JPS5865349A - Differential gear speed reducer - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gear system, and more particularly to a gear system that provides a large gear ratio in a single stage.

Conventionally, the use of gearing to vary the angular velocity by a desired ratio has been known in the past. In most cases, the typical gear shape determines the tooth geometry, but this tooth geometry does not provide an advantage due to the harsh gear shifting or gear ratio. Thus, for example, a gear ratio of 60 to 1 was most often achieved with several intermediate range gear stages that, when increased, would provide the desired ratio. The unnecessary increase in gears has been the subject of extensive research since each gear stage carries both loss efficiency and manufacturing and maintenance costs. Recently, gearing systems with an odd number of teeth have been utilized to provide large gear ratios in just one stage. A disadvantage of these gearing systems is that the ratio increments that can be achieved are determined by a multiple factor associated with the number of gear teeth. Thus, although said gearing with odd teeth can certainly be used if a specific gear ratio is incorporated into the configuration of gear stages, it does not result in an advantageous modification where different gear ratios are desired. In order to achieve current market economy, it is necessary to find a technology that allows large gear shifts to be achieved at low cost and without the necessary constraints in machining.

Accordingly, an object of the present invention is to provide a gear device that can provide any desired gear ratio by means of a pitch difference.

Another object of the invention is to provide a gear reduction device having two gears of unequal diameter configured with different pitches to achieve a desired gear differential.

Yet another object of the present invention is to provide a gear reduction device that achieves gear ratios by conveniently making a variety of pitch selections.

Briefly, these and other purposes can be achieved by having a selected nine circular pitch between the driving members and matable with either a rack or a large diameter gear with driven members engaging the teeth. This is achieved within the invention by providing a gear. The pitch difference between the driving and driven members of the rack or gear provides the required gear ratio, with which any suitable ratio can be achieved. In another form, this gearing principle can be used advantageously in solar or planetary gearing. The driving and driven members may be rollers or teeth engaging magnetically coupled magnets.

Due to the engagement of the rollers and the teeth or due to the coercive forces created between the permanent magnets, a relatively friction-free engagement is achieved which results in high efficiency and reduces or eliminates wear.

- Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 1, the principles of the invention are best illustrated by the rack and pinion assembly designated generally at 10. The rack and pinion assembly 10 includes a pinion gear 11 mounted in a bearing 12 supported by an axle 13 extending perpendicularly from a sliding engagement in a groove 15. Grooves 15 are formed within laterally aligned channel portions 16 located in a parallel array with respect to rack assembly 2o. This #1115 allows the shaft 13 to move along this groove, but vertical movement is restricted. The rack assembly is longitudinally movable. Rack assembly 20
are equally spaced along its longitudinal axis and gear 1
1 and a plurality of orthogonally oriented struts 21 arranged to engage the periphery of the device. Each post 21 supports on its outer surface a roller bearing 22 or similar friction-reducing outer shield, which reduces most of the contact friction. The gear 11 is provided around its periphery with a plurality of cutouts 31, each separated by a tooth 32. The notched portion 31 is formed to receive the roller 22 so that the protruding teeth 32 extend between the rollers 22 and enter the gap between the roller bearings. To further ensure good rolling contact, each recess between the teeth 32 is generally formed into an arc connecting the a straight surfaces making up one tooth. The teeth 32 or the recesses or arcs between the teeth are spaced apart at a predetermined circular pitch shown as pitch arc P. Pitch arc P for the center-to-center distance between the struts 21, indicated as distance T
The dimensions of set the gear ratio achieved with this device.

More specifically, if the pitch dimension P is equal to the center-to-center distance T over the desired gear ratio, no deceleration of motion will occur. Also, shaft 13 moves to the right or left without transmitting any motion to rack assembly 20. By the way, if the distance between the centers of the supports 22 is made equal to T + whistle (P is equal to T), when the shaft 13 moves 7 inches to the right, the rack 20 moves 67 inches to the left.
inches, thus giving a relative motion ratio of 100:/. Conversely, if the distance between the centers of the columns 22 is set to T-1, the movement of the shaft 13 to the right causes the rank 20 to move 19 degrees to the right. The movement is caused by the camming action of the rollers 22 along the walls of the groove or cutout 31. Thus, the difference between the advancement of rack assembly 20 and the advancement of shaft 13 within groove 15 will be equal to the reciprocal of the difference between circular pitch P and center-to-center distance T.

The above principle can be advantageously used in the planetary gear system shown in FIGS. 2 and 3. More specifically, as shown in these figures, one input shaft 51 is fixed at one end to a driven plate 52 having a substantially triangular planar shape, and joined to this driven plate 52 at the center.

Wire plate 52 has three circular holes, shown as holes 53, near each apex, each hole 53ti receiving one end of post 54. The other end of the column 54 is similarly received in a plurality of other holes 55 near the apex of the triangular plate 56. Plates 52 and 56 are substantially equal in planar shape and have a central axis 57 extending outwardly from the center of plate 56Fi. Thus, the input shaft 51 of one of the structures formed by the plates 52, 56 and the struts 54 supports the assembly in rotation;
Each post 54 supports a gear 60. This gear 60 is the first
It is similar to the gear 11 in the figure, with a plurality of circumferential cutouts separated by teeth.

More Details 1c Fi% Each gear 60 has a plurality of circular edge recesses or cutouts 61 formed around its periphery between adjacent teeth 62. As previously described, a one-piece assembly is formed mounting the gear 60 with the shaft 51.

In this manner, the gear 6o is free to rotate around each post, thus allowing the floor wheel 1 around the axis 12 in FIG.
It will be similar to the movement in step 1. According to the above principle, the planetary gear assembly rotates within a gear structure consisting of spaced circular plates 71, 72 supporting a plurality of rollers 75. Rollers 75 are disposed along the periphery of plates 71 , 72 in alignment to engage the teeth of gear 60 . In this way, by appropriately selecting the pitch difference between the tooth spacing of gear 60 and the circumferential spacing of roller 75, a large gear ratio can be obtained. The resulting gear ratio is determined by the pitch difference rather than the number of teeth. In this format, board 71.7
2 constitutes an output section 76 that produces gear reduction.

These principles can be implemented in differential assemblies such as those shown in FIGS. 9 and S. More particularly, as shown in these figures, the differential, designated by the numeral 100, includes an input shaft 101 extending inside a ring gear cage 102 of generally cylindrical section. Within the ring gear cage 102, the shaft 1o11 is splined with a sun gear 103 cut with conventional gear teeth and meshing with a plurality of planetary gears 104. The planetary gear 104 is added to a shaft 105, which has a number of circular end plates lO"6.
．． It is rotatably supported by a planetary gear support made of 107. Each of the shafts 105 splined to gears 104 also includes gears 108 formed in accordance with the present invention.
．． 109 and is keyed or spline connected. Gears 108 , 109 engage a plurality of peripheral rollers 110 located proximate the peripheral wall of differential cage 102 . Additionally, each of the gears 108 , 109 has a peripheral cutout 115 of a different pitch than the pitch of the peripheral roller 110 . In this way, the pitch of the differential can be used advantageously according to the principles described above.

The structure shown in FIGS. 9 and 9 can alternatively be implemented according to the description in FIG. For clarity, the same numbers as shown in Figures 1 and 5 are used to represent 1. Additional features advantageously used in FIG. 6 will now be described. More specifically, in FIG.
03 is spline-coupled in common with an inner roller cage 125 having a circular planar shape, and the roller cage 125 is provided with a plurality of rollers 130 around the roller cage 125. The radial dimensions of the arrangement of the rollers 3o are such that they contact the gears 108, 109. Further, the circumferential spacing of the row 2130 is
．． Since it is chosen to be equal to the circular pitch of 109, an inversion will occur.

Thus, the rotation of differential cage 102 is in this case pitch,
The rotation of shaft 101 is opposed by a ratio proportional to the difference.

In all the embodiments described above, the circular cutout and the relative geometry of the roller surface provide a single point contact ensuring high efficiency. In each case, the point contact maintains the required gear ratio and
Thus, an efficiency equivalent to that of a conventional gear train is achieved.

Unlike conventional gear trains, these efficiencies are typically achieved with a single stage rather than multiple stages to achieve high ratios.

The pitch differential gearing principle described above is made more efficient by using a magnetic coupling. More specifically, as shown in FIGS. 7 and 8, the planetary gear support 201
It is rotationally driven by a shaft 202 inside the beam/gugya assembly 203 . The planetary gear support 201 has a plurality of radial dipoles 2 magnetized north and south, as shown in FIG.
A plurality of gears 205 formed as cylindrical portions extending around the shaft 202 are rotatably supported equally spaced apart from the center of the shaft 202 in the radial direction. Similarly to this,
The googya assembly 203 includes an inwardly directed peripheral geared ring 211, each tooth 212 of which is magnetized as a magnetic dipole.

The magnetic polarities of the gear teeth 212 and the planetary gear teeth 206 are repellently aligned, thus ensuring a contactless gearing system. Due to this repulsion, the gear 203 is moved by an amount corresponding to the pitch difference. Ring gear tooth 212
and the circular pitch of the teeth around gear 205 are unequal, giving the differential gear system described above. In this form, the required gear ratio provides some axial absorption of magnetic repulsion to minimize contact between the two wheels.

Obtained in such a configuration as considered by potency.

This similar magnetic effect can be exploited to advantage by the explanation in FIG. In this description, the planetary gear 205 has a semicircular magnetic insert 226 around its periphery rather than having a circumferentially extending magnetic dipole. The ring gear 211 likewise has a semicircular magnetic insert 232, the magnetic alignment of which inserts 226, 232 is north-south' so as to be mutually absorbing. The circumferential spacing of the magnetic inserts 226 and the spacing of the inserts 2320 are such as to obtain a differential tooth, wheel arrangement. With this implementation, Day! An effective gearing system is obtained with the desired characteristics of no pre-mechanical contact, which is particularly practical for driving sophisticated devices such as drives or similar devices.

To generate higher torque, the magnetic device is
can be utilized as shown in the figure, in this case fixed track 233
is provided. The spacing between magnets 226 and 233 is equal, and the spacing of magnets 232 is different than the spacing of magnets 2260. Yet another arrangement is shown in FIGS. 1/1 and 1U, which is similar to FIG. 6 except that the gears are replaced by magnets. Note that the same reference numerals refer to the same parts.

In each of the embodiments described above, a circular pitch of the gears is used to obtain a large gear ratio.

If positive contact is to be made, the two surfaces of unequal radius ensure point contact which is further improved by the features of the rollers. In this way, the same efficiency as that obtained in a chain drive or gear train is obtained, with the added advantage that gear ratios that would normally be achieved through multiple gears can be achieved in just one gear. As this point of contact is displaced around the circumference of the roller, the roller mounting assembly will advance on the surface of the cutout without the need for opposing restraining forces. Thus, as each tooth advances into the mutual gap between the rollers, only one side of the tooth remains in contact. The other side of the teeth or the cutouts between the teeth are not in any contact. Therefore, for this gearing to advance over the rollers, a necessary opposite translational movement occurs in the roller assembly to achieve the desired gearing. This opposite translation occurs even if the roller structure is completely flat, before which no features are obtained. In magnetically coupled gear systems, the repulsive or attractive forces of the magnets provide a driving force that drives the gears while maintaining alignment and interlocking engagement of the poles.

It will be apparent that many modifications and changes may be made to the above description without departing from the spirit of the invention. Accordingly, the scope of the invention should be determined solely by the claims appended hereto.

[Brief explanation of the drawing]

1 is a front view of a rack-and-binion device illustrating the invention in detail; FIG. 1 is a partially cut-away front view of a planetary gearing incorporating the principles of FIG. 1; FIG. 3 is a front view taken along the lines of FIG. 3
-3; Figure 4 is a front view of another planetary gear system in combination with gears; Figure S is a cross-sectional side view along line 5-5 of Figure 4; Figure 6 is a planetary A front view of still another embodiment of the gear device; FIG. 7 shows a magnetic coupling gear device according to the present invention;
8 is a detailed view of a magnetic gearing useful in the structure of FIG. 7; FIG. 9 is a view of yet another embodiment of a magnetically engaged gearing; FIG. Line 10-10 in Figure 7
11 is a front view of a magnetically coupled planetary gear arrangement according to the invention; and FIG. 12 is a sectional view along line /2-/2 of FIG. There is no summer in the V-directed nonorchid) FIG/L2 261--5 1n to b-6 F/? F/LIO m-〃 hσ-12 Procedure Amendment (Method) % Formula % 1. Indication of the incident 1982 Patent I#I No. 132937 2. Title of the invention Differential gear reduction device 3. Make the amendment Relationship with the person’s case Applicant’s name: Leo G. Nikoladze 4, agent

Claims (1)

[Claims] (1) A gear-shaped circular member having a peripheral edge with a plurality of drive elements spaced apart at predetermined intervals around the periphery and rotating by being operatively connected to the drive elements; an elongated engagement member having a plurality of driven elements operatively connected thereto, the driven element being in continuous engagement with the driving element during rotation of the circular member; A device that changes the forward speed of the target.