KR20150029223A - endless Transmission - Google Patents
endless Transmission Download PDFInfo
- Publication number
- KR20150029223A KR20150029223A KR20130108100A KR20130108100A KR20150029223A KR 20150029223 A KR20150029223 A KR 20150029223A KR 20130108100 A KR20130108100 A KR 20130108100A KR 20130108100 A KR20130108100 A KR 20130108100A KR 20150029223 A KR20150029223 A KR 20150029223A
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- KR
- South Korea
- Prior art keywords
- input
- output
- shaft
- gear
- gears
- Prior art date
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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
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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
- F16H31/00—Other gearings with freewheeling members or other intermittently driving members
- F16H31/003—Step-by-step mechanisms for rotary motion
- F16H31/005—Step-by-step mechanisms for rotary motion with pawls driven by a reciprocating or oscillating transmission member
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Transmission (AREA)
Abstract
In the present invention, both the driving gear and the driven gear are parallel to each other, and the driving shaft and the driven shaft are internally engaged with each other through a bearing, Way clutch is interposed between the drive shaft and the drive gear group or between the driven shaft and the driven gear group, and the drive chain base and the driven chain base of the driven / paired clutches using the ball screw in the drive shaft and the driven shaft, So that two driving gears of the plurality of driving gears and two driven gears meshed with the two driving gears are engaged with each other so that the driving force of the driving shaft is transmitted to the driven shaft, Even if a driving force is transmitted to the driven shaft through the driven gear by one of the plurality of driving gears, Only the driven gear engaged with the one drive gear among the plurality of driven gears transmits the driving force to the driven shaft and the other driven gears are idle or held at the position, So that it is possible to transmit the load to the driven shaft with a smaller driving force than in the prior art, thereby reducing manufacturing cost and maintenance cost.
Description
BACKGROUND OF THE
The automatic transmission is a device in which the gear is automatically operated according to the speed at which the gear ratio is automatically selected and operated, regardless of the driver's operation. This automatic transmission automates the rudder operation and gear shifting required for the car to run.
In addition, depending on the speed set for each car and stepping on the accelerator, the appropriate gear is selected.
This automatic transmission is designed so that the gear ratio can be automatically selected by activating the fluid clutch, band or disc plate.
Typically, automatic transmissions include Ravigneaux or Simpson planetary gear units that include sun gear, planetary gears, ring gears, and planet gear carriers.
This planetary gear unit is required to have a complicated structure in which a sun gear, a planetary gear, a ring gear, and a planetary gear carrier are selectively engaged with an input shaft and an output shaft, respectively. The power of the input shaft is not instantaneously transmitted to the output shaft, and the driven object may fall freely when the driven object is receiving gravity.
Further, the conventional automatic transmission has a problem that it can provide a plurality of transmission stages, but can not provide infinitely many transmission stages.
An infinite transmission for solving such a problem is disclosed in Korean Patent No. 10-102968.
The above-described infinite transmission has a plurality of driven gears, each of which has a smaller diameter as it goes to one side, circumscribes the input shaft via a one-way clutch, and a plurality of driven gears, which are meshed with these driving gears, And a plurality of contact pressing members which are in contact with the inner circumferential surface of the plurality of driven gears by centrifugal force are mounted on the output shaft so as to be movable in the radial direction of the plurality of contact pressing members, And a loader of a support unit which is reciprocated by a translating portion in the output shaft so as to selectively support the contact pressing member so that power can be transmitted from the input shaft to the output shaft while being transmitted without loss of power transmission.
However, in the above-described automatic transmission, only when the plurality of contact pressure members are radially outwardly opened by the centrifugal force, the loader of the support unit enters between the two contact pressure members of the plurality of contact pressure members, So that the two contact pressing members contact and press the two driven gears among the plurality of driven gears to transmit the power transmitted from the driving gear to the two driven gears to be transmitted to the output shaft However, in a state in which the centrifugal force is not generated in the plurality of contact pressure members because the output shaft is not rotated, for example, in a state where the loader of the support unit is in the neutral position or the input shaft is stopped, A plurality of contact pressure members disposed above the contact pressure members are arranged in a radial direction So that the driven gears can not rotate and the power of the input shaft can not be transmitted to the output shaft even if the input shaft is restarted. Furthermore, since the left-right movement of the loader of the support unit is caused by gravity, The input shaft is driven to drive the driven shaft in order to constantly apply the centrifugal force to the plurality of contact pressure members because the shifting member can not enter between the contact pressing members which are obstructed by the pressure members, There is a problem in that it is impossible to realize a neutral state and there is a problem that a plurality of recesses are formed on the inner circumferential surface of the driven gear to cause a collision between the contact pressing member and the recessed portion due to the centrifugal force and noise is generated.
An automatic transmission for solving the above problem is disclosed in Patent Registration No. 10-0042099, which is patented and patent registered by the present inventor.
The above-described automatic transmission includes a ball screw fixedly inscribed on a tubular shaft; A chisel base portion which is fastened to the ball screw and slidably inserted in the tubular shaft; And a plurality of recesses are formed on the inner circumferential surface of the inner race of the one-way clutch at predetermined intervals along the circumferential direction of the one raceway clutch And a plurality of spur gears having a larger diameter toward an axial side; When the radially inner portion is seated in a plurality of through holes formed at predetermined intervals in the axial direction at the portions of the tubular shafts facing the plurality of spur gears and selectively pressed by the chain base portion in the radial outward direction to be pressed, And a plurality of spur gears fixedly circumscribed to the output shaft and meshing with the plurality of spur gears and having a smaller diameter toward the one axial side in the axial direction, And an automatic transmission having a length capable of contacting at least two protruding and retracting members including an driven gear portion and an axial length of the chain base portion in the axial direction.
In the above-described automatic transmission, when the chain base portion simultaneously engages two drive gears having different diameters, the two gears rotate equally by the tubular shaft, and the two driven gears, which are engaged with the two drive gears, The rotational force of the two driving gears having different circumferential speeds is applied to the gear, and the driven shaft fixedly inscribed on the two driven gears fixedly circumscribed to the driven shaft is subjected to the rotational forces of the peripheral speed, However, since the driving gears are rotatably circumscribed by the one-way clutch on the tubular shaft, only the driving gear of the larger diameter among the two driving gears is larger than the larger one of the two driven gears And transmits a rotational force to a small driven gear engaged with the drive gear, and a large driven gear of two driven gears fixedly circumscribed to the driven shaft The small drive gear is rotated in the same direction as the rotational direction of the tubular shaft by the peripheral speed of the tubular shaft, so that any p / drive gear, tubular shaft, and driven shaft are not damaged.
However, in the above-described automatic transmission, the driving force is transmitted to the driven shaft selectively by one of the plurality of driving gears by the engaging clutch in a state in which a plurality of driving gears are actually circumscribed via the bearings and the one- However, since a plurality of driven gears are fixedly circumscribed on the driven shaft, not only the driven gear engaged with the one drive gear among the plurality of driven gears rotates but also all of the driven gears rotate together with the driven shaft, There is a problem that a large power is required to transmit the driving force to the coaxial shaft.
The present invention has a problem in solving the above-mentioned problems.
In the present invention, both the driving gear and the driven gear are parallel to each other, and the driving shaft and the driven shaft are internally engaged with each other through a bearing, Way clutch is interposed between the drive shaft and the drive gear group or between the driven shaft and the driven gear group, and the drive chain base and the driven chain base of the driven / paired clutches using the ball screw in the drive shaft and the driven shaft, So that two driving gears of the plurality of driving gears and two driven gears meshed with the two driving gears are engaged with each other so that the driving force of the driving shaft is transmitted to the driven shaft, The above problems can be solved.
According to the present invention, even when a driving force is transmitted to a driven shaft through a driven gear by a driving gear of a plurality of driving gears, Only the driven gear engaged with the driving gear of the other driven gear is transmitted to the driven shaft and the other driven gears are idle or held in position to give a load in the rotating direction by the weight of the other driven gear to the driven shaft It is possible to transmit the driving force to the driven shaft with a smaller driving force than in the prior art, thereby reducing manufacturing cost and maintenance cost.
1 is a view showing an automatic transmission according to a first embodiment of the present invention,
2 is a view showing an automatic transmission according to a second embodiment of the present invention.
Hereinafter, an infinitely variable transmission according to an embodiment of the present invention will be described in detail with reference to FIG.
In Fig. 1, an infinite transmission is indicated by
The
The
The
The
The output clutch 120 includes an
The detailed configurations of the
The axial length of the
In addition, the axial length of the
The
The
The
Although the one-way clutch C is described as being interposed between the plurality of
Further, in the above embodiment, it is spatially limited that the
1 and 2, the
The
1, the position of the
In the former case, the
However, in the latter case, even if the
The mode switching means for synchronously moving the
Further, the
The first forward driven
The first and second stoppers (130, 140) are configured such that gears rotatably circumscribed by the tubular portion are rotatably connected to the tip of the rod of the cylinder fixed to the base via a bearing, It is preferable from the viewpoint of manufacturing and maintenance that the fluid is not supplied to the rotating body.
The infinite transmission having the mode switching means configured as described above can be operated as follows. In the following description, the forward direction is the clockwise direction and the reverse direction is the counterclockwise direction.
1. When the first to
In this case, the
2. When the
In this case, assuming that the
That is, when the acceleration ratio is 10 and the reduction ratio is 0.1, the
3. When the
In this case, assuming that the
That is, when the speed ratio is 10 and the speed ratio is 0.1, when the
In the case where the speed ratio is such that the first forward driven
This is because the
The infinitely-variable transmission as described above can arrange gears having different gear ratios in an axial direction in an infinite manner, so that it is possible to provide an operational effect of providing numerous speed-changing ratios.
Further, in the explanation of the infinitely variable transmission of the embodiment, although the
In the description of the infinitely variable transmission according to the above embodiment, the first forward driven
10; An input shaft, 110; An input clutch, 120; An output clutch, 200; Infinite transmission, 201; Output shaft
Claims (8)
A plurality of output gears rotatably circumscribed by a tubular output shaft and engaged with the plurality of input gears and arranged to have a larger diameter toward the other side in the axial direction;
A plurality of one-way clutches interposed between any one of input gears and output gears meshing with each other and an input shaft or an output shaft inscribed in either one of the gears;
An input clutch for engaging two adjacent gears among a plurality of input gears rotatably circumscribed on an input shaft or for engaging the one-way clutch inscribed on the input gear; And
An output clutch that engages two adjacent gears among a plurality of output gears that are rotatably circumscribed on an output shaft, or engages the one-way clutch that is inscribed in the output gear,
Each of the input clutch and the output clutch
An input chaining section or an output chaining section which is movable in an axial direction by an input translating section or an output translating section in an input shaft or an output shaft;
A plurality of input recesses or output recesses spaced along the circumferential direction on the inner circumferential surface of each of the plurality of input gears or output gears or the inner circumferential surface of the inner race of the plurality of one-way clutches; And
A radial inner portion is inserted and seated in each of a plurality of through holes spaced apart axially from a portion of the input shaft or the output shaft facing the plurality of input concave portions or output concave portions, And an input / output projecting / retracting member or an output projecting / retreating member, which is partially inserted into the input recessed portion or the output recessed portion when pressed by being pushed outwardly,
Wherein each of the plurality of one-way clutches is a one-way clutch in a state of being engaged when a rotational driving force is transmitted to the driven object in one direction,
Wherein the input synchronizing portion of the input clutch and the output synchronizing portion of the output clutch move synchronously with each other in the same direction in the axial direction on the input shaft and the output shaft.
Wherein the input translating unit and the output translating unit are ball screws,
Wherein the input wedge portion and the output wedge portion are wedge nuts,
The input translating unit and the output translating unit include first and second forward and reverse motors for selectively rotating the screw shaft of the ball screw in the forward and reverse directions to move the wrench nut in the axial direction, Wherein the transmission mechanism comprises:
The input translating unit and the output translating unit
The body of the cylinder fixed to the base,
The input wedge portion and the output wedge portion inscribed in the axial direction so as not to rotate in the circumferential direction on the input shaft and the output shaft,
And an input rod and an output rod rotatably inscribed in the input choke section and the output choke section via a bearing,
Wherein the input rod and the output rod are fixed to a main rod of the cylinder.
Further comprising mode switching means for synchronously shifting the input wobbling portion and the output wobbler portion at the same speed in the axial direction by the power source of the infinite variable speed gear.
The axial length of the input wobbling portion has a length capable of maintaining the pressurization with respect to the two adjacent input / output members in the input shaft at the time of shifting from the low speed to the high speed end and from the high speed end to the low speed However,
The axial length of the output wobbling portion has a length capable of maintaining the pressure on two neighboring output mobiles in the output shaft at the time of shifting from the low speed to the high speed and at the speed changing from the high speed to the low speed Wherein the transmission mechanism comprises:
Wherein the position of the input wobbling portion and the output wobbler portion are positioned at the same position in the axial direction of the input shaft or the position of the output wobbler portion The input wrench nut 113 is positioned at a position capable of simultaneously engaging another input gear of a smaller diameter than the one input gear with the one input gear, The output wedge nut 123 is positioned at a position where the other output gear 60 having a smaller diameter than the immediately adjacent output gear 60 can be engaged with the one output gear 60 at the same time An input gear 40 and an output gear 60 which are simultaneously engaged by the input wrench nut 113 and the output wrench nut 123 are engaged with the input wrench nut 113, And the output worm nut 123 is arranged so as to have a diameter larger than the diameter of the other one of the input gears 40 or the other output gear 60 which is engaged with one of the worm nuts of the output worm nut 123. [ Infinite transmission.
Wherein the mode switching means comprises:
A forward drive gear rotatably circumscribed by the drive shaft,
A first forward driven gear fixedly circumscribed to the output screw shaft,
A reverse intermediate gear interposed between the forward drive gear and the first forward driven gear and meshed with the forward drive gear and rotatably mounted on the base,
A first stopper for selectively driving the forward drive gear to rotate the drive shaft and the forward drive gear together,
A third stopper for selectively interlocking the reverse intermediate gear to prevent the reverse intermediate gear from rotating,
A second forward driven gear fixedly circumscribed to the output shaft,
A first reverse driven gear engaged with the second forward driven gear,
And a second stopper (140) for selectively rotating the input screw shaft and the first reverse driven gear together or only the first reverse driven gear with a driving force of the second forward driven gear,
Wherein the input screw shaft is one of a left-hand thread and a right-hand thread, and the output screw shaft is another one,
Wherein the first forward driven gear is set at a predetermined speed increase ratio with respect to the input shaft by a predetermined speed so as to rotate at a speed faster than or equal to the speed at which the output shaft rotates as fast as possible, Is set to be able to rotate with an inverse speed reduction ratio of the predetermined speed increasing ratio.
Wherein the mode switching means comprises:
A forward drive gear rotatably circumscribed by the drive shaft,
A first forward driven gear fixedly circumscribed to the output screw shaft,
A reverse intermediate gear interposed between the forward drive gear and the first forward driven gear and meshed with the forward drive gear and rotatably mounted on the base,
A first stopper for selectively driving the forward drive gear to rotate the drive shaft and the forward drive gear together,
A third stopper for selectively interlocking the reverse intermediate gear to prevent the reverse intermediate gear from rotating,
A second forward driven gear fixedly circumscribed to the output shaft,
A first reverse driven gear engaged with the second forward driven gear,
And a second stopper (140) for selectively rotating the input screw shaft and the first reverse driven gear together or only the first reverse driven gear with a driving force of the second forward driven gear,
Wherein the input screw shaft is one of a left-handed screw and a right-handed screw, and the output screw shaft is another one,
The first reverse driven gear is set so as to rotate with the predetermined speed increasing ratio by a predetermined speed with respect to the second forward driven gear so that the first reverse driven gear can rotate faster than the speed at which the output shaft rotates as fast as possible And the first forward driven gear is set so as to be able to rotate with respect to the input shaft with an inverse speed reduction ratio of the predetermined speed increasing ratio.
Priority Applications (1)
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KR20130108100A KR20150029223A (en) | 2013-09-09 | 2013-09-09 | endless Transmission |
Applications Claiming Priority (1)
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KR20130108100A KR20150029223A (en) | 2013-09-09 | 2013-09-09 | endless Transmission |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107859716A (en) * | 2017-10-16 | 2018-03-30 | 陈周林 | A kind of multipurpose low speed gearbox |
CN108679172A (en) * | 2018-07-18 | 2018-10-19 | 樊朝晖 | A kind of coaxial straight line gear |
WO2018212595A1 (en) * | 2017-05-19 | 2018-11-22 | 김복성 | Multi-speed transmission for motor |
CN109720197A (en) * | 2019-02-18 | 2019-05-07 | 福建万润新能源科技有限公司 | A kind of driving device and vehicle |
-
2013
- 2013-09-09 KR KR20130108100A patent/KR20150029223A/en active IP Right Grant
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018212595A1 (en) * | 2017-05-19 | 2018-11-22 | 김복성 | Multi-speed transmission for motor |
US11287015B2 (en) | 2017-05-19 | 2022-03-29 | Bok Soung KIM | Multi-speed transmission for motor |
CN107859716A (en) * | 2017-10-16 | 2018-03-30 | 陈周林 | A kind of multipurpose low speed gearbox |
CN108679172A (en) * | 2018-07-18 | 2018-10-19 | 樊朝晖 | A kind of coaxial straight line gear |
CN109720197A (en) * | 2019-02-18 | 2019-05-07 | 福建万润新能源科技有限公司 | A kind of driving device and vehicle |
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