CA1230760A - Speed variator - Google Patents
Speed variatorInfo
- Publication number
- CA1230760A CA1230760A CA000427023A CA427023A CA1230760A CA 1230760 A CA1230760 A CA 1230760A CA 000427023 A CA000427023 A CA 000427023A CA 427023 A CA427023 A CA 427023A CA 1230760 A CA1230760 A CA 1230760A
- Authority
- CA
- Canada
- Prior art keywords
- rotation
- transmission
- disk
- plate
- input
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired
Links
Classifications
-
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
-
- 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
- F16H21/00—Gearings comprising primarily only links or levers, with or without slides
- F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
- F16H21/12—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying rotary motion
- F16H21/14—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying rotary motion by means of cranks, eccentrics, or like members fixed to one rotary member and guided along tracks on the other
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Golf Clubs (AREA)
- Structure Of Transmissions (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
Device for generating different speeds of rotation between an input shaft and an output shaft is described. Two facing transmission plates are connected to the ends of respective shafts and are coupled to each other by means of an intermediate disk which is supported for rotation between the opposite faces of the transmission plates and is shiftable in transverse direc-tion relative to the axis of the shafts. The intermediate disk is coupled to respective transmission plates by corresponding carrier pins engaging radial guiding grooves in the plates. The guiding grooves can be rectilinear or may have a curved shape passing through the center of rotation of the assignment plate.
Device for generating different speeds of rotation between an input shaft and an output shaft is described. Two facing transmission plates are connected to the ends of respective shafts and are coupled to each other by means of an intermediate disk which is supported for rotation between the opposite faces of the transmission plates and is shiftable in transverse direc-tion relative to the axis of the shafts. The intermediate disk is coupled to respective transmission plates by corresponding carrier pins engaging radial guiding grooves in the plates. The guiding grooves can be rectilinear or may have a curved shape passing through the center of rotation of the assignment plate.
Description
~~ ~ t.~.
(' D~:VICE FOR GL.~ TIl~G D~Fl:`LP~EN'r SP~:EDS O~
ROT~TION BET~'E:N INPVT ~D O~TPUT SHN:TS
il `
~3076~) BACKGROVND OF THE INVENTION
The invention relates in general to a power transmis-sion device and in particular to a device for generating differ-ent speeds of rotation between an input shaft rotating prefer-ably with a uniform speed, about an axis, and a driven output shaft rotating about another axis.
~ Power transmission devices of this kind operate usually with gear trains. The disadvantage of geaxs is not only the fact that they are expensive in manufacture but also th~
difficulty in changing the rate of rotation between the input shaft and the output shaft, particularly if it is desirable to change the rotary speed between the two shafts during one cycle.
.5 Such a phase shift in the two courses of rotation in transmission gears can be accomplished only by exchanging corresponding gears.
SUMMARY OF THE INVENTION
~ ,.
It is therefore a general object of the present inven-tion to overcome the aforementioned disadvantages.
More particularly, it is an object of the invention to provide an improved differential device for producing differ-ent rotational speeds between a driving shaft rotating preferably at a uniform ~peed and a driven output ~haft, ~hich eliminates gears and is compDsed of simple rotation-symmetrical ~odies.
C l _ ~ ~
x~
123~760 27412-1 An addi.tional object of the invention is to provide such an improved transmission device in which t,he input shaft having a uniform rotary speed imparts to the driven output shaft a non-uniform rotary speed, or vice versa, and in which the speed difference is selectively adjustable.
A further object of the invention is to provide such an improved differential device at which the range of the generated speed difference is such that the driven shaft can become stationary in spite of the rotation of the driving shaft.
In keeping with these objects and others which will become apparent hereafter, one feature of the invention resides, in a transmission device of the above described type for generat-ing a rotary speed difference between an input shaft _otating about an axis and an output shaft rotating about another axis, said input and output shafts being aligned, comprisi.ng a first transmission plate of circular configuration connected for joint rotation with one of said shafts;
a second transmission plate of circular configuration connected for joint rotation with the other shaft;
a housing enclosing said transmission plates and supporting for rotation said input and output shafts;
an intermediate transmi.ssion disk supported for rotation in said housing between said first and a second transmission pla,tes and being rectilinearly displaceable in transverse direc-tion to the axes of said shafts, and the facing surfaces of said first and second transmission plates being provided respectively with a radial guiding groove;
1~30~7~0 each end face of said intermediate disk being provided with only one projecting carrier pin, each carrier pin being spaced apart from the center of rotation of the intermediate plate about the same distance and engaging the assigned radial guiding groove in the opposite transmission plate;
said radial guiding grooves in said transmission plates being through going and passing through the center of rotation of the corresponding plate symmetrically to the center and said intermediate disk being rectilinearly displaceable between a full-transmission position in which its center of rotation coincides with the axes of said input and output shafts, and two no-transmission positions in which one of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft or alternatingly the other of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft;
said intermedia~e transmission disk being supported for rotation in at least one circumferential bearing, said circum-ferential bearing being mounted in a rectangular frame which is displaceable in said housing in radial direction relative to the axis of rotation of said intermediate transmission disk and said frame being provided with a control rod passing through said housing r The construction of this invention employs simple geometrical bodies, such as for example rectangular or rotation-symmetrical disks.
_4_ ~'~3~760 27412-1 The carrier pin in said intermediate disk, which engages the guiding groove in each transmission plate, may have a configura-tion in the form of a cylindrical pin. As long as the intermediate disk is aligned along his axe of rotation with the axes of the transmission plates, no speed difference will result between the input shaft and the output shaft. As soon, however, as the axe of rotation of the intermediate disk is radially displaced rela-tive to the rotation axes of the transmission plates, then a different speed of rotation is generated between the input shaft and the output shaft; Depending on the magnitude of the displace ment, the course of the differential speed is completed during one cycle of the driving shaft; in a certain radial position of the intermediate disk, namely when the power transmitting carrier pin in one of said end faces of the intermediate disk is coaxial with the rotation axes of the two transmission plates, engaging the center of rotation of the corresponding guiding groove, the driven shaft becomes stationary in spite of the rotation of the driving shaft, and vice versa.
In a particularly advantageous embodiment, the shaft sections supporting the plates are journalled in a common housing in which is aranged the intermediate disk coupled by the groove and pin connections to the opposite first and second plates, and which is displaceable in radial direction relative to the axes of the input and output shafts.
In another advantageous modification of this invention, the plate assigned to the input shaft as well as the plate assigned to the output shaft are provided each with a guiding groove extending in radial direction, whereby the radially dis-~23~ 27412-1 placeable intermediate disk is provided at both end faces thereof with projecting carrier pins engaging the two guiding grooves.
According to another measure of this invention, the facing surfaces of the first and second plates connected to the input and output shafts are provided each with a single guiding groove crossing the center of rotation of the plate, and the intermediate disk is radially displaceable about a distance and one of its eccentric carrier pins is shiftable in a position in which it is coaxial either with the input shaft or on the opposite side, with the axis of rotation of the output shaft. This solution makes it possible that during one cycle of one plate, the differential speed at the other plate can ke such that even at a rotating input shaft the output shaft stands still.
The guiding groove in the first or in the second plate, assigned to the input shaft or to the output shaft, can be rectilinear. Preferably, the guiding groove extends over the entire diameter of the disk, or in the case of rectangular plates over the entire longer surface of the plate. The speed differential generating effect between the input and output shafts can be improved by providing a curved guiding groove.
A further improvement can be achieved when, in the embodiment in which the guiding grooves are provided in the opposite faces of the first and second plates, when the curve of the guiding groove in one plate differs from the curve of the opposite guiding groove.
In a further modification of the device of this invention, the C
~30760 27412-1 intermediate plate is in the form of a disk surrounded by a bearing which in turn is supported in a rectangular frame which is shiftable transversely to the axis of rotation of the inter-mediate disk. Preferably, the rectangular frame is connected to a plunger projecting in radial direction through the housing.
It is also of advantage when the bearing surrounding the intermediate disk is arranged in a further bearing which is rotatable in opposite direction relative to the inner bearing.
The novel features which are considered characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construc-tion and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in con-nection with the accompanying drawing.
BRIEF DESCRIPTION OF THE DRAWING
_ _ .
Figure 1 is a sectional top view of a schematic repre-sentation of the transmission device of this invention;
Figures 2 - 8 show respectively various angular posi-tions of radially displaced transmission plates in the device of Figure l;
Figure 9 is a plot diagram of the speed variation of one shaft versus the angular position of uniformly rotating other shaft;
Figure 10 is a further modification of the device of Figure l;
C
27412-l ~Z30760 Figure 11 shows the radial displacement of the inter-mediate disk in the device of Figure 10;
Figures 12 and 13 show respectively different shapes of guiding grooves in the transmission platesi Figure 14 is a side view of a shiftable support for the intermediate transmission disk;
Figure 15 is a plot diagram of different speeds of rotation between the input and output shafts;
Figure 16 is a vertical section of still another modification of the device of this invention; and Figure 17 shows schematically by way of an example the application of the device of this invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring firstly to Figure 1, the transmission device has an input shaft 10 fixedly connected at its end to a transverse transmission plate 11. Preferably, the shaft and the plate are made as a one-piece component. Plate 11 faces another transmission plate 13 which is fixedly connected to an output shaft 12. In this embodiment, the transmission plates 11 and 13 have circular configuration. The input and output shafts are supported in bearings 14 and 15, respectively. The end face of transmission plate 11 is formed with a radially directed guiding groove 16 of a rectangular cross section. The groove 16 is either machined in the plate 11, or it can be also in the form of a guiding channel which is additionally attached to the face of the disk. The end face of transmission plate 13 is also formed with a radially directed guiding groove 16a of a rectang-C
~.~3(1760 ular cross section~ Said groove 16a may also be either machined in plate 13, or it can be also in form of a guiding channel which is additionally attached to the face of the disk. Figure 1 illustrates a preferred embodiment of this invention, including an intermediate disk 20 provided on its circumference with a ball bearing 23 which is shiftable transversely to the axis of rotation of shafts 10 and 12. The bearings 14 and 15 of said shfats 10 respectively 12 are fixedly mounted in the housing 19.
In a position of the circumferential bearing 23 in which the center of rotation 21 of the intermediate plate 20 coincides with the axis of rotation of shafts 10 and 12, then, as shown in Figure 10, no speed differential is generated between the input and output shafts, inasmuch as the carrier pins 18 and 18a are spaced apart from the center of rotation 21 at the same distance.
As soon as the intermediate disk 20 is displaced by a distance X in radial direction with respect to the axis of rotation of the shafts 10 and 12 (Figures 1 and 2) then during the angular displacement of the input transmission plate 11 by an angle ~ the carrier pin 22a moves in the corresponding guiding groove 16a of the intermediate disk 20, and the latter is angularly displaced by an angle ~ which is smaller than the angle ~. For example, if the connection line 25 between the center 21 of the intermediate disk 20 and the carrier pin 22a is angularly displaced by ~ = 45 as shown in Figure 3, then the angular displacement of the connection line between the center of driving shaft 10 and the carrier pin 22a is larger than the 45.
_g_ C
~30~60 27412-1 As Figure 1 shows, the carrier pins 22 and 22a are fixed at opposite faces of the intermediate plate 20, and the corresponding guiding grooves 16 and 16a are formed in respective transmission plates 11 and 13.
Figures 2 - 8 show the relationship between the angular displacement of the output transmission plate 13 by the angle = 270, generated in response to the angular displacement ~ of the intermediate disk 20, which is radially shifted by a distance X relative to the axis 21 of rotation of the input and output shafts. At an angle of rotation between 0 and 180, the angular displacement ~ of the intermediate disk 20 lags behind the angular displacement ~ of the output shaft 12 and its transmission plate 13. At 180, illustrated in Figure 5, the angular displacements ~ and ~ are equal~ At angles exceeding 180, the rotary speed of the intermediate disk 20 exceeds the rotary speed of the output disk 13; in other words the angular displacement ~ is larger than the angular displacement ~ , as seen in Figures 6 and 7 showing respectively the angles ~ = 225 and 270. This behav~or is illustrated in the plot diagram of Figure 9, where the abscissa denotes the angular displacement during one cycle of the shaft and the ordinate denotes the variation of the rotary speed of one shaft relative to the rotary speed of the other shaft. In this example, it is assumed that output shaft 12 with its trasmission plate 13 rotates at uniform speed, whereas depending on the radial displacement A
be~ween the center 21 of the intermediate disk 20 and the axis of rotation of the driven shaft 12, the positive rotary speed change occurs between 0 and 180 and the negative speed change ~23~760 occurs between 180 and 360. At 0, 180 and at 360, the input and output shafts rotate at the same speed. From the plot of Figure 9, it is evident that during a single cycle of the input shaft the rotary speed of the output shaft varies according to a sine curve.
In Figure 8, the intermediate disk 20 is radially displaced relative to the axis of rotation of the output shaft by a distance Xl, which is smaller than the distance X in Figure
(' D~:VICE FOR GL.~ TIl~G D~Fl:`LP~EN'r SP~:EDS O~
ROT~TION BET~'E:N INPVT ~D O~TPUT SHN:TS
il `
~3076~) BACKGROVND OF THE INVENTION
The invention relates in general to a power transmis-sion device and in particular to a device for generating differ-ent speeds of rotation between an input shaft rotating prefer-ably with a uniform speed, about an axis, and a driven output shaft rotating about another axis.
~ Power transmission devices of this kind operate usually with gear trains. The disadvantage of geaxs is not only the fact that they are expensive in manufacture but also th~
difficulty in changing the rate of rotation between the input shaft and the output shaft, particularly if it is desirable to change the rotary speed between the two shafts during one cycle.
.5 Such a phase shift in the two courses of rotation in transmission gears can be accomplished only by exchanging corresponding gears.
SUMMARY OF THE INVENTION
~ ,.
It is therefore a general object of the present inven-tion to overcome the aforementioned disadvantages.
More particularly, it is an object of the invention to provide an improved differential device for producing differ-ent rotational speeds between a driving shaft rotating preferably at a uniform ~peed and a driven output ~haft, ~hich eliminates gears and is compDsed of simple rotation-symmetrical ~odies.
C l _ ~ ~
x~
123~760 27412-1 An addi.tional object of the invention is to provide such an improved transmission device in which t,he input shaft having a uniform rotary speed imparts to the driven output shaft a non-uniform rotary speed, or vice versa, and in which the speed difference is selectively adjustable.
A further object of the invention is to provide such an improved differential device at which the range of the generated speed difference is such that the driven shaft can become stationary in spite of the rotation of the driving shaft.
In keeping with these objects and others which will become apparent hereafter, one feature of the invention resides, in a transmission device of the above described type for generat-ing a rotary speed difference between an input shaft _otating about an axis and an output shaft rotating about another axis, said input and output shafts being aligned, comprisi.ng a first transmission plate of circular configuration connected for joint rotation with one of said shafts;
a second transmission plate of circular configuration connected for joint rotation with the other shaft;
a housing enclosing said transmission plates and supporting for rotation said input and output shafts;
an intermediate transmi.ssion disk supported for rotation in said housing between said first and a second transmission pla,tes and being rectilinearly displaceable in transverse direc-tion to the axes of said shafts, and the facing surfaces of said first and second transmission plates being provided respectively with a radial guiding groove;
1~30~7~0 each end face of said intermediate disk being provided with only one projecting carrier pin, each carrier pin being spaced apart from the center of rotation of the intermediate plate about the same distance and engaging the assigned radial guiding groove in the opposite transmission plate;
said radial guiding grooves in said transmission plates being through going and passing through the center of rotation of the corresponding plate symmetrically to the center and said intermediate disk being rectilinearly displaceable between a full-transmission position in which its center of rotation coincides with the axes of said input and output shafts, and two no-transmission positions in which one of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft or alternatingly the other of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft;
said intermedia~e transmission disk being supported for rotation in at least one circumferential bearing, said circum-ferential bearing being mounted in a rectangular frame which is displaceable in said housing in radial direction relative to the axis of rotation of said intermediate transmission disk and said frame being provided with a control rod passing through said housing r The construction of this invention employs simple geometrical bodies, such as for example rectangular or rotation-symmetrical disks.
_4_ ~'~3~760 27412-1 The carrier pin in said intermediate disk, which engages the guiding groove in each transmission plate, may have a configura-tion in the form of a cylindrical pin. As long as the intermediate disk is aligned along his axe of rotation with the axes of the transmission plates, no speed difference will result between the input shaft and the output shaft. As soon, however, as the axe of rotation of the intermediate disk is radially displaced rela-tive to the rotation axes of the transmission plates, then a different speed of rotation is generated between the input shaft and the output shaft; Depending on the magnitude of the displace ment, the course of the differential speed is completed during one cycle of the driving shaft; in a certain radial position of the intermediate disk, namely when the power transmitting carrier pin in one of said end faces of the intermediate disk is coaxial with the rotation axes of the two transmission plates, engaging the center of rotation of the corresponding guiding groove, the driven shaft becomes stationary in spite of the rotation of the driving shaft, and vice versa.
In a particularly advantageous embodiment, the shaft sections supporting the plates are journalled in a common housing in which is aranged the intermediate disk coupled by the groove and pin connections to the opposite first and second plates, and which is displaceable in radial direction relative to the axes of the input and output shafts.
In another advantageous modification of this invention, the plate assigned to the input shaft as well as the plate assigned to the output shaft are provided each with a guiding groove extending in radial direction, whereby the radially dis-~23~ 27412-1 placeable intermediate disk is provided at both end faces thereof with projecting carrier pins engaging the two guiding grooves.
According to another measure of this invention, the facing surfaces of the first and second plates connected to the input and output shafts are provided each with a single guiding groove crossing the center of rotation of the plate, and the intermediate disk is radially displaceable about a distance and one of its eccentric carrier pins is shiftable in a position in which it is coaxial either with the input shaft or on the opposite side, with the axis of rotation of the output shaft. This solution makes it possible that during one cycle of one plate, the differential speed at the other plate can ke such that even at a rotating input shaft the output shaft stands still.
The guiding groove in the first or in the second plate, assigned to the input shaft or to the output shaft, can be rectilinear. Preferably, the guiding groove extends over the entire diameter of the disk, or in the case of rectangular plates over the entire longer surface of the plate. The speed differential generating effect between the input and output shafts can be improved by providing a curved guiding groove.
A further improvement can be achieved when, in the embodiment in which the guiding grooves are provided in the opposite faces of the first and second plates, when the curve of the guiding groove in one plate differs from the curve of the opposite guiding groove.
In a further modification of the device of this invention, the C
~30760 27412-1 intermediate plate is in the form of a disk surrounded by a bearing which in turn is supported in a rectangular frame which is shiftable transversely to the axis of rotation of the inter-mediate disk. Preferably, the rectangular frame is connected to a plunger projecting in radial direction through the housing.
It is also of advantage when the bearing surrounding the intermediate disk is arranged in a further bearing which is rotatable in opposite direction relative to the inner bearing.
The novel features which are considered characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construc-tion and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in con-nection with the accompanying drawing.
BRIEF DESCRIPTION OF THE DRAWING
_ _ .
Figure 1 is a sectional top view of a schematic repre-sentation of the transmission device of this invention;
Figures 2 - 8 show respectively various angular posi-tions of radially displaced transmission plates in the device of Figure l;
Figure 9 is a plot diagram of the speed variation of one shaft versus the angular position of uniformly rotating other shaft;
Figure 10 is a further modification of the device of Figure l;
C
27412-l ~Z30760 Figure 11 shows the radial displacement of the inter-mediate disk in the device of Figure 10;
Figures 12 and 13 show respectively different shapes of guiding grooves in the transmission platesi Figure 14 is a side view of a shiftable support for the intermediate transmission disk;
Figure 15 is a plot diagram of different speeds of rotation between the input and output shafts;
Figure 16 is a vertical section of still another modification of the device of this invention; and Figure 17 shows schematically by way of an example the application of the device of this invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring firstly to Figure 1, the transmission device has an input shaft 10 fixedly connected at its end to a transverse transmission plate 11. Preferably, the shaft and the plate are made as a one-piece component. Plate 11 faces another transmission plate 13 which is fixedly connected to an output shaft 12. In this embodiment, the transmission plates 11 and 13 have circular configuration. The input and output shafts are supported in bearings 14 and 15, respectively. The end face of transmission plate 11 is formed with a radially directed guiding groove 16 of a rectangular cross section. The groove 16 is either machined in the plate 11, or it can be also in the form of a guiding channel which is additionally attached to the face of the disk. The end face of transmission plate 13 is also formed with a radially directed guiding groove 16a of a rectang-C
~.~3(1760 ular cross section~ Said groove 16a may also be either machined in plate 13, or it can be also in form of a guiding channel which is additionally attached to the face of the disk. Figure 1 illustrates a preferred embodiment of this invention, including an intermediate disk 20 provided on its circumference with a ball bearing 23 which is shiftable transversely to the axis of rotation of shafts 10 and 12. The bearings 14 and 15 of said shfats 10 respectively 12 are fixedly mounted in the housing 19.
In a position of the circumferential bearing 23 in which the center of rotation 21 of the intermediate plate 20 coincides with the axis of rotation of shafts 10 and 12, then, as shown in Figure 10, no speed differential is generated between the input and output shafts, inasmuch as the carrier pins 18 and 18a are spaced apart from the center of rotation 21 at the same distance.
As soon as the intermediate disk 20 is displaced by a distance X in radial direction with respect to the axis of rotation of the shafts 10 and 12 (Figures 1 and 2) then during the angular displacement of the input transmission plate 11 by an angle ~ the carrier pin 22a moves in the corresponding guiding groove 16a of the intermediate disk 20, and the latter is angularly displaced by an angle ~ which is smaller than the angle ~. For example, if the connection line 25 between the center 21 of the intermediate disk 20 and the carrier pin 22a is angularly displaced by ~ = 45 as shown in Figure 3, then the angular displacement of the connection line between the center of driving shaft 10 and the carrier pin 22a is larger than the 45.
_g_ C
~30~60 27412-1 As Figure 1 shows, the carrier pins 22 and 22a are fixed at opposite faces of the intermediate plate 20, and the corresponding guiding grooves 16 and 16a are formed in respective transmission plates 11 and 13.
Figures 2 - 8 show the relationship between the angular displacement of the output transmission plate 13 by the angle = 270, generated in response to the angular displacement ~ of the intermediate disk 20, which is radially shifted by a distance X relative to the axis 21 of rotation of the input and output shafts. At an angle of rotation between 0 and 180, the angular displacement ~ of the intermediate disk 20 lags behind the angular displacement ~ of the output shaft 12 and its transmission plate 13. At 180, illustrated in Figure 5, the angular displacements ~ and ~ are equal~ At angles exceeding 180, the rotary speed of the intermediate disk 20 exceeds the rotary speed of the output disk 13; in other words the angular displacement ~ is larger than the angular displacement ~ , as seen in Figures 6 and 7 showing respectively the angles ~ = 225 and 270. This behav~or is illustrated in the plot diagram of Figure 9, where the abscissa denotes the angular displacement during one cycle of the shaft and the ordinate denotes the variation of the rotary speed of one shaft relative to the rotary speed of the other shaft. In this example, it is assumed that output shaft 12 with its trasmission plate 13 rotates at uniform speed, whereas depending on the radial displacement A
be~ween the center 21 of the intermediate disk 20 and the axis of rotation of the driven shaft 12, the positive rotary speed change occurs between 0 and 180 and the negative speed change ~23~760 occurs between 180 and 360. At 0, 180 and at 360, the input and output shafts rotate at the same speed. From the plot of Figure 9, it is evident that during a single cycle of the input shaft the rotary speed of the output shaft varies according to a sine curve.
In Figure 8, the intermediate disk 20 is radially displaced relative to the axis of rotation of the output shaft by a distance Xl, which is smaller than the distance X in Figure
2. As a result of this shorter displacement, the difference between the angular displacements ~ and ~ is also smaller.
Similarly, in increasing the radial displacement X, the variation of the rotary speed difference will also be increased.
Figure 10 as well as Figure 11 illustrate an embodiment of this invention which differs from the embodiment of Figure 1 in that the guiding grooves 16 and 16a extend over the entire diameter of the corresponding transmission plates 11 and 13. The carrier pins 18 and 18a are mirror-sylilmetrically arranged on opposite sides of the intermediate plate 20 relative to its center of rotation 21. As long as the center or the axis of rotation 21 of the intermediate disk 20 as shown in Figure 10 coincides with the rotary axis of shafts 10 and 12, then no speed difference between the input and output will result. On the other hand, if the intermediate disk 20 is shifted in radial direction to a position as shown in Figure 11, in which the center axis of carrier pin 18 is in alignment with the axis of rotation of driving shaft 10, then the torque transmission is interrupted, inasmuch as the intermediate disk 20 is no longer set in rotary C
~Z3~760 27412-1 motion in spite of the rotation of the input transmission plate 11 (Figure 11).
In the embodiment according to Figures 10 and 11, the guiding grooves 16 and 16a are rectilinear. In the modification illustrated in Figures 12 and 13, the guiding grooves 16 or 16a may have a curved configuration. In either case, the guiding grooves 16 and 16a pass through the center of rotation of the assigned transmission plate, so that the aforementioned neutral or axially aligned position of the plate might be set. By means of the curvature of the guiding grooves, it is possible that the aforedescribed sinusoidal change of the speed difference can be modified. For example, the curve of Figure 9 may have a steeper ascending portion with a flat descending part, and vice versa, as will be explained below.
It will be seen also from Figures 10 and 11 that the circumferential ball bearing 23 on the intermediate plate 20 is inserted in an outer bearing 26 which in turn is rotatably supported in a frame 27 (Figure 14). The outer bearing 26 can be rotated by a carrier pin 29 against the direction of rotation 28 and 28a of the intermediate disk 20 and the inner bearing 23.
In this manner, the speed differential between the input and output shafts, or vice versa, can be additionally adjusted.
According to the embodiment of Figure 14, the frame 27 is connected to a control rod 31 passing through the housing 19.
Needle rollers 33 support the frame 27 so as to facilitate its reciprocating movement introduced by the control rod 31, as indicated by arrow 32.
C
~30760 By virtue of the aforementioned possibility to adjust the angular position of the intermediate disk 20 in a direction which is counter to the direction imparted by the input shaft, a multitude of possibilities to adjust the course of the rotary speed difference between the input and output shafts results. For example, as illustrated in the plot diagram in Figure 15, horizontal line 10 indicates a constant rotational rate of the input shaft 10. The plot of the rate of rotation of the output shaft 12 is illustrated in full lines, and an example of its adjustment is illustrated by a dashed line. Provided that the input shaft 10 rotates at a constant speed, in a starting position of the intermediate disk 20 its rotary angle ~ increases from 0 to 90. At this point, the intermediate disk 20 is shifted in its neutral position, illus-trated in Figure 11, and the rotary speed of the output shaft 12 is immediately set to zero, and in thislcondition it can remain for an arbitrarily long time interval, which in Figure 15 spans the angular displacement of 360. At this point, the intermed-iate disk 20 is again displaced in radial direction, and the speed difference between the input and output shafts steeply increases, whereupon in response to another displacement of frame 27 to a neutral position the output speed drops to zero again. Another example of the speed transmission shown by the dashed line, according to which the output speed is intermittently adjusted to equal the input rotary speed. Inasmuch as the transverse displacement of the frame 27 with the intermediate plate 20 can occur within broad limits and during the rotation ~3~
of the input and output shafts, then apart Erom -the aforementioned positions a-t which the ou-tput rotary speed equals the input rotary .speed, or the output rotary speed is zero during -the rotating inpu-t shaft, additional adjusting possibilities are achievable by changlng -the shape of the guiding groove 16 or 16a.
For this purpose it is of advantage when the guiding grooves are in the form of channels which are exchangeably connectable to -the intermedia-te disk.
In the embodiment according to Figure 16, the input shaft 10 as well as the output shaft 12 are arranged in align-ment with each other and supported respectively in bearings 14a and 14, and 15a and 15. Carrier pins 18 and 18a projecting from the intermediate plate are provided with ball bearings 34 and 34a engaging the corresponding guiding grooves 16 and 16a in the opposite transmission plates.
An example of an application of -this inven-tion is shown in Figure 17. For instance, in feeding a double-layered plastic foil, the advancing rollers 36 and 37 rotate respectively at different speeds, so as to shift the lower layer of foil 35 relative -to -the upper layer. Also -the cutting blade 38 may be driven by the device of this invention in such a manner that, prior to its cutting action, the rotary speed of its driving shaft 39 is accelerated, whereupon after the cu-t is made, the rotary speed in the direction of arrow 40 is decelerated.
It will be understood -that each of the elements described above, or two or more together, may also find a useful application in other types of constructions differing from the types described above.
~11 11 1;~31~760 1 prior art fairly constitute essential characteristics of the l generic or specific aspects of this invention.
i What is claimed as new and desired to be S Iprote ted t! ~etters Pa~ent is set fo th n ~he ~p~ended 1. ~
., , . -15-C . ' .
Similarly, in increasing the radial displacement X, the variation of the rotary speed difference will also be increased.
Figure 10 as well as Figure 11 illustrate an embodiment of this invention which differs from the embodiment of Figure 1 in that the guiding grooves 16 and 16a extend over the entire diameter of the corresponding transmission plates 11 and 13. The carrier pins 18 and 18a are mirror-sylilmetrically arranged on opposite sides of the intermediate plate 20 relative to its center of rotation 21. As long as the center or the axis of rotation 21 of the intermediate disk 20 as shown in Figure 10 coincides with the rotary axis of shafts 10 and 12, then no speed difference between the input and output will result. On the other hand, if the intermediate disk 20 is shifted in radial direction to a position as shown in Figure 11, in which the center axis of carrier pin 18 is in alignment with the axis of rotation of driving shaft 10, then the torque transmission is interrupted, inasmuch as the intermediate disk 20 is no longer set in rotary C
~Z3~760 27412-1 motion in spite of the rotation of the input transmission plate 11 (Figure 11).
In the embodiment according to Figures 10 and 11, the guiding grooves 16 and 16a are rectilinear. In the modification illustrated in Figures 12 and 13, the guiding grooves 16 or 16a may have a curved configuration. In either case, the guiding grooves 16 and 16a pass through the center of rotation of the assigned transmission plate, so that the aforementioned neutral or axially aligned position of the plate might be set. By means of the curvature of the guiding grooves, it is possible that the aforedescribed sinusoidal change of the speed difference can be modified. For example, the curve of Figure 9 may have a steeper ascending portion with a flat descending part, and vice versa, as will be explained below.
It will be seen also from Figures 10 and 11 that the circumferential ball bearing 23 on the intermediate plate 20 is inserted in an outer bearing 26 which in turn is rotatably supported in a frame 27 (Figure 14). The outer bearing 26 can be rotated by a carrier pin 29 against the direction of rotation 28 and 28a of the intermediate disk 20 and the inner bearing 23.
In this manner, the speed differential between the input and output shafts, or vice versa, can be additionally adjusted.
According to the embodiment of Figure 14, the frame 27 is connected to a control rod 31 passing through the housing 19.
Needle rollers 33 support the frame 27 so as to facilitate its reciprocating movement introduced by the control rod 31, as indicated by arrow 32.
C
~30760 By virtue of the aforementioned possibility to adjust the angular position of the intermediate disk 20 in a direction which is counter to the direction imparted by the input shaft, a multitude of possibilities to adjust the course of the rotary speed difference between the input and output shafts results. For example, as illustrated in the plot diagram in Figure 15, horizontal line 10 indicates a constant rotational rate of the input shaft 10. The plot of the rate of rotation of the output shaft 12 is illustrated in full lines, and an example of its adjustment is illustrated by a dashed line. Provided that the input shaft 10 rotates at a constant speed, in a starting position of the intermediate disk 20 its rotary angle ~ increases from 0 to 90. At this point, the intermediate disk 20 is shifted in its neutral position, illus-trated in Figure 11, and the rotary speed of the output shaft 12 is immediately set to zero, and in thislcondition it can remain for an arbitrarily long time interval, which in Figure 15 spans the angular displacement of 360. At this point, the intermed-iate disk 20 is again displaced in radial direction, and the speed difference between the input and output shafts steeply increases, whereupon in response to another displacement of frame 27 to a neutral position the output speed drops to zero again. Another example of the speed transmission shown by the dashed line, according to which the output speed is intermittently adjusted to equal the input rotary speed. Inasmuch as the transverse displacement of the frame 27 with the intermediate plate 20 can occur within broad limits and during the rotation ~3~
of the input and output shafts, then apart Erom -the aforementioned positions a-t which the ou-tput rotary speed equals the input rotary .speed, or the output rotary speed is zero during -the rotating inpu-t shaft, additional adjusting possibilities are achievable by changlng -the shape of the guiding groove 16 or 16a.
For this purpose it is of advantage when the guiding grooves are in the form of channels which are exchangeably connectable to -the intermedia-te disk.
In the embodiment according to Figure 16, the input shaft 10 as well as the output shaft 12 are arranged in align-ment with each other and supported respectively in bearings 14a and 14, and 15a and 15. Carrier pins 18 and 18a projecting from the intermediate plate are provided with ball bearings 34 and 34a engaging the corresponding guiding grooves 16 and 16a in the opposite transmission plates.
An example of an application of -this inven-tion is shown in Figure 17. For instance, in feeding a double-layered plastic foil, the advancing rollers 36 and 37 rotate respectively at different speeds, so as to shift the lower layer of foil 35 relative -to -the upper layer. Also -the cutting blade 38 may be driven by the device of this invention in such a manner that, prior to its cutting action, the rotary speed of its driving shaft 39 is accelerated, whereupon after the cu-t is made, the rotary speed in the direction of arrow 40 is decelerated.
It will be understood -that each of the elements described above, or two or more together, may also find a useful application in other types of constructions differing from the types described above.
~11 11 1;~31~760 1 prior art fairly constitute essential characteristics of the l generic or specific aspects of this invention.
i What is claimed as new and desired to be S Iprote ted t! ~etters Pa~ent is set fo th n ~he ~p~ended 1. ~
., , . -15-C . ' .
Claims (4)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A device for generating a rotary speed difference between an input shaft rotating about an axis and an output shaft rotating about another axis, said input and output shafts being aligned, comprising a first transmission plate of circular configuration connected for joint rotation with one of said shafts;
a second transmission plate of circular configuration connected for joint rotation with the other shaft;
a housing enclosing said transmission plates and supporting for rotation said input and output shafts;
an intermediate transmission disk supported for rotation in said housing between said first and a second transmission plates and being rectilinearly displaceable in transverse direction to the axes of said shafts, and the facing surfaces of said first and second transmission plates being provided respectively with a radial guiding groove;
each end face of said intermediate disk being provided with only one projecting carrier pin, each carrier pin being spaced apart from the center of rotation of the intermediate plate about the same distance and engaging the assigned radial guiding groove in the opposite transmission plate;
said radial guiding grooves in said transmission plates being through going and passing through the center of rotation of the corresponding plate symmetrically to the center and said intermediate disk being rectilinearly displaceable between a full-transmission position in which its center of rotation coincides with the axes of said input and output shafts, and two no-transmission positions in which one of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft or alternatingly the other of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft;
said intermediate transmission disk being supported for rotation in at least one circumferential bearing, said circum-ferential bearing being mounted in a rectangular frame which is displaceable in said housing in radial direction relative to the axis of rotation of said intermediate transmission disk and said frame being provided with a control rod passing through said housing.
a second transmission plate of circular configuration connected for joint rotation with the other shaft;
a housing enclosing said transmission plates and supporting for rotation said input and output shafts;
an intermediate transmission disk supported for rotation in said housing between said first and a second transmission plates and being rectilinearly displaceable in transverse direction to the axes of said shafts, and the facing surfaces of said first and second transmission plates being provided respectively with a radial guiding groove;
each end face of said intermediate disk being provided with only one projecting carrier pin, each carrier pin being spaced apart from the center of rotation of the intermediate plate about the same distance and engaging the assigned radial guiding groove in the opposite transmission plate;
said radial guiding grooves in said transmission plates being through going and passing through the center of rotation of the corresponding plate symmetrically to the center and said intermediate disk being rectilinearly displaceable between a full-transmission position in which its center of rotation coincides with the axes of said input and output shafts, and two no-transmission positions in which one of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft or alternatingly the other of said carrier pins of said intermediate transmission disk is in alignment with the axis of said input shaft or said output shaft;
said intermediate transmission disk being supported for rotation in at least one circumferential bearing, said circum-ferential bearing being mounted in a rectangular frame which is displaceable in said housing in radial direction relative to the axis of rotation of said intermediate transmission disk and said frame being provided with a control rod passing through said housing.
2. A device as defined in claim 1, wherein each guiding groove extends in radial direction along a straight line.
3. A device as defined in claim 1, wherein each guiding groove passes through the center of rotation of the assigned transmission plate and extends along a curved line.
4. A device as defined in claim 1, wherein the guiding groove on the first transmission plate has a different configuration than the guiding groove on the second transmission plate.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ZA82/2946 | 1982-04-29 | ||
| ZA822946 | 1982-04-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1230760A true CA1230760A (en) | 1987-12-29 |
Family
ID=25576046
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000427023A Expired CA1230760A (en) | 1982-04-29 | 1983-04-29 | Speed variator |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0093305B1 (en) |
| JP (1) | JPS5917028A (en) |
| AT (1) | ATE18596T1 (en) |
| CA (1) | CA1230760A (en) |
| DE (1) | DE3362501D1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996001960A1 (en) * | 1994-07-08 | 1996-01-25 | Prosser-Fenn, James, Edward | Drive mechanism |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3327610A1 (en) * | 1983-07-30 | 1985-02-07 | Franz Bendig | DEVICE FOR CONTROLLING THE MOVEMENT PROCESS IN A FILM PROCESSING MACHINE |
| JPS61244454A (en) * | 1985-04-19 | 1986-10-30 | Seiwa Sangyo Kk | Spiral groove forming device |
| FR2665937B1 (en) * | 1990-08-16 | 1993-01-08 | Rosset Bernard | DEVICE FOR USING A VARIABLE SPEED CIRCULAR MOTION FOR DRIVING A CONSTANT SPEED CIRCULAR MOTION. |
| GB9304288D0 (en) * | 1993-03-03 | 1993-04-21 | Allday Esca J | Improvements in or relating to variable gears and drives |
| WO2008062190A2 (en) * | 2006-11-23 | 2008-05-29 | Applied Engine Technology Limited | A rectilinear drive mechanism providing counter-rotation, speed ratio changes and reciprocating rectilinear motion |
| FR3002017B1 (en) * | 2013-02-12 | 2015-02-27 | Univ Bordeaux 1 | VIBRATORY SYSTEM |
| KR101671611B1 (en) * | 2015-01-12 | 2016-11-01 | 권윤구 | Transmission |
| HUE050780T2 (en) | 2016-06-21 | 2021-01-28 | Kkd Getriebebau Ug | Device for force transmission |
| CN107387696A (en) * | 2017-07-08 | 2017-11-24 | 吴大友 | Booster |
| CN109854694A (en) * | 2019-01-29 | 2019-06-07 | 四川云智云造科技有限公司 | A kind of change torsion coupling device |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR382427A (en) * | 1906-10-01 | 1908-02-06 | Hans Kupferschmid | Movement transmission mechanism |
| GB190900708A (en) * | 1909-01-11 | 1910-04-11 | Charles Abram Gee | Improvements in and relating to Means for Converting Continuous Rotary into Intermittent Rotary Motion. |
| AT108324B (en) * | 1926-04-29 | 1927-12-27 | Bosch Robert | Reduction gear with eccentric drive. |
| FR901584A (en) * | 1943-01-29 | 1945-07-31 | Philips Nv | Coupling of rotating parts using an auxiliary shaft |
| FR1068216A (en) * | 1952-12-06 | 1954-06-23 | Rotary drive device | |
| AT189002B (en) * | 1954-02-24 | 1957-02-25 | Johannes Neukirch | Eccentric gear |
| FR1138139A (en) * | 1955-01-08 | 1957-06-11 | Double lever mechanism | |
| DE1223218B (en) * | 1962-12-22 | 1966-08-18 | Windenfabrik Gottfried Schober | Eccentric epicyclic gear |
| GB1216557A (en) * | 1967-04-21 | 1970-12-23 | Desma Werke Gmbh | Improvements in gearings for producing intermittent and cyclically variable speed rotation |
| US3491604A (en) * | 1968-02-12 | 1970-01-27 | Cass B Levi | Device for modifying rotary motion |
| CH567200A5 (en) * | 1972-10-16 | 1975-09-30 | Koppers Co Inc | |
| US4332148A (en) * | 1980-06-04 | 1982-06-01 | General Motors Corporation | Cyclic phase-change coupling |
-
1983
- 1983-04-18 DE DE8383103742T patent/DE3362501D1/en not_active Expired
- 1983-04-18 EP EP83103742A patent/EP0093305B1/en not_active Expired
- 1983-04-18 AT AT83103742T patent/ATE18596T1/en active
- 1983-04-28 JP JP58074147A patent/JPS5917028A/en active Pending
- 1983-04-29 CA CA000427023A patent/CA1230760A/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996001960A1 (en) * | 1994-07-08 | 1996-01-25 | Prosser-Fenn, James, Edward | Drive mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5917028A (en) | 1984-01-28 |
| DE3362501D1 (en) | 1986-04-17 |
| EP0093305A1 (en) | 1983-11-09 |
| EP0093305B1 (en) | 1986-03-12 |
| ATE18596T1 (en) | 1986-03-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA1230760A (en) | Speed variator | |
| US3968700A (en) | Device for converting rotary motion into a unidirectional linear motion | |
| CA1238209A (en) | Transmission apparatus | |
| RU2130140C1 (en) | Transmission | |
| EP0207206B1 (en) | Gearless differential speed reducer | |
| US8287424B2 (en) | Speed adjusting mechanism for roller traction toroidal continuously variable transmission | |
| CN110425255A (en) | Sinusoidal plane second level movable teeth reducer | |
| CA1065168A (en) | Cyclic motion generator | |
| EP0688407B1 (en) | Mechanical gearing | |
| KR20000022074A (en) | Method and device for producing workpieces with a non-circular internal and/or external shape | |
| CA1282265C (en) | Frictionless continuously variable transmission | |
| US4715249A (en) | Speed change device | |
| EP0378978A2 (en) | A gear transmission | |
| CN2173882Y (en) | Planetary steel ball variable drive | |
| KR830009959A (en) | Differential transmission | |
| KR101801419B1 (en) | Mechanical speed variator with eccentric dynamic masses having a balanced structure | |
| RU2003132074A (en) | METHOD AND DEVICE FOR MANUFACTURE OF TRANSMISSION-FREE TRANSMISSION DISCS | |
| KR20000056955A (en) | Variable speed change gear | |
| CA2082591A1 (en) | Variable speed drive transmission | |
| US3793895A (en) | Power transmitting device | |
| CN108406754A (en) | A kind of leading screw servo articulated mechanical arm | |
| CN86106289A (en) | Reversible differential stepless variable speed gear | |
| GB2109084A (en) | Motion transmitting device | |
| US2506195A (en) | Variable speed friction gearing | |
| KR100454761B1 (en) | Backlash Adjustable Planetary Gear Reducer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |