft (10) at the time of a speed change from a low speed to a low speed and maintains the pressurization to at least two or more adjacent absorptive members (50) in the axial direction The power of the input shaft 10 is transmitted to the output shaft 201 while maintaining the pressure on the other one of the concave / convex members 50 adjacent to the axial direction. The wedge base 30 includes at least two axially adjacent The two input gears 40 and 40 having different numbers of teeth of the input device unit 210 having the one-way clutch C pressed to the two protruding members are maintained at the same angular speed By exercising The low speed side input gear 40 of the input gear unit 210 is connected to the low speed side input gear 40 of the input gear unit even when the two output gears 60 and 60 having different numbers of teeth of the meshed output gear unit 220 move at different angular speeds. The output gear 60 of the output gear unit 220 meshed with the input shaft 10 is engaged with the output gear 60 of the output gear unit 220 meshed with the high speed one side input gear 40 of the input gear unit 210. [ , The one-way clutch is not in a stepped state, so that the output shaft 201 receives the twisting force and the gear teeth are not broken, It is possible to transmit the power of the engine 10 to the output shaft 201 without interruption.
따라서, 모터(M)를 정역회전시켜 상기 입력축(10) 내에서 항상 이웃하는 입력기어(40)와 물림하고 있는 상기 쇄기부(30)를 좌우로 이동시키면, 입력축인 입력축(10)과 출력축(201) 간의 동력전달이 끊김없이 증속과 감속을 수행할 수 있게 되며, 본 실시예의 자동변속기가 중력을 받고 있는 구동대상물을 승하강시키는 윈치 또는 크레인 등과 같은 장치에 적용될 경우에 구동대상물이 자유낙하되는 것을 방지하고 설정 중량보다 가벼운 구동대상물을 변속하여 에너지를 절감함과 동시에 신속하게 승하강시킬 수 있는 작용효과를 제공할 수 있다.Therefore, when the motor M is rotated in the forward and reverse directions to move the input gear 40 adjacent to the input shaft 10 and the wedge 30 interposed therebetween, the input shaft 10 and the output shaft 201 can be increased and decreased without interruption, and when the automatic transmission according to the present embodiment is applied to an apparatus such as a winch or a crane that moves up and down a driven object under gravity, It is possible to reduce the energy by shifting the driving object which is lighter than the set weight, and at the same time, it is possible to provide an action and effect of rapidly moving up and down.
그리고 상기 출몰부재(50)가 비물림상태에서 6시방향을 사이에 둔 3시 방향과 9시방향 사이에 위치된 경우에도 상기 출몰부재(50)가 상기 일방향클러치(C)의 내주면 및 스페이서와 미끄럼접촉하여 상기 출몰부재(50)가 관통구멍(11) 내에서 제위치에 유지되기 때문에 회전하고 있는 입력축(10)과 회전하고 있지 않은 일방향클러치(C)의 인너레이스(C1) 간에 부딪침이 없어서, 소음없이 입력기어(40)와 상기 입력축(10) 간에는 동력이 전달되지 않게 된다. (50) is located between the 3 o'clock position and the 9 o'clock position, which are located between the 6 o'clock position and the non-contact position, the protruding and lowering member (50) There is no collision between the rotating input shaft 10 and the inner race Cl of the one-way clutch C which is not rotating since the projecting / retreating member 50 is held in position in the through hole 11 by sliding contact , Power is not transmitted between the input gear (40) and the input shaft (10) without noise.
이에 따라 상기 물림 클러치(100)는 복수개의 출몰부재(50)가 쇄기부(30)에 의해 지지를 받으면서 일방향클러치(C)의 인너레이스(C1)의 복수개의 요부(41)에 강제적으로 삽입되면 입력기어(40)와 입력축(10)이 함께 회전하게 되고, 쇄기부(30)에 의해 지지를 받지 않으면, 일방향클러치(C)의 인너레이스(C1)의 복수개의 요부(41)에서 이탈되어, 관통구멍(11)에서 유지되어서, 자유롭게 상기 복수개의 볼과 같은 출몰부재(50)에 장애를 받지 않고 입력기어(40) 또는 입력축(10)이 회전하게 되어 고속상태에서도 입력기어(40)와 입력축(10) 간의 결합 및 결합해제가 가능하게 된다.The plurality of protruding and retracting members 50 are forcibly inserted into the plurality of recesses 41 of the inner race C1 of the one-way clutch C while being supported by the wobbler 30 If the input gear 40 and the input shaft 10 rotate together and are not supported by the wobbler 30, the input gear 40 and the input shaft 10 are disengaged from the plurality of recesses 41 of the inner race C1 of the one- The input gear 40 or the input shaft 10 is rotated without being disturbed by the protruding and retreating member 50 such as the plurality of balls freely and held in the through hole 11 so that the input gear 40 and the input shaft 40 (10).
또한, 상기 실시예에서 입력기어부에 일방향클러치와 물림클러치가 구비되어 있는 것 대신에, 출력기어부에 일방향클러치와 물림클러치가 구비될 수 있으며, 이때에 상기 출력기어부에 개재된 상기 일방향클러치의 걸음방향은 상기 입력기어부에 개재된 일방향클러치의 걸음방향이면 동일한 작용효과를 제공할 수 있다.In the above embodiment, instead of the one-way clutch and the clutch engaged in the input unit, the output unit may include a one-way clutch and a catching clutch. In this case, Can provide the same operational effect as that of the one-way clutch interposed in the input unit.
또한, 상기 실시예에서는 입력기어부들의 입력기어들 중에서의 작은 직경을 갖은 입력기어에는 물림클러치와 일방향클러치가 개재되는 것이 공간적으로 한계가 있어서, 입력기어부의 복수개의 입력기어중 작은 직경을 가진 입력기어에 치합하는 상기 출력기어부의 출력기어에 일방향클러치가 개재될 수도 있다. 이때에 상기 출력기어부의 출력기어에 개재된 상기 일방향클러치의 걸음방향은 상기 입력기어부의 입력기어에 개재된 일방향클러치의 걸음방향에 반대이다.Further, in the above embodiment, it is spatially limited that the input clutch having the smaller diameter among the input gears of the input unit portions interposes the clutch and the one-way clutch. Thus, among the plurality of input gears of the input unit, A one-way clutch may be interposed in the output gear of the output gear unit. At this time, the direction of the one-way clutch interposed in the output gear of the output gear unit is opposite to the direction of the one-way clutch interposed in the input gear of the input gear unit.
(실시예2)(Example 2)
이하, 본 발명에 따른 실시예2의 자동 변속기가 도 3을 참조하여 상세히 설명될 것이다.Hereinafter, an automatic transmission according to a second embodiment of the present invention will be described in detail with reference to FIG.
도 3에는 자동 변속기가 부호 200으로서 지시되어 있다.3, the automatic transmission is indicated by reference numeral 200. In Fig.
상기 자동 변속기(200)는 일방향 구동원인 구동모터(M1)의 구동축(1)에 고정적으로 외접된 구동기어(2)에 치합된 피동기어(4)에 고정적으로 내접된 관형의 입력축(10), 상기 입력축(10)에 베어링(B)을 개재하여 일정 간격 이격되어 회전가능하게 외접된 입력기어부(210), 상기 입력축(10)에 대하여 평행하게 배치된 관형의 출력축(201)에 베어링을 개재하여 일정 간격 이격되어 회전가능하게 외접되어 상기 입력기어부(210)와 맞물리는 출력기어부(220), 상기 입력기어부(210)에 선택적으로 물림하는 입력물림클러치(110) 및 상기 출력기어부(220)에 선택적으로 물림하는 출력물림클러치(120)를 포함하고 있다. The automatic transmission 200 includes a tubular input shaft 10 fixedly inscribed on a driven gear 4 coupled to a drive gear 2 fixedly circumscribed to a drive shaft 1 of a drive motor M1 as a one- An input gear unit 210 which is rotatably circumscribed by a predetermined distance between the input shaft 10 and the bearing B; a tubular output shaft 201 disposed parallel to the input shaft 10 with a bearing interposed therebetween; An input clutch unit 110 selectively engaged with the input gear unit 210, and an output gear unit 220 selectively engaged with the input gear unit 220. The output gear unit 220 is selectively engaged with the input gear unit 210, And an output clutch 120 that engages with the output clutch 120.
상기 입력기어부(210)는 축선방향 일측으로 갈수록 직경이 큰 복수개의 입력기어(40)를 포함하고 있다. 상기 복수개의 입력기어(40) 각각은 상기 입력축(10)에 외접된 상기 베어링(B)에 일방향 클러치(C)를 개재하여 외접되어 있다.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.
상기 출력기어부(220)는 상기 복수개의 입력기어(40)와 각각 맞물리되 상기 축선방향 일측으로 갈수록 직경이 작은 복수개의 출력기어(60)를 포함하고 있다.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.
상기 입력물림클러치(110)는 병진부로서 상기 입력축(10)에 베어링을 개재하여 입력나사축(111)이 회전가능하게 삽입되어 있는 입력볼스크류(112)와 이 입력볼스크류(112)의 입력나사축에 체결되어 상기 입력축(10)에 축선방향으로 미끄럼이동가능하게 내접된 너트인 입력쇄기부(113)를 포함하고 있고, 그리고 상기 복수개의 입력기어(40) 각각의 일방향 클러치(C)의 인너레이스(C1)의 내주면에 둘레방향을 따라 일정 간격 이격되어 형성된 복수개의 입력요부(41); 및 상기 복수개의 입력기어(40) 각각의 일방향 클러치(C)의 인너레이스(C1)의 상기 복수개의 입력요부(41)와 마주하는 입력축(10)의 부위에 축선방향으로 일정 간격을 두고서 형성된 복수개의 입력관통구멍(11)에 방사상 안쪽 부위가 삽입 안착되어 상기 입력쇄기부(113)에 의해 선택적으로 반경바깥방향으로 밀어져서 가압을 받게 되면 반경바깥방향으로 밀어져서 상기 복수개의 입력요부(41) 중 마주하는 입력요부(41)에 일부가 삽입되는 볼과 같은 입력출몰부재(115)를 포함하고 있다.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 portion 113 that is a nut that is fastened to the screw shaft and is internally engaged with the input shaft 10 so as to be slidable in an axial direction. A plurality of input recessed portions 41 formed on the inner circumferential surface of the inner race 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 wedge 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.
또한, 상기 출력물림클러치(120)는 병진부로서 상기 출력축(201)에 베어링을 개재하여 출력나사축(121)이 회전가능하게 삽입되어 있는 출력볼스크류(122)와 이 출력볼스크류(122)의 출력나사축에 체결되어 상기 출력축(201)에 축선방향으로 미끄럼이동가능하게 내접된 너트인 출력쇄기부(123)를 포함하고 있고, 그리고 상기 복수개의 출력기어(60) 각각의 내주면에 둘레방향을 따라 일정 간격 이격되어 형성된 복수개의 출력요부(61); 및 상기 복수개의 출력기어(60) 각각의 상기 복수개의 출력요부(61)와 마주하는 출력축(201)의 부위에 축선방향으로 일정 간격을 두고서 형성된 복수개의 출력관통구멍(211)에 방사상 안쪽 부위가 삽입 안착되어 상기 출력쇄기부(123)에 의해 선택적으로 반경바깥방향으로 밀어져서 가압을 받게 되면 반경바깥방향으로 밀어져서 상기 복수개의 출력요부(61) 중 마주하는 출력요부(61)에 일부가 삽입되는 볼과 같은 출력출몰부재(125)를 포함하고 있다.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 wobbling portion 123 that is a nut fastened to an output screw shaft of the output gears 60 and internally engaged with the output shaft 201 so as to be slidable in an axial direction. A plurality of output recesses 61 spaced apart from each other by a predetermined distance; 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 wobbling portion 123 so that a part of the output recessed portion 61 of the plurality of output recessed portions 61 is inserted And an output protruding and retreating member 125 such as a ball.
상기 입력물림클러치(110)와 출력물림클러치(120)의 기본구성은 실시예1의 물림클러치의 구성과 동일하다. The basic configuration of the input clutch 110 and the output clutch 120 is the same as that of the engaging clutch of the first embodiment.
상기 입력쇄기부(113)가 축선방향으로 이웃한 2개의 입력출몰부재(115, 115)를 가압하여 2개의 입력기어(40, 40)를 물림하고 있는 상태에서, 상기 출력쇄기너트(123)가 상기 2개의 입력기어(40, 40)에 치합하고 있는 출력기어(60, 60)에 위치된 축선방향으로 이웃하는 2개의 볼과 같은 출력출몰부재(125, 125)를 물림하고 있으면, 상기 2개의 볼과 같은 입력출몰부재(115, 115)에 가압된 일방향클러치(C)를 가진 입력기어부(210)의 잇수가 다른 2개의 입력기어(40, 40)가 동일한 각속도로 운동하여 이들에 맞물린 출력기어부(220)의 잇수가 다른 2개의 출력기어(60, 60)가 상이한 각속도운동하여서 출력축(201)이 뒤틀림력을 받아서 기어 이빨이 파손될 수 있다고 판단되지만, 상기 입력기어부(210)의 복수개의 입력기어(40, 40) 각각에 일방향클러치(C)가 개재되어 있기 때문에, 입력기어부(210)의 저속단측 입력기어(40)는, 입력기어부(210)의 저속단측 입력기어(40)에 맞물린 출력기어부(220)의 출력기어(60)에 의해, 입력기어부(210)의 고속단측 입력기어(40)에 맞물린 출력기어부(220)의 출력기어(60)의 각속도에 맞출 수 있도록 입력축(10)의 회전보다 고속으로 입력축(10)의 회전방향으로 회전되게 되어 해당 일방향클러치가 걸음상태가 되지 않아, 원활하게 입력기어부(210)의 저속단측 입력기어(40)는 입력축(10)의 회전방향으로 회전하게 된다.The output worm nut 123 is rotated in the state in which the input wobbler 113 presses the two input / output projecting / contracting members 115 and 115 adjacent to each other in the axial direction to engage the two input gears 40 and 40 When two adjacent output-side projecting and retracting members 125 and 125 located in the axial direction located in the output gears 60 and 60 meshing with the two input gears 40 and 40 are engaged, The two input gears 40 and 40 having different numbers of teeth of the input gear unit 210 having the one-way clutch C pressed against the input and output projecting and contracting members 115 and 115 move at the same angular speed, It is determined that the two output gears 60 and 60 having different numbers of teeth of the input gear unit 220 move at different angular speeds so that the output shaft 201 receives the twisting force and the gear teeth may be broken. Since the one-way clutch C is interposed in each of the clutches 40 and 40, Speed low-speed side input gear 40 of the input unit 210 is connected to the low speed side input gear 40 of the input gear unit 210 by the output gear 60 of the output gear unit 220 engaged with the low- Is rotated in the rotational direction of the input shaft (10) at a higher speed than the rotation 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 one- The low speed side input gear 40 of the input unit 210 is rotated in the rotation direction of the input shaft 10. [
또한, 상기 실시예2에서, 입력기어부(210)의 복수개의 입력기어(40)에 일방향 클러치(C)가 개재된 것으로 설명되어 있지만, 본 발명은 이에 한정되지 않고 상기 출력기어부(220)의 복수개의 출력기어(60)의 각각과 상기 출력축(201) 사이에 일방향 클러치(C)가 개재될 수 있도 있으며, 이때에 상기 출력기어부(220)에 개재된 상기 일방향클러치(C)의 걸음방향은 상기 입력기어부(210)에 개재된 입방향클러치의 걸음방향에 반대이다.Although the one-way clutch C is interposed in the plurality of input gears 40 of the input device unit 210 in the second embodiment, the present invention is not limited to this, and a plurality of the output device units 220 Way 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 input unit section 210 is operated.
또한, 상기 실시예2에서는 입력기어부(210)의 복수개의 입력기어들 중에서의 작은 직경을 가진 입력기어에는 물림클러치(110)와 일방향클러치(C)가 개재되는 것이 공간적으로 한계가 있어서, 입력기어부(210)의 복수개의 입력기어(40)중 작은 직경을 가진 입력기어(40)에 치합하는 상기 출력기어부(220)의 출력기어(60)에 일방향클러치(C)가 개재될 수도 있다. 이때에 상기 출력기어부(220)의 출력어(60)에 개재된 상기 일방향클러치(C)의 걸음방향은 상기 입력기어부(210)의 입력기어(40)에 개재된 입방향클러치의 걸음방향에 반대이다.Further, in the second 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.
상기 입력물림클러치(110)의 입력쇄기너트(113)와 상기 출력물림클러치(120)의 출력쇄기너트(123)는, 도 3 및 도 4에 도시된 바와 같이, 후술되는 자체의 동력원으로 상기 입력쇄기부와 상기 출력쇄기부가 이동되게 하는 모드전환수단(300)에 의해 동기적으로 축선방향 양쪽으로 동시에 이동될 수 있다.3 and 4, 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 axial directions by the mode switching means (300) for moving the output base portion and the output base portion.
또한, 상기 입력쇄기부(113)와 상기 출력쇄기부(123)의 위치는, 도 3에 도시된 바와 같이, 입력축(10)의 축선방향에서 동일한 위치에 위치결정될 수도 있고, 또는 도 4에 도시된 바와 같이, 하나의 입력기어(40)와 이에 맞물리는 하나의 출력기어(60)를 사이에 두고 상기 하나의 입력기어(40)에 바로 인접한 상기 하나의 입력기어(40)보다 작은 직경의 다른 하나의 입력기어(40)를 상기 하나의 입력기어(40)와 동시에 물림할 수 있는 위치에 상기 입력쇄기부(113)가 위치결정되어 있고 그리고 상기 하나의 출력기어(60)에 바로 인접한 상기 하나의 출력기어(60)보다 작은 직경의 다른 하나의 출력기어(60)를 상기 하나의 출력기어(60)와 동시에 물림할 수 있는 위치에 상기 출력쇄기부(123)가 위치결정될 수도, 즉 상기 입력쇄기부(113)와 상기 출력쇄기부(123)에 의해 동시에 물려서 서로 치합하고 있는 하나의 입력기어(40)와 출력기어(60)가 상기 입력쇄기부(113)와 상기 출력쇄기부(123) 중 어느 하나의 쇄기부와 물려서 서로 치합하고 있는 다른 하나의 입력기어(40) 또는 다른 하나의 출력기어(60)의 직경보다 큰 직경을 가지게 배치될 수도 있다. 3, the positions of the input wobbler 113 and the output wobbler 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 wedge portion 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 portion 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, And the output wobbling portion 123 and the output wobbling portion 123 simultaneously And one input gear 40 and an output gear 60 which mate with each other are engaged with any one of the input wedge 113 and the output wedge 123, But may be arranged to have a larger diameter than the diameter of the gear 40 or the other output gear 60.
전자의 경우에는, 동력전달시에 입력쇄기부(113)에 물림되지 않은 다른 입력기어(40)들은 회전하지 않게 되고, 출력쇄기부(113)에 물림되지 않은 다른 출력기어(60)들도 회전하지 않게 된 상태에서, 입력쇄기부(113)가 직경이 작은 쪽으로 이동할 때에나 출력쇄기부(123)가 직경이 작은 쪽으로 이동할 때에는, 입력쇄기부(113)가 물림하고 있는 2개의 입력기어(40)중 직경이 큰 쪽의 하나의 입력기어(40)의 회전력으로 출력축(201)에 전달하기 때문에, 입력쇄기부(113)가 축선방향으로 이동하여 입력쇄기부(113)에 의해 물림되지 않아 회전하고 있지 않은 작은 입력기어(40)를 물림하거나 출력쇄기부(123)가 축선방향으로 이동하여 출력쇄기부(123)에 의해 물림되지 않아 회전하고 있지 않은 작은 출력기어(60)를 물림하여도, 일방향클러치(C)가 개재된 상기 새로이 물림된 작은 입력기어(40)가 헛돌게 되어, 이들 기어들이 회전하면서도 출력축(201)에 구동력을 전달하는 데 관여하지 않아서, 감속시에 출력축에 결합된 구동대상물의 부하가 상기 새로이 물림된 작은 입력기어(40)에 전달되지 않고, 다음으로 작은 입력기어(40)를 물림하기 위해 상기 입력쇄기부(113)가 이동할 때에 상기 새로이 물림된 작은 입력기어(40)에 의해 출력축(201)에 구동력이 전달되므로, 입력기어(40)와 이에 맞물린 출력기어(60)가 서로 치합된 상태로 회전하면서 구동력 전달 상태가 되어 부드럽게 감속을 수행할 수 있지만, 입력쇄기부(113)가 직경이 큰 쪽으로 이동할 때에나 출력쇄기부(123)가 직경이 큰 쪽으로 이동할 때에는, 회전하고 있지 않은 직경이 큰 입력기어(40) 또는 출력기어(60)에 회전하고 있는 입력축(10)과 출력축(201)이 입력쇄기부(113)와 출력쇄기부(123)에 의해 순간적으로 결합되면서 구동력 전달 상태가 되어, 부하대상물의 부하가 바로 상기 회전하고 있지 않은 직경이 큰 입력기어(40) 또는 출력기어(60)에 구동력과 함께 전달되게 되어 충격력이 발생되어서, 물림클러치, 입력축, 출력축, 입력기어, 출력기어 등이 변형 또는 파손될 수도 있다.In the former case, the other input gears 40 not engaged with the input wobbler 113 are not rotated during power transmission, and the other output gears 60 not engaged with the output wobbler 113 are rotated When the input wobbler 113 moves to a smaller diameter or when the output wobbler 123 moves to a smaller diameter in a state where the input wobbler 113 is not engaged, The input wobbler 113 moves in the axial direction and is not bumped by the input wobbler 113, so that the rotation of the input wobbler 113 Even when the output wedge 123 moves in the axial direction and is not caught by the output wedge 123 so that the output wedge 123 is not rotated, Way clutch (C) The input gear 40 is idle so that these gears are not involved in transmitting the driving force to the output shaft 201 while rotating so that the load of the driven object coupled to the output shaft at the time of deceleration is smaller than the load of the newly- The driving force is transmitted to the output shaft 201 by the newly engaged small input gear 40 when the input wobbler 113 moves so as to engage the small input gear 40 The input gear 40 and the output gear 60 meshing with the input gear 40 are engaged with each other to be in a driving force transmitting state to smoothly decelerate. However, when the input wobbler 113 moves to a larger diameter, The output shaft 201 and the input shaft 10 rotating in the input gear 40 or the output gear 60 having a large diameter which is not rotating when the chain base portion 123 moves to a larger diameter are connected to the input choke portion 113 ) And output And the load of the load object is transmitted to the input gear 40 or the output gear 60 having a large diameter that is not rotating immediately, together with the driving force, so that the impact force The input clutch, the input shaft, the output shaft, the input gear, the output gear, etc. may be deformed or broken.
하지만, 후자의 경우에는, 동력전달시에 입력쇄기부(113)와 출력쇄기부(123)가 축선방향에서 일측으로 또는 타측으로 동기적으로 이동하여도, 항상 입력쇄기너트(113)와 출력쇄기너트(123) 중 어느 하나가 직경이 작은 기어 쪽으로 이동하게 되어 입력쇄기부(113)와 출력쇄기부(123) 중 어느 하나가 직경이 큰 기어쪽으로 이동하여 새로인 직경이 큰 기어를 물림하게 되어도, 상기 새로이 물린 직경이 큰 기어와 이 큰 기어에 맞물린 작은 기어는 이미 출력축으로의 구동력이 전달되지 않은 채로 회전된 상태에 있기 때문에, 큰 충격력없이 구동력 전달상태가 되어, 물림클러치, 입력축, 출력축, 입력기어, 출력기어 등이 변형 또는 파손되는 것이 방지되어 바람직하다.However, in the latter case, even when the input wobbler 113 and the output wobbler 123 move synchronously from one side to the other or from the axial direction during power transmission, the input worm nut 113 and the output wobble When any one of the nuts 123 is moved to the gear having a smaller diameter so that either the input wedge 113 or the output wedge 123 moves toward the larger diameter gear to engage the new larger diameter gear 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.
상기 입력물림클러치(110)의 입력쇄기부(113)와 상기 출력물림클러치(120)의 출력쇄기부(123)를 동기적으로 축선방향으로 이동시키는 상기 모드전환수단(300)은, 입력축(10)의 회전방향 및 불변속도와 같은 회전방향과 회전속도로 입력나사축(111)을 회전시키는 동조부(310), 출력축(201)의 회전속도보다 빠른 또는 늦은 속도로 출력나사축(121)을 정역방향으로 회전시키는 상대속도차발생부(320), 및 출력나사축(121)과 출력쇄기부(123) 간의 상대속도 차이 만큼 출력축(201)의 회전수를 입력나사축(111)에 전달하는 상대속도차전달부(330)를 포함하고 있다.The mode switching means 300 for synchronously moving the input synchronizing portion 113 of the input clutch 110 and the output synchronizing portion 123 of the output engaging clutch 120 axially moves the input shaft 10 The output shaft 201 is rotated at a speed faster or slower than the rotational speed of the output shaft 201. The output shaft 201 is rotated at a speed that is lower than the rotational speed of the output shaft 201, A relative speed difference generator 320 for rotating the output shaft 201 in the forward and reverse directions and a rotational speed of the output shaft 201 to the input screw shaft 111 by a relative speed difference between the output screw shaft 121 and the output waxer 123 And a relative speed difference transfer unit 330.
상기 동조부(310)는 상기 구동축(1)에 고정적으로 외접된 정방향구동기어(301), 상기 정방향구동기어(301)에 치합된 역방향내외치기어(302), 상기 입력나사축(111)에 고정적으로 외접된 제1태양기어(303), 및 상기 제1태양기어(303)와 상기 역방향내외치기어(302)에 치합된 제1유성기어(304)를 포함하고 있다.The tuning unit 310 includes a forward drive gear 301 fixedly connected to the drive shaft 1, a reverse oar gear 302 coupled to the forward drive gear 301, And a first planetary gear 304 meshed with the first sun gear 303 and the reverse planetary gear 302. The first sun gear 303 is fixedly engaged with the first planetary gear 304,
상기 상대속도차발생부(320)는 상기 출력축(201)에 고정적으로 외접된 제1 및 제2정방향피동기어(321, 322), 상기 출력나사축(121)에 고정적으로 외접된 출력나사축구동기어(323), 상기 출력축(201)에 평행하게 배치된 제1아이들축(324), 상기 제1아이들축(324)에 회전가능하게 외접되어 상기 제1정방향피동기(321)에 치합하는 제1아이들기어(325), 상기 제1아이들축(324)에 회전가능하게 외접되어 제1중간기어(326)를 경유하여 상기 제2정방향피동기어(322)에 치합하는 제2아이들기어(327), 상기 제1아이들축(324)에 고정적으로 외접되어 상기 출력나사축구동기어(323)에 치합하는 출력나사축기동기어(328)을 포함하고 있다.The relative speed difference generator 320 includes first and second forward driven gears 321 and 322 fixedly circumscribed to the output shaft 201 and an output screw shaft fixedly circumscribed to the output screw shaft 121. [ A gear 323, a first idle shaft 324 disposed parallel to the output shaft 201, a second idle shaft 324 rotatably circumscribed by the first idle shaft 324 and meshing with the first forwardly- A second idle gear 327 rotatably circumscribed by the first idle shaft 324 and meshing with the second forward driven gear 322 via a first intermediate gear 326, And an output screw shaft starting gear 328 which is fixedly circumscribed to the first idle shaft 324 and meshes with the output screw motion synchronizing gear 323.
또한, 상기 상대속도차발생부(320)는 선택적으로 상기 제1아이들축(324)에 제1아이들기어(325)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제1스톱퍼(329A)와 그리고 선택적으로 상기 제1아이들축(324)에 제2아이들기어(327)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제2스톱퍼(329B)를 더 포함하고 있다.The relative speed difference generator 320 may selectively include a first stopper 329A that engages the first idle gear 325 on the first idle shaft 324 to rotate or idle the first idle gear 325, And a second stopper 329B that engages the second idle gear 327 with the first idle shaft 324 and rotates or idles them together.
상기 상대속도차전달부제2증감속부(330)는 상기 출력축(201)에 고정적으로 외접된 제3 및 제4정방향피동기어(331, 332), 상기 제1유성기어(304)에 고정적으로 내접된 유성기어축(305)에 고정적으로 외접된 제2유성기어(306)에 치합된 제2태양기어(333), 상기 출력축(201)에 평행하게 배치되어 상기 제2태양기어(333)에 고정적으로 내접된 제2아이들축(334), 상기 제2아이들축(334)에 회전가능하게 외접되어 상기 제3정방향피동기어(331)에 치합하는 제3아이들기어(335), 및 상기 제2아이들축(334)에 회전가능하게 외접되어 제2중간기어(336)를 경유하여 상기 제4정방향피동기어(332)에 치합하는 제4아이들기어(337)를 포함하고 있다.The relative speed difference difference transmission portion 2 speed increase / deceleration portion 330 includes third and fourth forward driven gears 331 and 332 which are fixedly circumscribed to the output shaft 201, fixed and inscribed in the first planetary gear 304 A second sun gear 333 meshing with the second planetary gear 306 fixedly circumscribed to the planetary gear shaft 305 and a second sun gear 333 disposed parallel to the output shaft 201 and fixed to the second sun gear 333 A third idle gear 335 rotatably circumscribed by the second idle shaft 334 and meshing with the third forward driven gear 331, And a fourth idle gear 337 rotatably circumscribed by the second intermediate gear 334 and meshing with the fourth forward driven gear 332 via a second intermediate gear 336.
또한, 상기 상대속도차전달부(330)는 선택적으로 상기 제2아이들축(334)에 제3아이들기어(335)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제3스톱퍼(339A)와 그리고 선택적으로 상기 제2아이들축(334)에 제2아이들기어(337)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제4스톱퍼(339B)를 더 포함하고 있다.The relative speed difference transfer unit 330 may further include a third stopper 339A that selectively engages the third idle gear 335 on the second idle shaft 334 to rotate or idle the third idle gear 335, And a fourth stopper 339B which engages the second idle gear 337 with the second idle shaft 334 and rotates or idles them together.
상기 제1태양기어(303)는 상기 정방향구동기어(301), 상기 역방향내외지치기어(302), 상기 제1유성기어(304) 및 상기 제1태양기어(303) 간의 기어비를 통하여 입력축(10)이 역방향으로 1회전할 때 역방향으로 1회전할 수 있도록 되어 있다.The first sun gear 303 is connected to the input shaft 10 through the gear ratio between the forward drive gear 301, the reverse internal and external ground gear 302, the first planetary gear 304 and the first sun gear 303. ) Can make one revolution in the reverse direction when making one revolution in the reverse direction.
또한, 상기 출력나사축구동기어(323)는 상기 출력나사축기동기어(328)와의 기어비를 통하여 출력나사축(121)이 상기 출력축(201)보다 몇배 빠르게 또는 몇배 느리게 회전할 수 있도록 되어 있고, 상기 제1태양기어(303)는 상기 제3정방향피동기어(331)와 제3아이들기어(335) 간의 기어비를 통하여 또는 상기 제4정방향피동기어(332), 제2중간기어(336) 및 제4아이들기어(337) 간의 기어비를 통하여 그리고 제2태양기어(333), 제2유성기어(306), 제1유성기어(304) 및 상기 제1태양기어(303) 간의 기어비를 통하여 상기 출력나사축(121)과 상기 출력축(201) 간의 회전속도차 만큼의 속도로 회전할 수 있도록 되어 있다.The output screw shaft driving gear 323 is configured such that the output screw shaft 121 rotates several times faster or several times slower than the output shaft 201 through the gear ratio with the output screw shaft starting gear 328, The first sun gear 303 is connected to the fourth forward driven gear 332 via the gear ratio between the third forward driven gear 331 and the third idle gear 335 or via the fourth forward driven gear 332, 4 idle gear 337 and through a gear ratio between the second sun gear 333, the second planetary gear 306, the first planetary gear 304 and the first sun gear 303, And can rotate at a speed corresponding to the rotational speed difference between the shaft 121 and the output shaft 201.
또한, 출력나사축(121)과 상기 출력축(201) 사이에는 선택적으로 상기 출력나사축(121)에 상기 출력축(201)을 물림하여 이들이 함께 회전하게 하여 이들 사이에 상대속도가 발생되지 않게 하거나 물림하지 않아 헛돌게 하는 제5스톱퍼(351)와 그리고 선택적으로 상기 입력나사축(111)에 상기 입력축(10)을 물림하여 이들이 함께 회전하게 하여 이들 사이에 상대속도가 발생되지 않게 하거나 물림하지 않아 헛돌게 하는 제6스톱퍼(352)가 개재되어 있다.The output shaft 201 is coupled to the output screw shaft 121 to selectively rotate the output shaft 201 between the output screw shaft 121 and the output shaft 201 so as to rotate the output shaft 201 together, A fifth stopper 351 for rotating the input shaft 10 and a fifth stopper 351 for selectively rotating the input shaft 10, and optionally the input shaft 10 is engaged with the input shaft shaft 111 so that they rotate together, And a sixth stopper 352 for turning is provided.
상기 제5스톱퍼(351)의 구성은 제1 내지 제4스톱퍼의 구성과 유사하며, 이를 간략하게 언급하면, 출력축(201)의 내주면에 둘레방향으로 이격된 복수개의 요부를 형성시키고 상기 출력나사축(121)의 일단을 관형부로 만들어서 상기 복수개의 요부와 마주하는 부분에 복수개의 관통구멍을 형성시키고, 상기 복수개의 관통구멍에 반경방향으로 출몰하는 출몰부재를 심고, 실린더의 로드(353)의 병진운동에 의해 병진운동하는 쇄기부를 상기 로드(353)에 회전가능하게 외접시키고, 상기 쇄기부로 하여금 상기 출몰부재를 가압하여 상기 요부에 강제적으로 삽입되게 하는 구성으로 될 수 있으며, 상기 제5스톱퍼(351)는 상기 출력나사축(121)이 상기 출력축(201)에 고정되어 모드전환수단이 가동되지 않을 때, 출력쇄기너트(123)가 축선방향으로 이동하는 것을 방지하는 작용을 한다.The configuration of the fifth stopper 351 is similar to that of the first to fourth stoppers. To simplify the description, a plurality of recesses spaced in the circumferential direction are formed on the inner circumferential surface of the output shaft 201, A plurality of through holes are formed in a portion facing the plurality of recessed portions, and a protruding and retreating member projecting in a radial direction is planted in the plurality of through holes, The chain base portion translationally moving by the motion is rotatably circumscribed by the rod 353 so that the chain base portion is forced to be inserted into the recess portion by pressing the protruding and retreating member, The output shaft nut 121 is fixed to the output shaft 201 to prevent the output wrench nut 123 from moving in the axial direction when the mode switching means is not operated And the dragon.
또한, 상기 제6스톱퍼(352)의 구성은 제1 내지 제4스톱퍼의 구성과 유사하며, 이를 간략하게 언급하면, 입력축(10)의 내주면에 둘레방향으로 이격된 복수개의 요부를 형성시키고 상기 입력나사축(111)의 일단을 관형부로 만들어서 상기 복수개의 요부와 마주하는 부분에 복수개의 관통구멍을 형성시키고, 상기 복수개의 관통구멍에 반경방향으로 출몰하는 출몰부재를 심고, 실린더의 로드(353)의 병진운동에 의해 병진운동하는 쇄기부를 상기 로드(353)에 회전가능하게 외접시키고, 상기 쇄기부로 하여금 상기 출몰부재를 가압하여 상기 요부에 강제적으로 삽입되게 하는 구성으로 될 수 있으며, 상기 제6스톱퍼(352)는 상기 입력나사축(111)이 상기 입력축(10)에 고정되어 모드전환수단이 가동되지 않을 때, 입력쇄기너트(113)가 축선방향으로 이동하는 것을 방지하는 작용을 한다. The sixth stopper 352 has a structure similar to that of the first to fourth stoppers. In brief, the sixth stopper 352 includes a plurality of recesses spaced in the circumferential direction on the inner circumferential surface of the input shaft 10, A plurality of through holes are formed in a portion facing the plurality of recesses, one end of the screw shaft 111 is made into a tubular portion, and a protruding and retreating member projecting in a radial direction is planted in the plurality of through holes, And the wedge base portion is forced to be inserted into the recessed portion by pressing the protruding and retreating member, and the wedge base portion may be configured to be forcedly inserted into the recessed portion, 6 The stopper 352 prevents the input wrench nut 113 from moving in the axial direction when the input screw shaft 111 is fixed to the input shaft 10 and the mode switching means is not operated. It acts.
상기 제5 및 제6스톱퍼(351, 352)는 별개의 실린더의 로드에 의해 병진운동할 수도 있고, 도 3 내지 도 4에 도시된 바와 같이, 하나의 실린더에 구비된 두개의 로드 각각에 구비될 수도 있다. The fifth and sixth stoppers 351 and 352 may be translationally moved by the rods of the different cylinders, and may be provided on the two rods provided on one cylinder, as shown in FIGS. 3 to 4 It is possible.
또한, 상기 제1 내지 제4스톱퍼(329A, 329B, 339A, 339B)는, 베이스에 고정된 실린더의 로드의 선단에 베어링을 개재하여 쇄기부가 관형축인 제1 및 제2아이들축(324, 334)에 전후진하면서 제1 및 제2아이들축(324, 334)에 회전가능하게 외접된 기어를 선택적으로 물림할 수 있는 공지의 물림클러치, 또는 베이스에 고정된 모터의 축에 결합된 나사축에 체결된 쇄기너트가 관형축인 제1 및 제2아이들축(324, 334)에 내접되어 전후진하면서 제1 및 제2아이들축(324, 334)에 회전가능하게 외접된 기어를 선택적으로 물림할 수 있는 공지의 물림클러치로 되면, 회전체에 전기와 유체가 공급되지 않아 제조 및 유비보수 관점에서 바람직하다.The first to fourth stoppers 329A, 329B, 339A, and 339B have first and second idle shafts 324, A known clutch engaged to selectively engage gears rotatably circumscribed on the first and second idle shafts 324 and 334 while moving forward or backward on the first and second idle shafts 334 and 334, 334 are engaged with the first and second idle shafts 324, 334 to selectively engage gears rotatably circumscribed by the first and second idle shafts 324, 334 while moving back and forth It is preferable from the viewpoint of manufacturing and maintenance that the electric motor and the fluid are not supplied to the rotating body.
또한, 상기 실시예2에서 상기 제1 및 제2아이들축(324, 334)이 회전중심축선이 동일한 선상에 있는 경우에는 도 3 및 도 4에 도시된 바와 같이, 상기 쇄기부가 2개로 되어 축선방향으로 이격되어서, 상기 2개의 쇄기부로 하여금 상기 입력쇄기와 출력쇄기를 일측으로 이동시킬 시에 제1 내지 제4아이들기어중 2개의 아이들기어를 물림하게 하고 타측으로 이동할 시에 다른 2개의 아이들기어를 물림하게 할 수도 있다.In the second embodiment, when the first and second idle axes 324 and 334 are on the same line as the rotation center axes, as shown in FIGS. 3 and 4, So as to allow the two chain base portions to engage the two idle gears of the first to fourth idle gears and move to the other side when the input wedge and the output wedge are moved to one side, It is also possible to engage the gears.
상기와 같이 구성된 실시예2의 자동변속기는 다음과 같이 작동될 수 있다. 이하의 설명에서 정방향은 시계방향이고 역방향은 반시계방향이며, 입력나사축은 왼나사선을 가지고 있고 출력나사축은 오른나사선을 가지고 있는 것으로 하여 작동이 설명될 것이다.The automatic transmission of the second embodiment configured as described above can be operated as follows. In the following description, the operation will be described assuming that the forward direction is the clockwise direction and the reverse direction is the counterclockwise direction, the input screw shaft has the left screw thread, and the output screw shaft has the right screw thread.
1. 제1 내지 제4스톱퍼(329A 329B, 339A, 339B)가 비물림 상태에 있고 제5 및 제6스톱퍼(351, 352)가 물림상태에 있는 경우1. When the first to fourth stoppers 329A 329B, 339A and 339B are in the non-engaged state and the fifth and sixth stoppers 351 and 352 are in the engaged state
이 경우에는 입력축(10)에 의해 입력쇄기부(113)와 입력나사축(111)이 동일한 속도로 함께 역방향으로 회전하게 되고 그리고 출력축(201)에 의해 출력쇄기부(123)와 출력나사축(121)이 동일한 속도로 함께 정방향으로 회전하게 되어, 입력쇄기부(113)와 출력쇄기부(123)는 무부하 상태에 있으며, 이 상태에서 제5 및 제6스톱퍼(351, 352)에 의해 출력축(201)과 출력나사축(121)이 서로 고정되어 있고 입력축(10)과 입력나사축(111)이 서로 고정되어 있어서, 출력쇄기부(123)와 입력쇄기부(113)는 축선방향으로 이동하지 못하고 확실하게 제위치에 유지되게 된다.In this case, the input shaft portion 113 and the input screw shaft 111 rotate in the opposite directions together at the same speed by the input shaft 10 and the output shaft portion 123 and the output screw shaft The input and output chokes 113 and 123 are in a no-load state. In this state, the fifth and sixth stoppers 351 and 352 rotate the output shaft 201 and the output screw shaft 121 are fixed to each other and the input shaft 10 and the input screw shaft 111 are fixed to each other so that the output wedge 123 and the input wedge 113 are not moved in the axial direction And can be held in position without fail.
2. 제5 및 제6스톱퍼(351, 352) 그리고 제1 및 제 3스톱퍼(329A, 339A)가 비물림 상태에 있고, 제2 및 제4스톱퍼(329B, 339B)가 물림상태에 있는 경우2. When the fifth and sixth stoppers 351 and 352 and the first and third stoppers 329A and 339A are in the non-engaged state and the second and fourth stoppers 329B and 339B are in the engaged state
이 경우에는, 구동축(1)이 정방향으로 1번 회전한다고 가정할 때, 입력축(10)과 입력쇄기부(113)가 함께 역방향으로 예를 들면 1회전하게 되고, 출력축(201)과 출력쇄기부(123)가 변속되어 정방향으로 9번 회전하게 되며, 이 때에 출력측에서는 출력나사축구동기어(323)는, 출력나사축기동기어(328) 간의 기어비가 예를 들면 2 ; 1인 경우에, 9번 회전하고 있는 제2정방향피동기어(322)에 의해 역방향으로 18번 회전하게 되어, 결국 출력쇄기부(123)와 출력나사축(121) 간에는 9번의 회전차가 발생되어 출력나사축(121)이 오른나사선을 가진 관계로 상기 출력쇄기부(123)는 풀림방향(도 14에서 좌측방향)으로 A거리 만큼 이동하게 되고, 입력측에서는 정방향구동기어(301)에 의해 역방향내외치기어(302)가 1회 자전하게 되고, 제1유성기어(304)가 1회 고정하게 되고 제1태양기어(303)와 입력나사축(111)이 1회 자전하게 되어, 입력축(10)의 1회전에 의해 입력나사축(111)의 1회전이 상쇄되어 입력나사축(111)이 무부하상태가 된 상태에서, 상기 출력축(201)에 의해 정방향으로 9번 회전하고 있는 제4정방향피동기어(332)가 상기 제4정방향피동기어(332), 제2중간기어(336) 및 제4아이들기어(337) 간의 기어비를 통하여 제1태양기어(303)를 정방향으로 9번 회전시켜서, 입력나사축(111)이 왼나사선을 가진 관계로 상기 입력쇄기부(113)는 풀림방향(도 14에서 좌측방향)으로 A거리 만큼 이동하게 되어, 결국, 입력쇄기부(113)와 출력쇄기부(123)는 동기적으로 함께 좌측으로 출력쇄기부(123)와 출력나사축(121) 간의 속도차 만큼 동일한 축선상의 길이를 이동하게 된다.In this case, assuming that the drive shaft 1 rotates once in the forward direction, the input shaft 10 and the input wobbler 113 are rotated together in the opposite direction, for example, and the output shaft 201 and the output shaft- At this time, on the output side, the output threaded spur gear 323 is engaged with the output screw shaft starting gear 328 at a gear ratio of 2; The first forward driven gear 322 is rotated 18 times in the reverse direction by the second forward driven gear 322 rotating 9 times so that nine rotational differences are generated between the output worm 123 and the output screw shaft 121, The output wedge 123 is moved by a distance A in the unwinding direction (the left direction in Fig. 14), and on the input side, the forward drive gear 301 moves the output wedge 123 in the reverse direction, The first planetary gear 304 is fixed once and the first sun gear 303 and the input screw shaft 111 are rotated once to rotate the input shaft 10 The fourth forward driven gear (the third forward driven gear) is rotated nine times in the forward direction by the output shaft 201 in a state in which one rotation of the input screw shaft 111 is canceled by one rotation and the input screw shaft 111 is in a no- 332) transmits the gear ratio between the fourth forward driven gear 332, the second intermediate gear 336 and the fourth idle gear 337 The first sun gear 303 is rotated nine times in the forward direction so that the input screw shaft 111 has the left screw thread and the input worm shaft portion 113 is rotated by a distance A in the releasing direction The input wobbler 113 and the output wobbler 123 are moved synchronously to the left side along the same axial line by the speed difference between the output wobbler 123 and the output screw shaft 121 do.
3. 제1 및 제 3스톱퍼(329A, 339A)가 물림 상태에 있고, 제5 및 제6스톱퍼(351, 352)그리고 제2 및 제4스톱퍼(329B, 339B)가 비물림상태에 있는 경우3. When the first and third stoppers 329A and 339A are in the engaged state and the fifth and sixth stoppers 351 and 352 and the second and fourth stoppers 329B and 339B are in the non-engagement state
이 경우에는, 구동축(1)이 정방향으로 1번 회전한다고 가정할 때, 입력축(10)과 입력쇄기부(113)가 함께 역방향으로 예를 들면 1회전하게 되고, 출력축(201)과 출력쇄기부(123)가 변속되어 정방향으로 9번 회전하게 되며, 이 때에 출력측에서는 출력나사축구동기어(323)는, 출력나사축기동기어(328) 간의 기어비가 예를 들면 2 ; 1인 경우에, 9번 회전하고 있는 제1정방향피동기어(321)에 의해 정방향으로 18번 회전하게 되어, 결국 출력쇄기부(123)와 출력나사축(121) 간에는 9번의 회전차가 발생되어 출력나사축(121)이 오른나사선을 가진 관계로 상기 출력쇄기부(123)는 체결방향(도 14에서 우측방향)으로 A거리 만큼 이동하게 되고, 입력측에서는 정방향구동기어(301)에 의해 역방향내외치기어(302)가 1회 자전하게 되고, 제1유성기어(304)가 1회 고정하게 되고 제1태양기어(303)와 입력나사축(111)이 1회 자전하게 되어, 입력축(10)의 1회전에 의해 입력나사축(111)의 1회전이 상쇄되어 입력나사축(111)이 무부하상태가 된 상태에서, 상기 출력축(201)에 의해 정방향으로 9번 회전하고 있는 제3정방향피동기어(331)가 제3아이들기어(335) 간의 기어비를 통하여 제1태양기어(303)를 역방향으로 9번 회전시켜서, 입력나사축(111)이 왼나사선을 가진 관계로 상기 입력쇄기부(113)는 체결방향(도 14에서 우측방향)으로 A거리 만큼 이동하게 되어, 결국, 입력쇄기부(113)와 출력쇄기부(123)는 동기적으로 함께 우측으로 출력쇄기부(123)와 출력나사축(121) 간의 속도차 만큼 동일한 축선상의 길이를 이동하게 된다.In this case, assuming that the drive shaft 1 rotates once in the forward direction, the input shaft 10 and the input wobbler 113 are rotated together in the opposite direction, for example, and the output shaft 201 and the output shaft- At this time, on the output side, the output threaded spur gear 323 is engaged with the output screw shaft starting gear 328 at a gear ratio of 2; 1, the first forward driven gear 321 is rotated eight times in the forward direction by the first forward driven gear 321. As a result, nine rotational differences are generated between the output worm 123 and the output screw shaft 121, The output wedge 123 is moved by a distance A in the fastening direction (right direction in Fig. 14), and the forward drive gear 301 moves the reverse output shaft The first planetary gear 304 is fixed once and the first sun gear 303 and the input screw shaft 111 are rotated once to rotate the input shaft 10 A third forward driven gear rotated nine times in the forward direction by the output shaft 201 in a state in which one rotation of the input screw shaft 111 is canceled by one rotation and the input screw shaft 111 is in a no- 331 rotate the first sun gear 303 in the reverse direction nine times through the gear ratio between the third idle gears 335 , The input wedge 113 is moved by a distance A in the fastening direction (rightward in Fig. 14), so that the input wedge 113 and the output wedge 113, The bases 123 move synchronously with each other along the same axial length by the speed difference between the output wedge 123 and the output screw shaft 121 to the right.
상기 실시예2의 설명에서 출력쇄기부(123)의 속도보다 출력나사축(121)이 2배 빠른 속도를 갖는 것을 설명되어 있지만, 2배 늦어도 되고 어떠한 배수로도 될 수 있어서, 산업적으로 구속을 받지 않고 다양한 조건을 만족시킬 수 있다.In the description of the second embodiment, it is described that the speed of the output screw shaft 121 is two times faster than the speed of the output wax 123. However, the speed can be doubled or any multiple can be obtained, Various conditions can be satisfied.
또한, 상기 실시예2의 설명에서 출력나사축이 오른나사선을 가지고 있고 입력나사축이 왼나사선을 가지고 있는 것으로 설명되어 있지만, 본 발명은 이에 한정되지 않고, 출력나사축이 왼나사선을 가지고 있고 입력나사축이 오른나사선을 가질 수도 있고, 또는 모두 동일한 나사선을 가질 수도 있다.In the description of the second embodiment, the output screw shaft has a right screw thread and the input screw shaft has a left screw thread. However, the present invention is not limited to this, and the output screw shaft may have a left- The screw shaft may have a right-hand thread, or both may have the same thread.
전자의 경우에는, 제1 및 제 3스톱퍼(329A, 339A)가 비물림 상태에 있고, 제2 및 제4스톱퍼(329B, 339B)가 물림상태에 있을 때 입력쇄기부(113)와 출력쇄기부(123)가 체결방향으로 이동하게 되고, 제1 및 제 3스톱퍼(329A, 339A)가 물림 상태에 있고, 제2 및 제4스톱퍼(329B, 339B)가 비물림상태에 있는 경우에 있을 때 입력쇄기부(113)와 출력쇄기부(123)가 풀림방향으로 이동하게 된다.In the former case, when the first and third stoppers 329A and 339A are in the non-engaged state and the second and fourth stoppers 329B and 339B are in the engaged state, the input wedge 113 and the output wedge When the first and third stoppers 329A and 339A are in the engaged state and the second and fourth stoppers 329B and 339B are in the unbraided state, The wedge 113 and the output wedge 123 are moved in the unwinding direction.
후자의 경우에는,제1 및 제 4스톱퍼(329A, 339B)가 물림 상태에 있을 때 조임방향(오른나사선)이고, 제2 및 제3스톱퍼(329B, 339A)가 물림상태에 있을 때 풀림방향(오른나사선)이며, 그리고 제1 및 제 4스톱퍼(329A, 339B)가 물림 상태에 있을 때 풀림방향(왼나사선)이고, 제2 및 제3스톱퍼(329B, 339A)가 물림상태에 있을 때 조임방향(왼나사선)이다.In the latter case, when the first and fourth stoppers 329A and 339B are in the engaged state, the fastening direction (right-handed thread) and when the second and third stoppers 329B and 339A are in the engaged state, And the second and third stoppers 329B and 339A are in the engaged state when the first and fourth stoppers 329A and 339B are in the engaged state, (Left-hand line).
상기와 같이 구성된 실시예2의 자동 변속기는 축선방향으로 무한으로 기어비가 다른 기어들을 배열할 수 있어서 무수히 많은 변속비를 제공하는 작용효과를 제공할 수 있다. The automatic transmission according to the second embodiment configured as described above can arrange gears having different gear ratios in an axial direction in an infinite manner, thereby providing an operational effect of providing numerous speed ratios.
상기와 같이 구성된 실시예2의 자동 변속기의 모드전환수단(300)은 다른 실시예로서 다음과 같이 구성될 수 있다.The mode switching means 300 of the automatic transmission according to the second embodiment configured as described above may be configured as another embodiment as follows.
상기 다른 실시예의 자동 변속기의 모드전환수단(300)은 도 5에 도시된 바와 같이, 입력축(10)의 회전방향 및 불변속도와 같은 회전방향과 회전속도로 입력나사축(111)을 회전시키는 동조부(310), 출력축(201)의 회전속도보다 빠른 또는 늦은 속도로 출력나사축(121)을 정방향으로 회전시키는 상대속도차발생부(320), 및 출력축(201)의 변속된 회전수를 입력나사축(111)에 동일한 회전수로 전달하는 연동부(340)를 포함하고 있다.5, the mode switching means 300 of the automatic transmission according to the other embodiment is provided with a tuning means for turning the input screw shaft 111 in the rotational direction and the rotational speed such as the rotational direction and the constant speed of the input shaft 10, A relative speed difference generator 320 for rotating the output screw shaft 121 in a forward direction at a speed that is faster or slower than the rotational speed of the output shaft 201, And an interlocking portion 340 for transmitting the same to the screw shaft 111 at the same rotational speed.
상기 동조부(310)는 실시예2과 같이 상기 구동축(1)에 고정적으로 외접된 정방향구동기어(301), 상기 정방향구동기어(301)에 치합된 역방향내외치기어(302), 상기 입력나사축(111)에 고정적으로 외접된 제1태양기어(303), 및 상기 제1태양기어(303)와 상기 역방향내외치기어(302)에 치합된 제1유성기어(304)를 포함하고 있다.The tuning unit 310 includes a forward drive gear 301 fixedly attached to the drive shaft 1 as in the second embodiment, a reverse oar gear 302 meshing with the forward drive gear 301, A first sun gear 303 fixedly circumscribed to the shaft 111 and a first planetary gear 304 meshing with the first sun gear 303 and the reverse outer gear 302.
상기 상대속도차발생부(320)는 상기 출력축(201)에 고정적으로 외접된 제1정방향피동기어(321), 상기 출력나사축(121)에 고정적으로 외접된 출력나사축구동기어(323), 상기 출력축(201)에 평행하게 배치된 제1아이들축(324), 상기 제1아이들축(324)에 베어링을 개재하여 회전가능하게 외접되어 상기 제1정방향피동기(321)에 치합하는 제1아이들기어(325), 상기 제1아이들축(324)에 베어링을 개재하여 회전가능하게 외접되어 상기 출력나사축구동기어(323)에 치합하는 출력나사축기동기어(328)을 포함하고 있다.The relative speed difference generator 320 includes a first forward driven gear 321 fixedly circumscribed to the output shaft 201, an output screw driven gear 323 fixedly connected to the output screw shaft 121, A first idle shaft 324 disposed parallel to the output shaft 201 and a second idle shaft 324 rotatably circumscribed by the first idle shaft 324 via a bearing and meshing with the first forwardly- An idle gear 325 and an output screw shaft starting gear 328 rotatably circumscribed by the first idle shaft 324 via a bearing and meshing with the output screw driven gear 323.
또한, 상기 상대속도차발생부(320)는 선택적으로 상기 제1아이들축(324)에 제1아이들기어(325)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제1스톱퍼(329A)와 그리고 선택적으로 상기 제1아이들축(324)에 상기 출력나사축기동기어(328)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제7스톱퍼(329)를 더 포함하고 있다.The relative speed difference generator 320 may selectively include a first stopper 329A that engages the first idle gear 325 on the first idle shaft 324 to rotate or idle the first idle gear 325, And a seventh stopper 329 that engages the output screw shaft starting gear 328 with the first idle shaft 324 and rotates or idles them together.
상기 연동부(340)는 상기 출력축(201)에 고정적으로 외접된 제3정방향피동기어(331), 상기 제1유성기어(304)에 고정적으로 내접된 유성기어축(305)에 고정적으로 외접된 제2유성기어(306)에 치합된 제2태양기어(333), 상기 출력축(201)에 평행하게 배치되어 상기 제2태양기어(333)에 고정적으로 내접된 제2아이들축(334), 상기 제2아이들축(334)에 베어링을 개재하여 회전가능하게 외접되어 상기 제3정방향피동기어(331)에 치합하는 제3아이들기어(335) 및 상기 제2아이들축(334)에 회전가능하게 외접되어 제2중간기어(336)를 경유하여 상기 제4정방향피동기어(332)에 치합하는 제4아이들기어(337)를 포함하고 있다.The linkage unit 340 includes a third forward driven gear 331 fixedly circumscribed to the output shaft 201 and a third forward driven driven gear 331 fixedly circumscribed to the planetary gear shaft 305 fixedly inscribed on the first planetary gear 304 A second idle gear 333 meshed with the second planetary gear 306 and a second idle shaft 334 disposed parallel to the output shaft 201 and fixedly inscribed in the second sun gear 333, A third idle gear 335 rotatably circumscribed by a second idle shaft 334 via a bearing and meshing with the third forward driven gear 331 and a third idle gear 335 rotatably circumscribed by the second idle shaft 334 And a fourth idle gear 337 meshing with the fourth forward driven gear 332 via a second intermediate gear 336. [
또한, 상기 연동부(340)는 선택적으로 상기 제2아이들축(334)에 제3아이들기어(335)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제3스톱퍼(339A)와 그리고 선택적으로 상기 제2아이들축(334)에 제2아이들기어(337)를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제4스톱퍼(339B)를 더 포함하고 있다.The interlocking portion 340 may optionally include a third stopper 339A that engages the third idle gear 335 on the second idle shaft 334 to cause them to rotate or idle together, And a fourth stopper 339B that engages the second idle gear 337 on the idle shaft 334 and rotates or idles them together.
상기 제1태양기어(303)는 상기 정방향구동기어(301), 상기 역방향내외지치기어(302), 상기 제1유성기어(304) 및 상기 제1태양기어(303) 간의 기어비를 통하여 입력축(10)이 역방향으로 1회전할 때 역방향으로 1회전할 수 있도록 되어 있다.The first sun gear 303 is connected to the input shaft 10 through the gear ratio between the forward drive gear 301, the reverse internal and external ground gear 302, the first planetary gear 304 and the first sun gear 303. ) Can make one revolution in the reverse direction when making one revolution in the reverse direction.
또한, 상기 출력나사축구동기어(323)은 상기 출력나사축기동기어(328)와의 기어비를 통하여 출력나사축(121)이 상기 출력축(201)보다 몇배 빠르게 또는 몇배 느리게 회전할 수 있도록 되어 있다.The output screw shaft driving gear 323 can rotate the output screw shaft 121 several times faster or several times slower than the output shaft 201 through the gear ratio with the output screw shaft starting gear 328.
또한, 상기 제1태양기어(303)는 상기 제4정방향피동기어(332), 제2중간기어(336) 및 제4아이들기어(337) 간의 기어비를 통하여 그리고 제2태양기어(333), 제2유성기어(306), 제1유성기어(304) 및 상기 제1태양기어(303) 간의 기어비를 통하여 상기 출력나사축(121)과 상기 출력축(201) 간의 회전속도차 만큼의 속도로 회전할 수 있도록 되어 있다.The first sun gear 303 is connected to the second sun gear 333 via the gear ratio between the fourth forward driven gear 332, the second intermediate gear 336 and the fourth idler gear 337, The output shaft 201 rotates at a speed corresponding to the rotational speed difference between the output screw shaft 121 and the output shaft 201 through the gear ratio between the planetary gear 306, the first planetary gear 304 and the first sun gear 303 .
또한, 상기 제1태양기어(303)는 상기 제3정방향피동기어(331)와 제3아이들기어(335) 간의 기어비를 통하여 그리고 제2태양기어(333), 제2유성기어(306), 제1유성기어(304) 및 상기 제1태양기어(303) 간의 기어비를 통하여 상기 출력축(201)의 회전수와 동일한 회전수로 회전할 수 있도록 되어 있다.The first sun gear 303 is connected to the third forward gear 331 through the third forward gear 331 and the third idler gear 335 via the gear ratio between the third forward gear 331 and the third idler gear 335, 1 planetary gear 304 and the first sun gear 303 at the same rotational speed as that of the output shaft 201. [
또한, 입력나사축(111)은 도 5에 왼사나선으로 도시되어 있지만, 오른나사선을 가지고 있고, 출력나사축(121)은 실시예2와 같이 오른나사선을 가지고 있다.5, the input screw shaft 111 has a right screw thread, and the output screw shaft 121 has a right screw thread as in the second embodiment.
또한, 상기 다른 실시예의 자동 변속기의 모드전환수단(300)은 도 5에 도시된 바와 같이, 출력나사축(121) 또는 출력나사축구동기어(323)를 선택적으로 회전하지 못하게 하는 제8스톱퍼(360)을 더 포함하고 있다.5, the mode switching means 300 of the automatic transmission of the other embodiment is provided with an eighth stopper (not shown) for preventing the output screw shaft 121 or the output screw moving gear 323 from selectively rotating, 360).
상기 제8스톱퍼(360)는 도 5에 도시된 바와 같이, 베이스에 고정되어 자화되면 상기 출력나사축구동기어(323)와 결합되어 상기 출력나사축구동기어(323)을 회전하지 못하게 하고 자화되지 않으면, 상기 출력나사축구동기어(323)와의 결합이 해제되어 상기 출력나사축구동기어(323)이 회전될 수 있게 하는 전자척이 될 수 있다.5, when the eighth stopper 360 is magnetized, the eighth stopper 360 is engaged with the output screw motion synchronizing gear 323 so as not to rotate the output screw synchronizing gear 323 and is not magnetized The output screw baseball gear 323 may be disengaged from the output screw baseball gear 323 so that the output screw baseball gear 323 may be rotated.
상기 다른 실시예의 자동 변속기의 모드전환수단(300)의 나머지 구성은 실시예2의 모드전환수단(300)의 구성과 동일하다.The remaining configuration of the mode switching means 300 of the automatic transmission of the other embodiment is the same as that of the mode switching means 300 of the second embodiment.
상기와 같이 구성된 다른 실시예의 자동변속기는 다음과 같이 작동될 수 있다. 이하의 설명에서 정방향은 시계방향이고 역방향은 반시계방향이며, 도 5에 왼사나선으로 도시된 입력나사축은 오른나사선을 가지고 있고, 출력나사축은 오른나사선을 가지고 있는 것으로 하여 작동이 설명될 것이다.The automatic transmission of another embodiment configured as above can be operated as follows. In the following description, the operation will be described assuming that the forward direction is the clockwise direction and the reverse direction is the counterclockwise direction, the input screw shaft shown with the left-hand spiral in FIG. 5 has a right-hand thread and the output screw shaft has a right-hand thread.
1. 제1, 제3, 제4, 제 7 및 제8스톱퍼(329A, 339A, 339B, 329, 360)가 비물림 상태에 있고 제5 및 제6스톱퍼(351, 352)가 물림상태에 있는 경우1. When the first, third, fourth, seventh and eighth stoppers 329A, 339A, 339B, 329 and 360 are in the non-engaged state and the fifth and sixth stoppers 351 and 352 are in the engaged state Occation
이 경우는 제1실시예와 동일하게 출력쇄기너트(123)과 입력쇄기너트(113)는 축선방향으로 이동하기 못하고 확실하게 제위치에 유지되게 된다.In this case, as in the first embodiment, the output wedge nut 123 and the input wedge nut 113 can not be moved in the axial direction and are reliably held in place.
2. 제5 및 제6스톱퍼(351, 352) 그리고 제1, 제4, 및 제7스톱퍼(329A, 339B, 329)가 비물림 상태에 있고, 제3스톱퍼(339A)와 제8스톱퍼(360)가 물림상태에 있는 경우2. The fifth and sixth stoppers 351 and 352 and the first, fourth and seventh stoppers 329A and 339B and 329 are in the non-engaged state and the third stopper 339A and the eighth stopper 360 ) Is in a stuck state
이 경우에는, 구동축(1)이 정방향으로 1번 회전한다고 가정할 때, 입력축(10)과 입력쇄기부(113)가 함께 역방향으로 예를 들면 1회전하게 되고, 출력축(201)과 출력쇄기부(123)가 변속되어 정방향으로 9번 회전하게 되며, 이 때에 출력측에서는 출력나사축구동기어(323)가 제8스톱퍼(360)에 의해 회전하지 못하여 출력나사축(121)이 정지가 되어 결국 출력쇄기부(123)와 출력나사축(121) 간에는 9번의 회전차가 발생되어 출력나사축(121)이 오른나사선을 가진 관계로 상기 출력쇄기부(123)는 자체의 정방향 회전에 의해 풀림방향(도 16에서 좌측방향)으로 A거리 만큼 이동하게 되고, 입력측에서는 정방향구동기어(301)에 의해 역방향내외치기어(302)가 1회 자전하게 되고, 제1유성기어(304)가 1회 고정하게 되고 제1태양기어(303)과 입력나사축(111)이 1회 자전하게 되어, 입력축(10)의 1회전에 의해 입력나사축(111)의 1회전이 상세되어 입력나사축(111)이 무부하상태가 된 상태에서, 상기 출력축(201)에 의해 정방향으로 9번 회전하고 있는 제3정방향피동기어(331)가 상기 제3정방향피동기어(331)와 제3아이들기어(335) 간의 기어비를 통하여 그리고 제2태양기어(333), 제2유성기어(306), 제1유성기어(304) 및 상기 제1태양기어(303) 간의 기어비를 통하여 제1태양기어(303)를 역방향으로 9번 회전시켜서, 입력나사축(111)이 오른나사선을 가진 관계로 상기 입력쇄기부(113)는 풀림방향(도 3에서 좌측방향)으로 A거리 만큼 이동하게 되어, 결국, 입력쇄기부(113)와 출력쇄기부(123)는 동기적으로 함께 좌측으로 출력쇄기부(123)와 출력나사축(121) 간의 속도차 만큼 동일한 축선상의 길이를 이동하게 된다.In this case, assuming that the drive shaft 1 rotates once in the forward direction, the input shaft 10 and the input wobbler 113 are rotated together in the opposite direction, for example, and the output shaft 201 and the output shaft- The output screw shaft 323 is not rotated by the eighth stopper 360 and the output screw shaft 121 is stopped at the output side, Since the output shaft 121 has a right-hand thread, the output worm 123 is rotated in its forward direction by the rotation of the output worm 123 in the forward direction 16 in the left direction). On the input side, the reverse-direction external gear 302 is rotated once by the forward-direction drive gear 301, and the first planetary gear 304 is once fixed The first sun gear 303 and the input screw shaft 111 rotate once, and the input shaft 10 And the third forward direction driven by the output shaft 201 in the forward rotational direction by the output shaft 201 in a state in which one rotation of the input screw shaft 111 is detailed by one rotation of the output shaft 201 and the input screw shaft 111 is in a no- The gear 331 is connected to the second sun gear 333, the second planetary gear 306 and the first planetary gear 304 via the gear ratio between the third forward driven gear 331 and the third idle gear 335, The first sun gear 303 is rotated nine times in the reverse direction through the gear ratio between the first sun gear 303 and the first sun gear 303 so that the input shaft 111 has a right- The input wobbler 113 and the output wobbler 123 are synchronously moved to the left side together by the output wobbler 123 and the output worm shaft 121 (left side in Fig. 3) ) In the direction of the axis.
3. 제5 및 제6스톱퍼(351, 352) 그리고 제3스톱퍼(339A)와 제8스톱퍼(360)가 비물림 상태에 있고, 제1, 제4, 및 제7스톱퍼(329A, 339B, 329)가 물림상태에 있는 경우3. The fifth and sixth stoppers 351 and 352 and the third stopper 339A and the eighth stopper 360 are in the non-engagement state and the first, fourth and seventh stoppers 329A, 339B and 329 ) Is in a stuck state
이 경우에는, 구동축(1)이 정방향으로 1번 회전한다고 가정할 때, 입력축(10)과 입력쇄기부(113)가 함께 역방향으로 예를 들면 1회전하게 되고, 출력축(201)과 출력쇄기부(123)가 변속되어 정방향으로 9번 회전하게 되며, 이 때에 출력측에서는 출력나사축구동기어(323)는, 출력나사축기동기어(328) 간의 기어비가 예를 들면 2 ; 1인 경우에, 9번 회전하고 있는 제1정방향피동기어(321)에 의해 정방향으로 18번 회전하게 되어, 결국 출력쇄기부(123)와 출력나사축(121) 간에는 9번의 회전차가 발생되어 출력나사축(121)이 오른나사선을 가진 관계로 상기 출력쇄기부(123)는 체결방향(도 16에서 우측방향)으로 A거리 만큼 이동하게 되고, 입력측에서는 정방향구동기어(301)에 의해 역방향내외치기어(302)가 1회 자전하게 되고, 제1유성기어(304)가 1회 고정하게 되고 제1태양기어(303)과 입력나사축(111)이 1회 자전하게 되어, 입력축(10)의 1회전에 의해 입력나사축(111)의 1회전이 상세되어 입력나사축(111)이 무부하상태가 된 상태에서, 상기 출력축(201)에 의해 정방향으로 9번 회전하고 있는 제4정방향피동기어(332)가 상기 제4정방향피동기어(332), 제2중간기어(336) 및 제4아이들기어(337) 간의 기어비를 통하여 그리고 제2태양기어(333), 제2유성기어(306), 제1유성기어(304) 및 상기 제1태양기어(303) 간의 기어비를 통하여 제1태양기어(303)를 정방향으로 9번 회전시켜서, 입력나사축(111)이 오른나사선을 가진 관계로 상기 입력쇄기부(113)는 체결방향(도 16에서 우측방향)으로 A거리 만큼 이동하게 되어, 결국, 입력쇄기부(113)와 출력쇄기부(123)는 동기적으로 함께 우측으로 출력쇄기부(123)과 출력나사축(121) 간의 속도차 만큼 동일한 축선상의 길이를 이동하게 된다.In this case, assuming that the drive shaft 1 rotates once in the forward direction, the input shaft 10 and the input wobbler 113 are rotated together in the opposite direction, for example, and the output shaft 201 and the output shaft- At this time, on the output side, the output threaded spur gear 323 is engaged with the output screw shaft starting gear 328 at a gear ratio of 2; 1, the first forward driven gear 321 is rotated eight times in the forward direction by the first forward driven gear 321. As a result, nine rotational differences are generated between the output worm 123 and the output screw shaft 121, The output wedge 123 is moved by a distance A in the fastening direction (right direction in FIG. 16), and the input side is rotated by the forward drive gear 301 to rotate the reverse external gear The first planetary gear 304 is fixed once and the first sun gear 303 and the input screw shaft 111 rotate once so that the rotation of the input shaft 10 One fourth rotation of the input shaft of the input shaft is performed by one rotation and the fourth forward driven gear rotated nine times in the forward direction by the output shaft 201 in a state in which the input shaft is in a no- 332) transmits the gear ratio between the fourth forward driven gear 332, the second intermediate gear 336 and the fourth idle gear 337 The first sun gear 303 is rotated in the forward direction 9 times through the gear ratio between the second sun gear 333, the second planetary gear 306, the first planetary gear 304 and the first sun gear 303, The input wedge 113 is moved by a distance A in the fastening direction (right direction in Fig. 16), so that the input wedge 113 and the input wedge 113 are moved The output wobbling portion 123 moves synchronously with the output wobbling portion 123 and the output worm shaft 121 to the right side along the same axial length by the speed difference.
상기 다른 실시예의 설명에서 출력쇄기부(123)의 속도보다 출력나사축(121)이 2배 빠른 속도를 갖는 것을 설명되어 있지만, 2배 늦어도 되고 어떠한 배수로도 될 수 있어서, 산업적으로 구속을 받지 않고 다양한 조건을 만족시킬 수 있다.In the description of the other embodiments, it is described that the output screw shaft 121 has a speed two times faster than the output worm 123, but it can be doubled or any other multiple, so that it is not industrially restricted Various conditions can be satisfied.
또한, 상기 다른 실시예의 설명에서 출력나사축이 오른나사선을 가지고 있고 입력나사축이 오른나사선을 가지고 있는 것으로 설명되어 있지만, 본 발명은 이에 한정되지 않고, 실시예3에서 설명된 바와 같이, 출력나사축이 왼나사선을 가지고 있고 입력나사축이 오른나사선을 가질 수도 있고, 또는 출력나사축이 오른나사선을 가지고 있고 입력나사축이 왼나사선을 가질 수도 있다.In the description of the other embodiments, the output screw shaft has a right screw thread and the input screw shaft has a right screw thread. However, the present invention is not limited to this, and as described in the third embodiment, The shaft may have a left-hand thread and the input screw shaft may have a right-hand thread, or the output screw shaft may have a right-hand thread and the input screw shaft may have a left-hand thread.
상기 실시예2 및 다른 실시예의 자동변속기는 복수개의 구동기어 중 하나의 구동기어에 의해 피동기어를 통하여 피동축에 구동력을 전달하여도, 피동축에 외접된 복수개의 피동기어들 중 상기 하나의 구동기어에 맞물림된 피동기어만 피동축에 구동력을 전달하게 되고, 다른 피동기어들은 헛돌게 하거나 제위치에 유지되게 하여, 다른 피동기어의 중량에 의한 회전방향에서의 부하를 피동축에 부여하지 않아, 실시예1의 자동변속기 보다도 작은 구동력을 갖고서 피동축에 전달하게 하는 가능하게 하여, 제조단가 및 유지보수비용을 절감하면서도, 구동용 쇄기부와 피동용 쇄기부를 자체의 동력원에 의해 동기적으로 그리고 동일한 속도로 축선방향으로 이동시키는 모드전환수단이 기어비를 자유롭게 조절하는 것을 가능하게 하여, 산업적으로 적용하기 위한 다양성이 증대시킬 수 있다.The automatic transmission of the second embodiment and another embodiment of the present invention is configured such that 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 gear transmits the driving force to the driven shaft and the other driven gears are idle or held in position so that the load in the rotational direction by the weight of the other driven gear is not given to the driven shaft, The drive chain base and the driven chain base can be synchronously moved by their own power sources while reducing the manufacturing cost and maintenance cost by enabling the transmission to be transmitted to the driven shaft with a drive force smaller than that of the automatic transmission of the first embodiment Mode switching means for shifting in the axial direction at the same speed makes it possible to freely adjust the gear ratio, There are a variety to be increased.

Claims (16)

  1. 입력축에 외접된 서로 직경을 달리하는 복수개의 입력기어로 이루어진 입력기어군;An input device group including a plurality of input gears circumscribed on an input shaft and having diameters different from each other;
    출력축에 외접되어 상기 입력기어군과 치합된 서로 직경을 달리 하는 복수개의 축력기어로 이루어진 출력기어군; An output gear member circumscribed to the output shaft and having a plurality of axial gears meshed with the input gear member and having diameters different from each other;
    서로 치합하는 입력기어군의 입력기어 각각 및 출력기어군의 출력기어 각각 중 어느 하나의 기어와 상기 어느 하나의 기어에 내접된 입력축 또는 출력축 사이에 각각 개재된 복수개의 일방향클러치; 및A plurality of one-way clutches interposed between any one of an input gear of an input gear group that meshes with each other and an output gear of an output gear group and an input shaft or an output shaft that are inscribed in either one of the gears; And
    상기 입력기어군 및 상기 출력기어군 중 적어도 어느 하나의 기어군의 복수개의 기어들중 선택적으로 어느 하나를 물림하거나, 또는 복수개의 일방향클러치의 인너레이스 중 선택적으로 어느 하나를 물림하는 물림클러치를 구비한 자동 변속기로서,And an automatic clutch having a clutch engaged to selectively engage either one of a plurality of gears of at least one of the input gear group and the output gear group or an inner race of a plurality of one- As a transmission,
    상기 입력축과 상기 출력축 중 적어도 어느 하나의 축은 관형축이고, Wherein at least one of the input shaft and the output shaft is a tubular shaft,
    상기 적어도 하나의 관형축에 외접된 상기 입력기어군의 복수개의 입력기어 또는 상기 출력기어군의 복수개의 출력기어 각각은 상기 적어도 하나의 관형축에 대하여 회전가능하고,Each of the plurality of input gears of the input gear group circumscribed to the at least one tubular shaft or the plurality of output gears of the output gear group is rotatable with respect to the at least one tubular shaft,
    상기 물림클러치는 The biting clutch
    상기 적어도 하나의 관형축 내에서 병진수단에 의해 상기 적어도 하나의 관형축의 축선방향으로 이동가능한 쇄기부;A chaining base movable in the axial direction of said at least one tubular axis by said translating means in said at least one tubular axis;
    상기 적어도 하나의 관형축에 외접된 상기 입력기어군의 복수개의 입력기어 또는 상기 출력기어군의 복수개의 출력기어 각각의 내주면에 또는 상기 적어도 하나의 관형축 중 하나의 관형축에 외접된 복수개의 일방향클러치 각각의 인너레이스의 내주면에 형성된 하나 또는 복수개의 요부; 및 A plurality of one-way clutches circumscribed on an inner circumferential surface of each of the plurality of input gears of the input gear group circumscribed to the at least one tubular shaft or a plurality of output gears of the output gear group or one of the at least one tubular shaft, One or a plurality of recessed portions formed on an inner peripheral surface of the inner race; And
    상기 하나 또는 복수개의 요부와 마주하는 상기 적어도 하나의 관형축의 부위에 축선방향으로 이격되어 형성된 복수개의 관통구멍 각각에 방사상 안쪽 부위가 삽입 안착되어, 상기 쇄기부에 의해 선택적으로 반경바깥방향으로 밀어져서 가압을 받게 되면 상기 하나 또는 복수개의 요부 중 마주하는 하나 또는 복수개의 요부 각각에 일부가 삽입되는 복수개의 출몰부재를 포함하고,A radially inner portion is inserted and seated in each of a plurality of through holes axially spaced apart from each other at a portion of the at least one tubular axis facing the one or more recesses, and is selectively pushed radially outward by the chain base portion And a plurality of protruding and retracting members partially inserted into each of the one or the plurality of facing recesses of the one or more recessed portions when pressed,
    상기 쇄기부의 축선방향 길이가 축선방향으로 인접한 적어도 2개의 출몰부재를 접촉할 수 있는 길이를 갖고,The axially extending length of the chain base portion has a length capable of contacting at least two protruding members adjacent in the axial direction,
    상기 복수개의 출몰부재는 반경방향 양쪽이 둥근면으로 되어 있는 것을 특징으로 하는 자동 변속기. Wherein the plurality of protruding and retracting members are rounded on both sides in the radial direction.
  2. 제 1항에 있어서, The method according to claim 1,
    상기 관형축에 형성된 복수개의 관통구멍은 관형축의 길이방향으로 일 피치 내에서 복수개의 나선줄 배열을 갖도록 복수개의 나선줄로 배치된 상태에서, 관형축의 둘레방향으로 동일한 위상차를 가지고서 복수개 배열되어 있는 것을 특징으로 하는 물림클러치. A plurality of through holes formed in the tubular shaft are arranged in a plurality of helical lines so as to have a plurality of helical filament arrangements within a pitch in the longitudinal direction of the tubular axes and a plurality of through holes are arranged with the same phase difference in the circumferential direction of the tubular axis Bite clutch with feature.
  3. 제 1항에 있어서,The method according to claim 1,
    상기 하나 또는 복수개의 요부 각각에 탄성체를 개재하여 삽입되어 탄성적으로 반경방향으로 이동하는 복수개의 스페이서를 더 포함하고 있고, Further comprising a plurality of spacers which are elastically inserted into the one or more recesses to elastically move in the radial direction,
    상기 복수개의 스페이서는 상기 복수개의 출몰부재가 상기 쇄기부에 의해 반경바깥방향으로 밀어지게 되면, 상기 복수개의 출몰부재에 의해 반경바깥방향으로 밀어지게 되어 있는 것을 특징으로 하는 자동 변속기.Wherein the plurality of spacers are pushed outward in the radial direction by the plurality of protruding / retracting members when the plurality of protruding / retracting members are pushed outward in the radial direction by the chain base.
  4. 제 1항에 있어서,The method according to claim 1,
    상기 복수개의 관통구멍 각각의 반경방향 안쪽의 구경이 상기 복수개의 출몰부재 각각이 일부만 삽입되고 상기 복수개의 출몰부재 각각의 전체가 관통될 수 없는 크기로 되어 절두원추형의 형상을 갖은 상태에서, 상기 복수개의 관통구멍은 상기 복수개의 출몰부재 각각과 미끄럼접촉하고 있으며,The plurality of through-holes each having a diameter inwardly in the radial direction is formed such that a part of each of the plurality of the protruding / retracting members is inserted and the entirety of each of the plurality of protruding / Each of the through holes being in sliding contact with each of the plurality of protruding /
    상기 복수개의 출몰부재는 볼이거나, 절두형상부를 갖되 반경방향 양단이 둥근 돌출부를 갖거나, 직경을 달리하는 복수개의 볼이거나, 또는 상기 복수개의 관통구멍 각각의 반경방향 바깥 단이 둥근 돌출부를 갖는 상태에서 상기 복수개의 관통구멍 각각의 반경방향 외측에 배치된 절두형상부와 상기 복수개의 관통구멍 각각의 반경방향 내측에 배치된 볼을 포함하는 것을 특징으로 하는 물림클러치. The plurality of protruding and retracting members may be balls or a plurality of balls each having a truncated conical shape but having rounded protrusions at both ends in the radial direction, or a plurality of balls having different diameters, or each of the plurality of through holes may have a rounded protrusion And a ball disposed radially inwardly of each of the plurality of through holes and disposed in a radially outer side of each of the plurality of through holes.
  5. 제 1항에 있어서,The method according to claim 1,
    상기 병진수단는 볼스크류, 실린더 또는 선형모터인 것을 특징으로 하는 자동 변속기.Wherein the translating means is a ball screw, a cylinder, or a linear motor.
  6. 제 1항에 있어서,The method according to claim 1,
    상기 입력축과 상기 출력축은 모두 관형축이고, Wherein the input shaft and the output shaft are both tubular shafts,
    상기 물림클러치는 입력축에 회전가능하게 외접된 복수개의 입력기어중 인접한 2개의 기어를 물림하거나 또는 상기 입력기어에 내접된 상기 일방향클러치를 물림하는 입력물림클러치; 및 출력축에 회전가능하게 외접된 복수개의 출력기어중 인접한 2개의 기어를 물림하거나 또는 상기 출력기어에 내접된 상기 일방향클러치를 물림하는 출력물림클러치;를 포함하고,Wherein the engaging clutch comprises: an input clutch that engages two adjacent gears among a plurality of input gears rotatably circumscribed by the input shaft, or engages the one-way clutch inscribed in the input gear; And an output clutch which engages two adjacent gears among a plurality of output gears rotatably circumscribed by the output shaft, or engages the one-way clutch inscribed in the output gear,
    상기 입력물림클러치와 상기 출력물림클러치 각각은 Each of the input clutch and the output clutch
    상기 입력축과 상기 출력축 내에 회전가능하게 장착된 입력나사축과 출력나사축에 치합되어 축선방향으로 이동가능한 너트인 입력쇄기부와 출력쇄기부를 포함하고,And an output wedge portion and an output wedge portion that are engaged with an input screw shaft and are movable in an axial direction, the input wedge portion and the output wedge portion being rotatably mounted in the input shaft and the output shaft,
    상기 입력물림클러치의 입력쇄기부와 상기 출력물림클러치의 출력쇄기부는 모드전환수단에 의해 입력축과 출력축에서 축선방향에서 동일한 방향으로 서로 동기적으로 각각 이동하며,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 by the mode switching means,
    상기 입력쇄기부의 축선방향 길이는 저속단에서 고속단으로의 변속시에 그리고 고속단에서 저속으로의 변속시에 상기 입력축 내에서 이웃하는 2개의 입력출몰부재에 대한 가압을 유지할 수 있는 길이를 가지고 있고,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,
    상기 출력쇄기부의 축선방향 길이는 저속단에서 고속단으로의 변속시에 그리고 고속단에서 저속으로의 변속시에 상기 출력축 내에서 이웃하는 2개의 출력출몰부재에 대한 가압을 유지할 수 있는 길이를 가지고 있고,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 However,
    상기 모드전환수단은 The mode switching means
    상기 입력축의 회전방향 및 불변속도와 같은 회전방향과 회전속도로 입력나사축을 회전시키는 동조부, A tuning unit for rotating the input screw shaft at a rotational direction and a rotational speed same as the rotational direction and the constant speed of the input shaft,
    출력축의 회전속도보다 빠른 또는 늦은 속도로 출력나사축을 정역방향으로 회전시키는 상대속도차발생부, 및 A relative speed difference generator for rotating the output screw shaft in forward and reverse directions at a speed that is earlier or later than the rotational speed of the output shaft,
    출력나사축과 출력쇄기부 간의 상대속도 차이 만큼 출력축의 회전수를 입력나사축에 전달하는 상대속도차전달부를 포함하고 있는 것을 특징으로 하는 자동 변속기. And a relative speed difference transmitting portion for transmitting the rotational speed of the output shaft to the input screw shaft by a relative speed difference between the output screw shaft and the output worm shaft portion.
  7. 제 1항에 있어서,The method according to claim 1,
    상기 입력축과 상기 출력축은 모두 관형축이고, Wherein the input shaft and the output shaft are both tubular shafts,
    상기 물림클러치는 입력축에 회전가능하게 외접된 복수개의 입력기어중 인접한 2개의 기어를 물림하거나 또는 상기 입력기어에 내접된 상기 일방향클러치를 물림하는 입력물림클러치; 및 출력축에 회전가능하게 외접된 복수개의 출력기어중 인접한 2개의 기어를 물림하거나 또는 상기 출력기어에 내접된 상기 일방향클러치를 물림하는 출력물림클러치;를 포함하고,Wherein the engaging clutch comprises: an input clutch that engages two adjacent gears among a plurality of input gears rotatably circumscribed by the input shaft, or engages the one-way clutch inscribed in the input gear; And an output clutch which engages two adjacent gears among a plurality of output gears rotatably circumscribed by the output shaft, or engages the one-way clutch inscribed in the output gear,
    상기 입력물림클러치와 상기 출력물림클러치 각각은 Each of the input clutch and the output clutch
    상기 입력축와 상기 출력축 내에 회전가능하게 장착된 입력나사축과 출력나사축에 치합되어 축선방향으로 이동가능한 너트인 입력쇄기부와 출력쇄기부를 포함하고,And an input worm shaft rotatably mounted on the input shaft and the output shaft and an input worm wheel and an output worm wheel which are engaged with an output screw shaft and are movable in an axial direction,
    상기 입력물림클러치의 입력쇄기부와 상기 출력물림클러치의 출력쇄기부는 모드전환수단에 의해 입력축과 출력축에서 축선방향에서 동일한 방향으로 서로 동기적으로 각각 이동하며,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 by the mode switching means,
    상기 입력쇄기부의 축선방향 길이는 저속단에서 고속단으로의 변속시에 그리고 고속단에서 저속으로의 변속시에 상기 입력축 내에서 이웃하는 2개의 입력출몰부재에 대한 가압을 유지할 수 있는 길이를 가지고 있고,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,
    상기 출력쇄기부의 축선방향 길이는 저속단에서 고속단으로의 변속시에 그리고 고속단에서 저속으로의 변속시에 상기 출력축 내에서 이웃하는 2개의 출력출몰부재에 대한 가압을 유지할 수 있는 길이를 가지고 있고,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 However,
    상기 모드전환수단은 The mode switching means
    상기 입력축의 회전방향 및 불변속도와 같은 회전방향과 회전속도로 상기 입력나사축을 회전시키는 동조부, A tuning unit for rotating the input screw shaft at a rotational direction and a rotational speed same as the rotational direction and the constant speed of the input shaft,
    상기 출력축의 회전속도보다 빠른 또는 늦은 속도로 출력나사축을 정방향으로 회전시키는 상대속도차발생부, A relative speed difference generator for rotating the output screw shaft in a forward direction at a speed that is earlier or later than the rotational speed of the output shaft,
    상기 출력축의 변속된 회전수를 상기 입력나사축에 동일한 회전수로 전달하는 연동부 및 An interlocking portion for transmitting the shifted rotational speed of the output shaft to the input screw shaft at the same rotational speed,
    상기 출력나사축을 선택적으로 회전하지 못하게 하는 제8스톱퍼를 포함하고 있는 것을 특징으로 하는 자동 변속기.And an eighth stopper for preventing the output screw shaft from being selectively rotated.
  8. 제 6항 또는 제 7항에 있어서, 8. The method according to claim 6 or 7,
    상기 입력쇄기부와 상기 출력쇄기부의 위치는, 입력축의 축선방향에서 동일한 위치에 위치결정되거나, 또는 하나의 입력기어와 이에 맞물리는 하나의 출력기어를 사이에 두고 상기 하나의 입력기어에 바로 인접한 상기 하나의 입력기어보다 작은 직경의 다른 하나의 입력기어를 상기 하나의 입력기어와 동시에 물림할 수 있는 위치에 상기 입력쇄기부가 위치결정되어 있고 그리고 상기 하나의 출력기어에 바로 인접한 상기 하나의 출력기어보다 작은 직경의 다른 하나의 출력기어를 상기 하나의 출력기어와 동시에 물림할 수 있는 위치에 상기 출력쇄기부가 위치결정되어서, 상기 입력쇄기부와 상기 출력쇄기부에 의해 동시에 물려서 서로 치합하고 있는 하나의 입력기어와 출력기어가 상기 입력쇄기부와 상기 출력쇄기부 중 어느 하나의 쇄기부와 물려서 서로 치합하고 있는 다른 하나의 입력기어 또는 다른 하나의 출력기어의 직경보다 큰 직경을 가지게 배치되어 있는 것을 특징으로 하는 자동 변속기.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 wedge portion 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, and the one output gear is positioned immediately adjacent to the one output gear The output wedge portion is positioned at a position where the other output gear having a diameter smaller than that of the gear can be engaged with the one output gear at the same time so that the input wedge portion and the output wedge portion are simultaneously engaged and mated with each other One input gear and one output gear are connected to either one of the input chaining portion and the output chaining portion, Standing in the other of the input gear or the other of the output, it characterized in that the automatic transmission is arranged to have a diameter larger than the diameter of the gears combined values with each other.
  9. 제 6항 또는 제 7항에 있어서,8. The method according to claim 6 or 7,
    상기 동조부는 상기 구동축에 고정적으로 외접된 정방향구동기어, 상기 정방향구동기어에 치합된 역방향내외치기어, 상기 입력나사축에 고정적으로 외접된 제1태양기어, 및 상기 제1태양기어와 상기 역방향내외치기어에 치합된 제1유성기어를 포함하고 있는 것을 특징으로 하는 자동 변속기.A first sun gear fixedly circumscribed to the input screw shaft; and a second sun gear fixedly attached to the input shaft shaft, and a second sun gear fixedly connected to the first sun gear and the reverse inner and outer gears And a first planetary gear engaged with the gear teeth.
  10. 제 6항 또는 제 7항에 있어서,8. The method according to claim 6 or 7,
    상기 상대속도차발생부는 The relative speed difference generator
    상기 출력축에 고정적으로 외접된 제1 및 제2정방향피동기어, First and second forward driven gears fixedly circumscribed to the output shaft,
    상기 출력나사축에 고정적으로 외접된 출력나사축구동기어, An output screw coaxial gear fixedly circumscribed to the output screw shaft,
    상기 출력축에 평행하게 배치된 제1아이들축, A first idle shaft disposed parallel to the output shaft,
    상기 제1아이들축에 회전가능하게 외접되어 상기 제1정방향피동기에 치합하는 제1아이들기어, A first idle gear rotatably circumscribed on the first idle shaft and meshing with the first forward driven member,
    상기 제1아이들축에 회전가능하게 외접되어 제1중간기어를 경유하여 상기 제2정방향피동기어에 치합하는 제2아이들기어, A second idle gear rotatably circumscribed on the first idle shaft and meshing with the second forward driven gear via a first intermediate gear,
    상기 제1아이들축에 고정적으로 외접되어 상기 출력나사축구동기어에 치합하는 출력나사축기동기어, An output screw shaft starting gear fixedly circumscribed to the first idle shaft and meshing with the output screw driving synchronous gear,
    선택적으로 상기 제1아이들축에 제1아이들기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제1스톱퍼, 및 A first stopper that selectively engages the first idle gear on the first idle shaft to rotate or idle them together, and
    선택적으로 상기 제1아이들축에 제2아이들기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제2스톱퍼를 포함하거나, 또는And a second stopper selectively engaging the second idle gear with the first idle shaft so that they rotate or idle together, or
    상기 출력축에 고정적으로 외접된 제1정방향피동기어, A first forward driven gear fixedly circumscribed to the output shaft,
    상기 출력나사축에 고정적으로 외접된 출력나사축구동기어, An output screw coaxial gear fixedly circumscribed to the output screw shaft,
    상기 출력축에 평행하게 배치된 제1아이들축, A first idle shaft disposed parallel to the output shaft,
    상기 제1아이들축에 베어링을 개재하여 회전가능하게 외접되어 상기 제1정방향피동기에 치합하는 제1아이들기어, A first idle gear rotatably circumscribed by the first idle shaft via a bearing and meshing with the first forward driven member,
    상기 제1아이들축에 베어링을 개재하여 회전가능하게 외접되어 상기 출력나사축구동기어에 치합하는 출력나사축기동기어,An output screw shaft starting gear that is rotatably circumscribed by the first idle shaft via a bearing and meshes with the output threaded spur gear,
    선택적으로 상기 제1아이들축에 제1아이들기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제1스톱퍼, 및A first stopper that selectively engages the first idle gear on the first idle shaft to rotate or idle them together, and
    선택적으로 상기 제1아이들축에 상기 출력나사축기동기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제7스톱퍼를 포함하고 있는 것을 특징으로 하는 자동 변속기.And a seventh stopper selectively engaging the output screw shaft starting gear on the first idle shaft so that they rotate or idle together.
  11. 제 9항에 있어서,10. The method of claim 9,
    상기 상대속도차전달부는 The relative speed difference transfer unit
    상기 출력축에 고정적으로 외접된 제3 및 제4정방향피동기어, Third and fourth forward driven gears fixedly circumscribed to the output shaft,
    상기 제1유성기어에 고정적으로 내접된 유성기어축에 고정적으로 외접된 제2유성기어에 치합된 제2태양기어, A second sun gear meshed with a second planetary gear fixedly circumscribed to a planetary gear shaft fixedly inscribed on the first planetary gear,
    상기 출력축에 평행하게 배치되어 상기 제2태양기어에 고정적으로 내접된 제2아이들축, A second idle shaft disposed parallel to the output shaft and fixedly inscribed in the second sun gear,
    상기 제2아이들축에 회전가능하게 외접되어 상기 제3정방향피동기어에 치합하는 제3아이들기어, A third idle gear rotatably circumscribed on the second idle shaft and meshing with the third forward driven gear,
    상기 제2아이들축에 회전가능하게 외접되어 제2중간기어를 경유하여 상기 제4정방향피동기어에 치합하는 제4아이들기어,A fourth idle gear rotatably circumscribed on the second idle shaft and meshing with the fourth forward driven gear via a second intermediate gear,
    선택적으로 상기 제2아이들축에 제3아이들기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제3스톱퍼, 및A third stopper selectively engaging a third idle gear on the second idle shaft to rotate or idle them together, and
    선택적으로 상기 제2아이들축에 제2아이들기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제4스톱퍼를 포함하거나, 또는And a fourth stopper which selectively engages the second idle gear on the second idle shaft so that they rotate or idle together, or
    상기 연동부는 The interlocking portion
    상기 출력축에 고정적으로 외접된 제3정방향피동기어, A third forward driven gear fixedly circumscribed to the output shaft,
    상기 제1유성기어에 고정적으로 내접된 유성기어축에 고정적으로 외접된 제2유성기어에 치합된 제2태양기어, A second sun gear meshed with a second planetary gear fixedly circumscribed to a planetary gear shaft fixedly inscribed on the first planetary gear,
    상기 출력축에 평행하게 배치되어 상기 제2태양기어에 고정적으로 내접된 제2아이들축, A second idle shaft disposed parallel to the output shaft and fixedly inscribed in the second sun gear,
    상기 제2아이들축에 베어링을 개재하여 회전가능하게 외접되어 상기 제3정방향피동기어에 치합하는 제3아이들기어, A third idle gear rotatably circumscribed by the second idle shaft via a bearing and meshing with the third forward driven gear,
    상기 제2아이들축에 회전가능하게 외접되어 제2중간기어을 경유하여 상기 제4정방향피동기어에 치합하는 제4아이들기어,A fourth idle gear rotatably circumscribed on the second idle shaft and meshing with the fourth forward driven gear via a second intermediate gear,
    선택적으로 상기 제2아이들축에 제3아이들기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제3스톱퍼, 및A third stopper selectively engaging a third idle gear on the second idle shaft to rotate or idle them together, and
    선택적으로 상기 제2아이들축에 제2아이들기어를 물림하여 이들이 함께 회전하게 하거나 헛돌게 하는 제4스톱퍼를 포함하고 있는 것을 특징으로 하는 자동 변속기.And a fourth stopper selectively engaging a second idle gear on the second idle shaft so that they rotate or idle together.
  12. 제 9항에 있어서,10. The method of claim 9,
    상기 제1태양기어는 상기 동조부에 의해 입력축이 역방향으로 1회전할 때 역방향으로 1회전할 수 있도록 되어 있는 것을 특징으로 하는 자동 변속기.Wherein the first sun gear is configured to make one rotation in the reverse direction when the input shaft rotates once in the reverse direction by the tuning unit.
  13. 제 10항에 있어서,11. The method of claim 10,
    상기 출력나사축은 상기 제상대속도차발생부에 의해 상기 출력축보다 빠르게 또는 느리게 회전할 수 있도록 되어 있는 것을 특징으로 하는 자동 변속기.Wherein the output screw shaft is capable of rotating faster or slower than the output shaft by the relative speed difference generator.
  14. 제 11항에 있어서,12. The method of claim 11,
    상기 입력축은 상기 상대속도차전달부 또는 상기 연동부에 의해 상기 출력나사축과 상기 출력축 간의 회전속도차 만큼의 속도로 회전할 수 있도록 되어 있는 것을 특징으로 하는 자동 변속기.Wherein the input shaft is rotatable by the relative speed difference transmitting portion or the linked portion at a speed corresponding to a rotational speed difference between the output screw shaft and the output shaft.
  15. 제 6항 또는 제 7항에 있어서,8. The method according to claim 6 or 7,
    상기 출력나사축과 상기 출력축 사이에는 Between the output screw shaft and the output shaft
    선택적으로 상기 출력나사축에 상기 출력축을 물림하여 이들이 함께 회전하게 하여 이들 사이에 상대속도가 발생되지 않게 하거나 물림하지 않아 헛돌게 하는 제5스톱퍼와 그리고 A fifth stopper selectively engaging the output shaft on the output screw shaft so that the output shaft rotates together with the output shaft so that the relative speed does not occur between the output shaft and the output shaft,
    상기 입력나사축과 상기 입력축 사이에는Between the input screw shaft and the input shaft
    선택적으로 상기 입력나사축에 상기 입력축을 물림하여 이들이 함께 회전하게 하여 이들 사이에 상대속도가 발생되지 않게 하거나 물림하지 않아 헛돌게 하는 제6스톱퍼가 개재되어 있는 것을 특징으로 하는 자동 변속기.And a sixth stopper interposed between the input shaft and the input shaft to selectively rotate the input shaft so that the input shaft rotates together with the input shaft so that a relative speed is not generated between the input shaft and the input shaft.
  16. 제 15항에 있어서,16. The method of claim 15,
    상기 제5 및 제6스톱퍼는 하나의 실린더에 구비된 두개의 로드 각각에 구비되어 있는 것을 특징으로 하는 자동 변속기.And the fifth and sixth stoppers are provided on each of two rods provided in one cylinder.
PCT/KR2014/003285 2013-04-17 2014-04-16 Automatic transmission WO2014171722A1 (en)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR1020130042099A KR101267823B1 (en) 2013-04-17 2013-04-17 Automatic transmission
KR10-2013-0042099 2013-04-17
KR1020130065616A KR101533794B1 (en) 2013-06-10 2013-06-10 structure of claw clutch
KR10-2013-0065616 2013-06-10
KR20130110910A KR20150031563A (en) 2013-09-16 2013-09-16 endless transmission
KR10-2013-0110910 2013-09-16

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WO2014171722A1 true WO2014171722A1 (en) 2014-10-23

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FR3032757A1 (en) * 2015-02-13 2016-08-19 Renault Sa DEVICE FOR CONTROLLING A MECHANICAL CONCENTRIC RECEIVER CLUTCH
GB2538532A (en) * 2015-05-19 2016-11-23 R Abbott William Gear change system incorporating simultaneous selection of multiple gears
CN107477104A (en) * 2017-09-29 2017-12-15 东莞市松研智达工业设计有限公司 A kind of torque clutch that speed change is can adjust based on gear
CN109442016A (en) * 2018-12-31 2019-03-08 牛清锋 Diameter pushing-type transmission gear shift regulating mechanism
CN109469722A (en) * 2018-12-31 2019-03-15 牛清锋 Gearbox diameter pushing-type gear engagement structure
CN109854689A (en) * 2019-01-31 2019-06-07 牛清锋 Inner bearing type gearshift gearbox
CN111878523A (en) * 2020-08-31 2020-11-03 黄建 Electric control automatic gearbox
CN112112938A (en) * 2020-04-29 2020-12-22 黄建 Automatic gearbox capable of adding gears
CN112780729A (en) * 2021-01-20 2021-05-11 鲍杰 Novel municipal administration is blow off water pump for pump house
WO2021160946A1 (en) 2020-02-13 2021-08-19 Franck Guigan Transmission with a shaft and dog connected by a thread
FR3108958A1 (en) * 2020-04-07 2021-10-08 Franck Guigan Gearbox

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KR20020036979A (en) * 2002-03-05 2002-05-17 이창복 how to put the car into gear with an automatic transmission
US20020091033A1 (en) * 2001-01-09 2002-07-11 Tianfu Li Transmission mechanism
KR20030031797A (en) * 2001-10-16 2003-04-23 하태환 all wheel drive device of an automobile

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US20020091033A1 (en) * 2001-01-09 2002-07-11 Tianfu Li Transmission mechanism
KR20030031797A (en) * 2001-10-16 2003-04-23 하태환 all wheel drive device of an automobile
KR20020036979A (en) * 2002-03-05 2002-05-17 이창복 how to put the car into gear with an automatic transmission

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3032757A1 (en) * 2015-02-13 2016-08-19 Renault Sa DEVICE FOR CONTROLLING A MECHANICAL CONCENTRIC RECEIVER CLUTCH
GB2538532A (en) * 2015-05-19 2016-11-23 R Abbott William Gear change system incorporating simultaneous selection of multiple gears
CN107477104A (en) * 2017-09-29 2017-12-15 东莞市松研智达工业设计有限公司 A kind of torque clutch that speed change is can adjust based on gear
CN109442016A (en) * 2018-12-31 2019-03-08 牛清锋 Diameter pushing-type transmission gear shift regulating mechanism
CN109469722A (en) * 2018-12-31 2019-03-15 牛清锋 Gearbox diameter pushing-type gear engagement structure
CN109854689A (en) * 2019-01-31 2019-06-07 牛清锋 Inner bearing type gearshift gearbox
CN109854689B (en) * 2019-01-31 2024-05-10 浙江海天机械有限公司 Internal support type gear shifting mechanism gearbox
WO2021160946A1 (en) 2020-02-13 2021-08-19 Franck Guigan Transmission with a shaft and dog connected by a thread
FR3108958A1 (en) * 2020-04-07 2021-10-08 Franck Guigan Gearbox
CN112112938A (en) * 2020-04-29 2020-12-22 黄建 Automatic gearbox capable of adding gears
CN111878523A (en) * 2020-08-31 2020-11-03 黄建 Electric control automatic gearbox
CN112780729A (en) * 2021-01-20 2021-05-11 鲍杰 Novel municipal administration is blow off water pump for pump house

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