JP2008202611A - Groove-fitting constant velocity joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a low-cost groove-fitting constant velocity joint of simple structure capable of reducing the location interval between devices in comparison with a propeller shaft mechanism using a pair of universal joints and a spline yoke or a constant velocity drive shaft mechanism conventionally used to transmit constant velocity rolling force between devices, of which shaft center position is irregularly changed in a direction at a right angle against the shaft, in the case of transmitting constant velocity rolling force between devices wherein the shaft centers of a driving shaft and a driven shaft are offset in a direction at a right angle against the shaft. <P>SOLUTION: Bar-like projections 4 and 8 are provided in one end of each of shafts 2 and 10 on a drive side and a driven side for transmitting rotating power between a driving and a driven devices, and recessed grooves 5 wherein the projections 4 and 8 of the driving and driven shafts 2 and 10 are fitted to be slid, crossing at a right angle against each other at the center of one plate 16 in the surface and the back surface thereof. Each of the recessed parts 5 of the surface and the back surface of the plate are fitted in the projections 4 and 8 of the shaft of the driving and driven devices facing each other so as to form joint structure for transmitting constant velocity rolling force between the devices. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

In the present invention, when rotational power is transmitted between a drive and a driven device, the drive and driven shaft positions of each device are different, or the shaft position between the devices changes or changes. The present invention relates to a mechanism for transmitting rotational power at a constant speed between the devices.

This is a typical device, such as the constant-speed drive shaft and propeller shaft of a rotational power transmission mechanism of an automobile. In order to transmit constant-speed rotational power between devices such as indefinite changes in the direction perpendicular to the axis extension direction, the rotational power is transmitted by a propeller shaft equipped with a pair of universal joints or a constant-speed drive shaft. ing.

(A) In order to construct a constant-speed drive shaft or propeller shaft, a pair of universal joints that combine many high-precision parts is required.
(B) When rotational power is transmitted using a constant-speed drive shaft or propeller shaft, if there is a change in the axial center position between the driven and driven devices, the distance between the devices will be expanded and contracted. A spline yoke is required, and the length of the constant-speed drive shaft and propeller shaft mechanism requires the size of a pair of universal joints and the length of the spline yoke.
(C) The present invention has problems such as omission of the pair of universal joints of (A), omission of the spline yoke of (A), and reduction of the minimum installation interval of the driving and driven devices. It was made to solve.

(A) As shown in FIG. 1, a square plate-like protrusion 4 is provided on a circular plate 3 and coupled to the driven-side tip of the drive shaft 2.
(A) As in (A) above, a square bar-like protrusion 8 is provided on the circular plate 9 and coupled to the driving-side tip of the driven shaft 10.
(C) A groove 5 is provided on one surface of the circular plate slide plate 6 so as to be slidably fitted with the protrusion 4 of the drive shaft 2.
(D) The groove 7 is slide-fitted with the projection 8 of the driven shaft 10 on the other side of the circular plate slide plate 6 and the groove 5 of the above (c) is at the center. Provide to intersect at right angles.
(E) The groove 5 of the slide plate 6 is fitted to the protrusion 4 of the drive shaft 2, and the protrusion 8 of the driven shaft 10 is fitted to the groove 7 of the slide plate 6 to constitute a groove fitting constant velocity joint. .
(F) With the configuration of (v) above, when the drive shaft 2 is rotated, the rotation rotates the driven shaft 10 via the slide plate 6.
(G) When the groove-fitting constant velocity joint moves rotational power from the driving device 1 to the driven device 11 and moves the axial distance between the driving shaft 2 and the driven shaft 10 in the angular direction of the axial extension direction. Since the groove 5 of the slide plate 6 and the groove 7 of the slide plate 6 intersect each other at right angles, the protrusion 4 of the input shaft 2, the groove 5 of the slide plate 6 and the protrusion 8 of the driven shaft 10 are provided. The groove 7 of the slide plate 6 slides, and constant speed rotational power is transmitted while the slide plate 6 rotates and moves.
(H) By making the protrusions 4 of the drive shaft 2 and the protrusions 8 of the driven shaft 10 or the grooves 5 and 7 of the slide plate 6 large, the axial centers of the drive shaft 2 and the driven shaft 10 are mutually increased. The distance that can be moved between can be set large.

(A) The groove-fitting constant velocity joint of the present invention has an extremely simple structure and can transmit rotational power at a constant speed between devices with different shaft center positions of the drive shaft 2 and the driven shaft 10, so that it can be used for the same application. Compared to the propeller shaft mechanism and constant-speed drive shaft mechanism, a pair of universal joint mechanisms and spline yokes that combine many high-precision parts become unnecessary.
(B) The groove-fitting constant velocity joint has a simpler structure and lower production costs compared to the conventional propeller shaft mechanism and constant velocity drive shaft.
(C) Since the installation interval between the drive and the driven device can be reduced, the configuration of the entire machine can be reduced in size.
(D) Groove-fitting constant velocity joints are also effective for use in toys that have functions such as rotation, rotation, and swing, taking advantage of the low cost of production.
(E) As shown in (c), the groove-fitting constant velocity joint is characterized by the small distance between the driven and driven devices, and the ability to arbitrarily control the distance between the shafts. It is also effective to adopt it for operations such as shoulder indirect and neck joints.
(F) The rotating wheel eccentric rotation mechanism described in FIGS. 6 and 0010 is impossible with the conventional propeller shaft mechanism and constant speed drive shaft by utilizing the groove fitting constant speed joint. This makes it possible to arbitrarily control the position of the center of rotation of another rotating body that rotates together with the rotating shaft provided on the rotating shaft, making it possible to apply this characteristic to a variety of applications.
(G) The rotating wheel eccentric rotation mechanism of (F) above can be connected to several rotating wheels on a single rotating shaft, and is useful for driving caterpillars, conveyor belts, etc. with high accuracy and high efficiency. It is effective.

(A) Hereinafter, embodiments of the present invention will be described. FIG. 1 is an exploded view of each part of a groove fitting constant velocity joint.
(A) The drive shaft 2 in FIG. 1 has a disk 3 having a protrusion 4 directly connected to the driven shaft end, and a disk 9 having a protrusion 8 directly connected to the drive shaft side end of the driven shaft 10. is there.
(C) On the driving side surface of the slide plate 6, there are five grooves that are slidably fitted on the protrusions 4 of the driving shaft 2, and on the opposite driven side surface, there are grooves 7 that are slidably fitted on the protrusions 8 of the driven shaft 10. In the center of the slide plate 6, they are provided so as to cross each other at right angles.
(D) The material and structure of the drive shaft projection 4 and the groove 5 of the slide plate 6, and the driven shaft projection 8 and the groove 7 of the slide plate 6 are made of materials and structures having a small friction coefficient, and are lubricated. Consider dust prevention.
(E) The height and width of the projection 4 of the drive shaft and the projection 8 of the driven shaft 10 and the depth and width of the groove 7 are set to a size that takes into account the transmission torque, as well as the groove 5 of the slide plate 6 fitted to them. To do.
2A is a top perspective view of the assembled state, FIG. 2B is a bottom perspective view, and FIG. 2C is a perspective view of the drive coaxial 2 from the perspective view of FIG. It is a diagram in which the distance between the shaft centers of the driven shafts 10 is moved horizontally by a distance N. Note that the difference in size between the driving side plate 3 and the driven side plate 9 in each drawing is for ease of illustration and representation. Yes, the practical size can be the same.

(A) FIG. 3G shows the direction of movement of the driven shaft 10, and FIG. 3A shows the groove-fitting constant velocity joint with the drive shaft 2 and the driven shaft 10. It is a bottom perspective view when the driven shaft 10 is moved N in the X direction shown in FIG. (G) from the state where it is assembled on the same core, and FIG. (A1) is a plan view when FIG. (A) is viewed from above. FIG.
(B) The virtual diagram IC in FIG. 3A1 is the drive shaft core, UC is the driven shaft core, SPC is the center of the slide plate 6, and R is the rotation of the drive shaft 2. This is a virtual circle drawn by the center SPC of the slide plate 6 when transmitted to the driven shaft 10.
(C) Figures (B), (C), (D), and (E) of FIG. 3 are based on FIG. (A), and the drive shaft 2 is moved to the slide plate every 45 degrees. 6 is a lower perspective view showing a state in which rotation is transmitted to the driven shaft 10 through 6. FIG.
(D) Figure (B1) in Figure 3 is shown in Figure (B), Figure (C1) is shown in Figure (C), Figure (D1) is shown in Figure (D), and Figure (E1) is shown in Figure (E). It is a corresponding plane virtual view seen from the top.
(E) From (f) to (c), the process of transmitting the rotation of the drive shaft 2 by 180 ° to the driven shaft 10 having a different axis position will be described.
(F) The grooves 5 and 7 on the front and back of the slide plate 6 are provided so as to be perpendicular to each other at the center.
(G) FIG. 3A is a diagram in which the driven shaft UC is moved N from the drive shaft IC in the X direction shown in FIG. The groove 5 of the slide plate 6 to be fitted is also in the Y to -Y direction shown in FIG.
(H) Since the driven-side groove 7 of the slide plate 6 in FIG. 3A is provided at right angles to the driving-side groove 5, the projection 8 of the driven shaft 10 is the same as the groove 7. It is the X to -X direction shown in (G). FIG. 3A is a lower perspective view at this time, and FIG.
(R) 45R in FIG. 3B is a view in which the drive shaft 2 is rotated by 45 ° from the state of (G) and (K), and the projection 4 of the drive shaft 2 and the groove 5 of the slide plate 6 are shown. Also, the groove 7 of the slide plate 6 and the protrusion 8 of the driven shaft 10 are also rotated by 45 °. At this point, the center SPC of the slide plate 6 is between the concaves and convexes engaged with each other. It overlaps with the center position where the projection 4 of the drive shaft 2 and the projection 8 of the driven shaft 10 intersect while rotating with the slide. (FIG. 3B is a lower perspective view at this point, and FIG. B1 is a virtual plan view thereof.)
(G) 90R in FIG. 3C is a view in which the drive shaft 2 is further rotated by 45 ° from the state of (1) above, and the protrusion 4 of the drive shaft 2 and the groove 5 of the slide plate 6 are further provided. At the same time, the groove 7 of the slide plate 6 and the protrusion 8 of the driven shaft 10 are further rotated by 45 °. At this time, the center SPC of the slide plate 6 slides between the concaves and convexes that are engaged. While rotating, the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10 overlap each other at the center position.
(At this point, the slide plate 6 has revolved 180 ° centering on the middle of the IC and UC. FIG. 3C is a lower perspective view at this point, and FIG. is there. )
(S) 135R in FIG. 3D is a view in which the drive shaft 2 is further rotated by 45 ° from the state of (C), and the protrusion 4 of the drive shaft 2 and the groove 5 of the slide plate 6 are further provided. At the same time, the groove 7 of the slide plate 6 and the protrusion 8 of the driven shaft 10 are further rotated by 45 °. At this point, the center SPC of the slide plate 6 is slid between the concavo-convexities that are engaged. While rotating, it overlaps the center position where the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10 intersect. (Drawing (D) in FIG. 3 is a lower perspective view at this point, and FIG. (D1) is a virtual plan view thereof.)
(G) 180R in FIG. 3E is a view in which the drive shaft 2 is further rotated by 45 ° from the state (S). The protrusion 4 of the drive shaft 2 and the groove 5 of the slide plate 6 are also shown. Further, the groove 7 of the slide plate 6 and the protrusion 8 of the driven shaft 10 are further rotated by 45 °, and at this time, the center SPC of the slide plate 6 is between the engaging irregularities. While sliding and rotating, it overlaps the center position where the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10 intersect.
At this point, the slide plate 6 has made one revolution about the center between the center IC of the drive shaft 2 and the center UC of the driven shaft 10. (FIG. 3E is a lower perspective view at this time, and FIG. E1 is a virtual plan view thereof.)
(S) As described in (F) to (H) above, the center SPC of the slide plate 6 is located between the irregularities to be occluded while always obtaining the intersection of the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10. While rotating, revolving and revolving, the rotation of the drive shaft 2 is transmitted to the driven shaft 10 at an equal angle (constant speed).
The above is the explanation from 0 ° to 180 ° rotation transmission, but it is omitted from 180 ° to 360 ° rotation transmission, so it is omitted.

(A) FIG. 4G is a diagram showing the direction in which the center UC of the drive shaft 2 in FIG. A is moved, and FIG. 4A shows the groove-fitting constant velocity joint in FIG. FIG. 6 is a virtual plan view when the driven shaft 10 is moved N in the X direction shown in FIG. (G) from the state where the drive shaft 2 and the driven shaft 10 are assembled on the same core as shown in FIG.
(B) FIG. 4B shows a state in which the driven shaft 10 slides a distance A in the Y direction shown in FIG. 4G without rotating the driving shaft 2 from the state shown in FIG. In this figure, the center SPC of the slide plate 6 slides without rotating while finding the center point where the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10 intersect. At this time, the driven shaft 10 Does not rotate.
(C) FIG. 4C shows a state in which the driven shaft 10 is further moved by a distance B in the X direction shown in FIG. 4G without rotating the drive shaft 2 from the state of FIG. It is a diagram of sliding movement, and the center SPC of the slide plate 6 slides without rotating while finding the center point where the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10 intersect. 10 does not rotate.
(D) FIG. 4D shows the distance C in the −Y direction shown in FIG. 4G when the driven shaft 10 is not rotated from the state shown in FIG. It is a slide view, and the center SPC of the slide plate 6 slides without rotating while obtaining the center point where the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10 intersect. The shaft 10 does not rotate.
(E) FIG. 4E shows the distance N in the −X direction shown in FIG. 4G when the driven shaft 10 is not rotated from the state shown in FIG. It is a + D slide movement, and the center SPC of the slide plate 6 slides without rotating while finding the center point where the protrusion 4 of the drive shaft 2 and the protrusion 8 of the driven shaft 10 intersect. The driven shaft 10 does not rotate.
(F) As seen from (a) to (e) above, if the shaft position of the driven shaft 10 is slid without rotating the drive shaft 2, the drive shaft 2 and the driven shaft 10 will not rotate. The slide plate 6 slides without rotating along the center point where the projection 4 of the drive shaft 2 and the projection 8 of the driven shaft 10 intersect.
(G) Therefore, even if the distance between the shaft centers changes during transmission of rotational power from the drive shaft 4 to the driven shaft 10, the rotation of the drive shaft 2 is driven by the sliding movement of the slide plate 6 as described above. The rotation is transmitted to the moving shaft 10 at a constant speed.
However, when the distance between the drive shaft 2 and the driven shaft 10 is too large, the protrusion 4 of the drive shaft 2 and the groove 5 of the slide plate 6 and the protrusion 8 of the driven shaft 10 and the groove of the slide play 6 are provided. 7 is shortened and the rotational torsional force is concentrated on the mating part, resulting in an obstacle to sliding. Therefore, the length of each protrusion and groove is the distance between the center of the drive shaft 2 and the driven shaft 10 is the maximum. It is necessary to set it appropriately considering the above.

(A) FIG. 5A is a groove fitting constant velocity joint mechanism according to the present invention, and FIG. 5A is a diagram in which the installation offset interval between the driving device 1 and the driven device 11 is connected by N. It is an image diagram.
(A) FIG. 5B is a diagram using a conventional propeller shaft mechanism P, and FIG. 5B is a diagram in which the installation offset interval between the driving device 1 and the driven device 11 is N, and the propeller It is the figure which connected the phase angle X of the shaft mechanism P to 30 degrees.
(C) Comparing Figures (A) and (aa) in Figure 5 with Figures (B) and (bb), the groove fitting constant velocity joint mechanism in Figures (A) and (aa) It can be confirmed that the structure is simple, and the installable distance between each device of the driving device 1 and the driven device 11 can be reduced by C, which is the difference between A and B.

(A) Figure (6) shows a rotating wheel eccentric rotation mechanism utilizing a groove-fitting constant velocity joint. (The mechanism up to (0 009), where the driving and driven shaft cores are in the straight direction of each axis. The rotating shaft 21 of the rotating wheel 24 provided on the rotating shaft 21 is separated from the shaft core of the rotating shaft 21 (in addition to the mechanism for transmitting the rotational power at a constant speed between the devices arranged at different positions in the direction perpendicular to the rotating shaft 21). The mechanism is rotated at a position arbitrarily decentered from a, and this will be described below.
(A) FIG. 6A is a configuration diagram of the rotating wheel eccentric rotation mechanism, where the rotating shaft 21 is an input rotating shaft, the center of which is a, and the rotating shaft plate 22 is illustrated in FIG. 1 corresponds to the plate 3 having rod-shaped protrusions, the slide ring 23 corresponds to the slide plate 6 in FIG. 1 as an example, and the rotary wheel 24 has a protrusion on the drive shaft side in FIG. 1 as an example. The position adjusting collar A26 and the position adjusting collar B25 are provided to adjust and maintain the eccentric distance from the center a of the rotating shaft 21 when the rotating wheel 24 rotates. .
(C) The position adjustment collar A26 shown in FIGS. 6 (A), (B), (C), and (D) is a size that is incorporated so that the outer diameter rotates in the hole of the position adjustment collar 25. The center is b, the inner diameter is a size to be assembled to rotate on the rotary shaft 21, the center is offset from the center position by a distance n as shown in each figure, and an adjustment lever A27 to be rotated is attached.
(D) The position adjustment collar B25 shown in FIGS. 6A, 6B, 6C, and 6D of FIG. 6 is a size that is incorporated so that the outer diameter rotates in the hole of the rotating wheel 24, and is centered. c, the inner diameter is a size to be incorporated so that the position adjusting collar A26 is rotated, and the center is offset n distance from the center position c as shown in each figure, and an adjusting lever B28 to be rotated is attached.
(E) FIG. 6G shows the direction in which the center d of the rotating wheel 24 moves around the rotating shaft 21.
(F) In FIG. 6H, the position adjustment collar A26 and the position adjustment collar B25 are rotated in order to arbitrarily change the position of the rotation center d of the rotation wheel 24 with the center a of the rotation shaft 21 as a reference. The direction of rotation is indicated by right rotation as right and left rotation as left.
(G) The description of how the rotating wheel 24 rotates integrally with the rotating shaft 21 in FIG. 6 is the same as that described in the above (0 007), and is therefore omitted.
(H) FIG. 6B shows the case where the center d of the rotating wheel 24 rotates at the same position as the axis a of the rotating shaft 21 (the eccentric distance is zero). The center b is located at a distance n from the axis a of the rotating shaft 21 in the X direction shown in FIG. (G), and the center c of the position adjusting collar B25 is at the same position as the axis a of the rotating shaft 21. Yes.
(C) FIG. 6C shows the time when the center d of the rotating wheel 24 rotates from the axis a of the rotating shaft 21 at a distance n + n in the −X direction shown in FIG. At this time, the center b of the position adjusting collar A26 is located at a distance n from the axis a of the rotating shaft 21 in the -X direction shown in FIG. 5G, and the center c of the position adjusting collar B25 is the axis of the rotating shaft 21. It is located at a distance n + n from the lead a in the −X direction shown in FIG.
At this time, the position adjustment collar B26 is moved 180 ° to the right or left shown in FIG. (H) from the time when the axis a of the rotating shaft 21 and the center d of the rotating wheel 24 shown in FIG. It is a figure of the rotated position.
(D) FIG. 6D is a time when the center d of the rotating wheel 24 rotates from the axis a of the rotating shaft 21 at a distance n + n in the X direction shown in FIG. At this time, the center b of the position adjusting collar A26 has moved a distance n from the axis a of the rotating shaft 21 in the X direction shown in FIG. 5G, and the center c of the position adjusting collar A25 is the axis a of the rotating shaft 21. To a distance n + n in the X direction shown in FIG.
At this time, the position adjustment collar B25 is turned 180 ° to the right or left shown in FIG. (H) from the time when the axis a of the rotary shaft 21 and the center d of the rotary wheel 24 shown in FIG. It is a figure of the rotated position.
(C) The wheel eccentricity mechanism that uses a groove-fitting constant velocity joint, the position adjustment collar B25 and the position adjustment collar A26 as described above By adjusting the rotation with the adjusting lever A, the rotation center position of the rotary wheel 24 is adjusted in the range of X, -X, Y, -Y in the range of the distance from zero to n + n. This is a mechanism that can arbitrarily change the eccentric position of the center d of the rotary wheel 24.

The perspective view of the disassembled state of the groove fitting constant velocity joint of the present invention The perspective view of the assembly state of the groove fitting constant velocity joint of this invention Explanation of rotation transmission status of grooved constant velocity joint Virtual diagram for explanation when the drive and driven axis spacing changes Comparison diagram of groove fitting constant velocity joint mechanism of the present invention and conventional propeller shaft mechanism Rotating wheel eccentric mechanism using groove fitting constant velocity joint

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Drive side apparatus 2 Drive shaft 3 The board | plate which has the rod-shaped protrusion directly connected to the front-end | tip of the drive shaft 2 The rod-shaped protrusion 5 of the front-end | tip of a drive shaft The groove | channel 6 of the slide plate which the protrusion 4 of a front-end of a drive shaft fits and slides 7 Slide plate groove 8 on which driven shaft tip projection 8 is fitted and slid 8 Rod-like projection 9 on driven shaft tip Plate having rod-like projection directly connected to the tip of driven shaft 10
10 Driven shaft
11 Driven device
21 Rotation axis
22 Rotating shaft plate
23 Slide ring
24 rotating wheel
25 Position adjustment color B
26 Position adjustment color A
27 Adjustment lever A
28 Adjustment lever B
IC Axis of driving shaft UC Axis of driven shaft SPC Center point R of slide plate 6 Virtual circle P of locus drawn by center point SPC when slide plate 6 revolves Propeller shaft mechanism diagram a Axis of rotating shaft 21 b Center of position adjusting collar 26 c Center of position adjusting collar 25 d Center of rotating wheel 24
n Eccentric distance of the center of the hole relative to the center position of the position adjustment collar 26 and position adjustment collar 25

Claims (1)

Square rod-shaped projections are provided at the ends of the rotating shafts on the driving side and driven side in the alignment direction, and concave grooves are provided on each of the front and back surfaces of one middle plate so that they are perpendicular to each other. The distance between the drive and driven shaft centers is indeterminate in the direction perpendicular to the shaft during rotation by sandwiching the middle plate and transmitting the rotation so that the projection of each drive shaft slides into each recess of the middle plate. Constant-velocity joint with groove-fitting connection, which transmits constant rotational power even if a change occurs.

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