KR830001107B1 - reducer - Google Patents

Abstract

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Description

reducer

1 is a cross-sectional view of the first embodiment of the present invention.

FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1, with the sprocket removed from the first embodiment and the bolts securing it from the first embodiment for clarity.

3 is a perspective view of the supporting convex of the first embodiment.

4 is a perspective view of the pinion of the first embodiment.

FIG. 5 is a cross-sectional view showing the second, third, and fourth embodiments in which the head of the support convex is deformed corresponding to FIG.

6 is a sectional view of a fifth embodiment of the present invention.

7 is a cross-sectional view of a sixth embodiment of the present invention.

The present invention relates to a speed reducer. More specifically, a first outer tooth fixed to an input side, a plurality of second outer teeth engaged with the first outer tooth, and the rotational motion of the second outer tooth are converted into their own rotational motions. Plural crank pins connected to a second outer gear, pinions each having a plurality of pin holes arranged to have a circumferentially spaced interval, and an outer tooth formed on an outer circumference thereof, and an eccentricity of the pinion by the rotation of the crank pin. A planetary differential gear type gear reducer having a crank pin inserted into a pin hole for generating an orbital motion, and an inner tooth hub surrounding the outer tooth of the pinion and engaged with the outer tooth.

A speed reducer having the above structure is known, for example, as disclosed in Japanese Patent Publication No. 25398/64.

Such reducers are used where large speed reductions must be made. However, the speed reducer disclosed in Japanese Patent Laid-Open No. 25398/64 does not satisfy the requirement to reduce and transmit a very large output torque because the speed of the speed reducer is large in certain fields such as the endless track vehicle field, and consequently the weight is large. There is a drawback to not doing it.

In particular, the above-mentioned speed reducer is supported by one end of the crank pin like a cantilever (hereinafter referred to as cantilever type) and its output torque amount is limited according to the strength of the crank pin.

If the diameter of the crank pin is increased to increase the output torque, the size of the bearing portion of the crank pin must be increased, and consequently, the appearance of the reducer must also be increased.

In addition, in the reduction gear disclosed in Japanese Patent Publication No. 25398/64, the drive shaft must be supported so as to be rotatable by the reduction gear case, and since the case surrounds the hub with internal teeth, the thickness of the case and the distance between the case and the hub are increased. There is another drawback that the appearance of the reducer is large because it follows essentially.

The primary object of the present invention is to eliminate the above disadvantages and to provide a reducer that produces a large output with a small appearance and weight.

The present invention relates to one or more pinions having one or more through holes formed at intervals between adjacent pinholes, and one or more columnar portions formed thereon loosely inserted into the pinion through holes and integrally formed with the columnar portions. And a support block for supporting both ends of the crankpin to rotate, and one or more bearings installed between the support block and the hub to allow relative rotational movement of the support block and the hub. Achieved by a reducer.

According to the present invention, the columnar portion of the support block is loosely inserted into the through hole formed in the pinion so that both ends formed integrally with the columnar portion of the support block support both ends of the crank pin (hereinafter referred to as non-spinning) and The overall rigidity of the support block, which is formed at both ends, is significantly increased, and both ends of the crankpin are supported by both ends integrally formed in the support block having large rigidity, so that distortion of the crankpin can be minimized.

In other words, if the critical distortions of the crankpins are the same, the output torque from the speed reducer of the present invention is several times larger than that from the conventional speed reducer having a cantilevered crankpin.

Due to the stabilization of the crankpin supported by the non-formality and the reduction of the distortion thereof, a bearing of a smaller size than the bearing in the conventional speed reducer can be used, thus reducing the appearance of the speed reducer. On the contrary, if the bearing is as large as the bearing in the conventional speed reducer, the life of the bearing becomes longer than the bearing life of the cantilevered crank pin.

In addition, the stabilization of the crank pin and its distortion reduction increase the engagement effect between the pinion's outer tooth and the hub's inner tooth, thereby facilitating the transfer of larger output torque.

In the embodiment of the present invention, the support block is composed of two parts, that is, the body part and the single plate, and the two parts are firmly fixed when assembling the reducer. With this structure, the work of assembling the reducer is much improved and the appearance of the reducer is minimized. If the single plate is not formed separately and is formed as a single body having only the body portion of the support block, the size of the pinion must be larger than the size required to insert the non-assembled support block in order to assemble the support block.

In the present invention, the support block has a specially designed structure. More specifically, the support block in this embodiment includes a primary portion extending circumferentially and a secondary portion extending radially inward at the primary portion. Accordingly, the stress in the radial direction due to torque generation in the speed reducer and the radial stress due to the external load connected to the speed reducer are effectively supported by the radially extending secondary portion. Torsional stresses resulting from torque generation by the reducer are also effectively supported by the circumferentially extending primary part.

In an embodiment of the present invention, the pinion has a plurality of through-holes formed therein and connected to each other such that its inner shaft end forms a star shape extending radially inwardly from the center, and the support block also has a plurality of columnar portions. And its ends are connected to each other so that a star shape is formed extending radially inwardly. Because of the specially designed structure of the support block, the support block has a greater hardness against the load exerted in the radial direction than the support block which does not conform to the present structure.

As shown in the embodiment of the present invention, it is suitable for a bearing to be provided between the surface of the support block and the inner surface of the hub to allow relative rotation of the support block and the hub. As a result, there is no need for a casing that surrounds the hub, which was indispensable in a conventional reducer, and no support block that must enclose the hub. Therefore, the risk of the speed reducer becomes smaller than that of the conventional apparatus.

In this case, to reduce the length of the reducer, one bearing is installed between the outer surface of the body of the support block and the inner surface of the hub and another bearing is placed between the outer surface of the single plate and the inner surface of the hub. It is suitable to install. By this structure, the size of the two bearings can be equal.

If the smaller diameter pins are equidistantly installed on the inner surface of the hub to form a pin gear as shown in the present invention, the eccentric distance of the crank pins can be minimized, so that the distance between the center of rotation of the crank pin and the center of rotation of the pinion can be minimized. It can be shortened. Thus, the appearance of the reducer is smaller than the conventional reducer in which the involute gear is used.

In addition, the engagement effect between the inner tooth of the hub and the outer tooth of the pinion can be improved and the allowable gap between the through-hole in the pinion and the peripheral wall of the columnar portion in the support block can be reduced.

As shown in the embodiments of the present invention, it is preferable that two or more pinions are disposed in parallel in the hub to simultaneously engage the internal teeth in the hub. By this structure, the fluctuation of the torque transmitted to the crank pin is reduced so that the torque is transmitted smoothly through the pinion.

Some embodiments of the present invention will now be described in detail with reference to the drawings.

Referring to FIG. 1 showing the first embodiment of the present invention used for a hydraulic motor speed reducer having a speed reducer for operating a crawler vehicle, the conventional hydraulic power frame 1 of the crawler vehicle is fixed to the frame. It has the prime mover 3, and the rotation of the hydraulic prime mover 3 is decelerated by the reducer 5. As shown in FIG.

The output shaft 11 of the hydraulic motor 3 is also used as the rotation input side of the speed reducer according to the present invention and is supported to be rotatable to the casing 13 via a pair of bearings 15, 16.

The casing 13 of the hydraulic motor 3 constitutes the support block of the reducer according to the present invention, and thus will be considered as a support block hereinafter.

The body portion of the support block 13 is composed of a disc portion 17 and a star portion 19 protruding from the disc portion, as shown in FIGS. 1 and 3. The rear side of the disc portion 17 has a recess 17a formed to abut on the body portion of the hydraulic motor 3 (FIG. 1). The star-shaped portion 19 has three columnar portions 21 which are equidistantly arranged along the circumference and each of which has a head 21b extending radially from the head 21a extending circumferentially. The base 21b extends inward to the center of the columnar portion and is connected to each other. The original surface of the plate portion 17 has a predetermined constant depth and has a bearing insertion hole 17b formed between adjacent columnar portions 21. The surface of the disc portion 17 also has thereon a screw hole 17c used to fix the support block 13 to the frame 1 of the crawler vehicle using bolts.

In addition, the center of the star portion 19 has a central through-hole 19a, through which the rotation input shaft 11 is inserted. As shown in FIG. 1, the pin holes 21c and 21d (FIG. 3) form a single plate 25, which is a part of the support block 13, by the pins 23 and 23 '. It is formed in the head 21a of the columnar portion 21 to be fixed to the 21. The size of the pins 23, 23 'is determined so that the pins can withstand the shear stress caused by the load.

Although the two pins 23 and 23 'are used in the embodiment of Figs. 1 and 3, if necessary, the number or diameter of the pins is extended because the head 21a, on which the pins can be arranged, extends circumferentially. You can also increase it.

A screw hole 21e is formed in the columnar portion at the inner radial position of the pinholes 21c and 21d so that the single plate 25 can be fixed to the columnar portion 21 of the support block 13 by the bolt 24. do.

Referring to FIG. 1, the unit plate 25 is formed through the pinholes 25a and 25b and through holes coinciding with the pinholes 21c and 21d of the columnar portion 21 (FIG. 3). A through hole 25c formed thereon in accordance with (21e) to insert the bolt therethrough, and a bearing insertion hole (25d) formed thereon in accordance with the bearing insertion hole (17b) formed on the disc (17). . The conventional roller bearings 27 and 29 are inserted into the bearing insertion holes 17b and 25d so that the crank pin 31 is rotatably supported between the roller bearings 27 and 29. The crank pin 31 has two crank portions 31a and 31c eccentrically arranged with respect to the rotational axis A _CD so that two pinions 33 are inserted onto the crank portions 31a and 31c.

Referring to FIG. 4, the pinion 33 has a tooth-shaped outer tooth 33a formed of an equidistant curve from the pericycloidic curve on the outer circumferential surface.

The pinion 33 also has a pinhole 31b which abuts the crank portion 31a or 31c (FIG. 1) of the crank pin 31 (FIG. 1) via the bearing 35 (FIG. 1). have. The pinion 33 has a star-shaped groove 33c extending in an equidistant radial direction and slightly larger than the star portion 19 (FIG. 3) of the support block 13 (FIG. 3).

Referring again to FIG. 1, the ball bearings 36a, 36b are formed by the disc portion (3) in the support block 13 so that the hub 37 is rotatably supported by the bearings 36a, 36b. It is inserted into the outer surface of 17) and the outer surface of the single plate 25 in the support block 13. The hub 37 is used to drive the drive sprocket 7 of the crawler vehicle. The hub 37 has pins 39 of small diameter and fixed at an equidistant distance to the inner surface thereof so that the pin gears are formed, the number of the pins 39 being around the pinion 33. It is slightly larger than the number of the outer teeth 33a (FIG. 2, FIG. 4) formed in the. Instead of fixing the pins 39, the pins may be rotatably provided in recesses (not shown) formed on the inner surface of the hub 39. As shown in FIG. In this case, it is suitable that the outer race side of the bearings 36a and 36b (FIG. 1) is used to prevent the lateral movement of the pin 39.

The star-shaped groove 33c of the pinion 33 is loosely inserted onto the star-shaped portion 19 constituted by the columnar portion 21 of the support block 13 (FIGS. 1 and 3). You can find out. Therefore, referring to FIG. 1, when the crank pin 31 rotates, the center axis of the crank pins 31a and 31c eccentrically rotates around the rotation axis A _CD of the crank pin 31, and FIG. As shown, the outer tooth 33a meshes with a pin gear formed on the hub 37. Between the center A and the position where the pinhole 33b (FIG. 4) in the pinion 33 is arranged, that is, the arrangement position of the bearing insertion hole 17b (FIG. 3) in the support block 13; If the distance is represented by the radius R ₁ (figure 2) and the distance between the center A and the outermost part of the columnar part of the support block is represented by R ₂ (figure 2), the ratio of R ₁ to R ₂ , That is, R ₁ / R ₂ is suitably selected from the ranges 1 / 1.15 and 1 / 1.55.

If the ratio is smaller than the above-mentioned range, the durability against the radial load due to the generation of the internal load and torque generated by the radially extending base 21b of the columnar portion of the support block 13 can be increased. There will be no.

On the contrary, if the ratio is larger than the above range, the thickness of the pinion 33 between the periphery of the pinion 33 and the star groove 33c is too small to support the stress on the pinion 33. As a result, the strength of the pinion 33 may be poor.

When the diameter of the portion with the smallest diameter in the star portion 19 in the support block 13 (FIG. 2) is denoted by R ₃ , the ratio R ₁ / R ₃ is 1 / 0.267 and 1 / 0.433. It is appropriate to be chosen from the range.

If the ratio is smaller than this range, the thickness of the base in the star portion 19 formed in the support block 13 is too small to be effectively connected. On the other hand, if the ratio exceeds this range, the thickness of the portion around the pinhole 33b formed in the pinion 33 becomes too small to give the pinion 33 sufficient strength.

When the circumferential portion of the head 21a of the columnar portion 21 formed on the support block 13 is represented by L, and the shortest distance between the walls of adjacent pinholes is represented by S, the ratio S / L is 1 It is appropriate to be in the range /0.75 and 1 / 1.30. If the ratio is smaller than this range, the length of the head 21a may be too short to withstand the stresses caused by the torsional load. On the contrary, if the ratio exceeds this range, the strength of the pinion may decrease. It may be.

This means that although the pinion 33 has a through hole having a length equal to the length L of the head 21a in the support block 13, if the ratio exceeds the above range, This is because the length of the through hole extending circumferentially from the pinion 33 becomes too long.

When the narrowest width of the base 21b is denoted by W, the ratio of the shortest distance S and its narrowest width W, i.e., S / W, is selected in the range 1 / 0.40 and 1 / 0.73. If the ratio is smaller than this range, the width of the base 21b becomes too narrow for each of the durability against the radial load. On the other hand, if the ratio exceeds this range, the distance between the pinhole 33b and the star groove 33c in the pinion 33 becomes too short to support the external force.

The portion having the narrowest width W in the base 21b is generally located on or near the line connecting the centers of the bearing insertion holes 17b (FIG. 3) located on both sides of the base 21b. Note that

Referring to FIG. 2, the head 21a of the support block 13 is depicted with a bow with respect to the center A of the support block 13 and the base 21b is the center of the bearing insertion hole 17b. It is suitable that the head 21a and the base 21b are combined into one body because the head 21a and the base 21b are combined in the shape of a bow. This is because it can be minimized.

In another embodiment shown in FIG. 5, the head of the columnar portion 21 of the support block 13 is shaped like a triangle, as shown by reference numeral 21a ', or as a rectangle or as reference numeral 21a ". It may be elliptical, as indicated by the number 21a ". Note that the columnar portion 21 is T-shaped.

In this case, the star-shaped groove 33c formed in the pinion 33 has a shape corresponding to the star-shaped portion 16 formed by the columnar portion 21 in the support block 13, and the size of the portion is It is good to be chosen within the above range.

In another embodiment of the present invention, the support block 13 consists of three columnar portions 21b extending radially from its center portion and a circular portion 21a "connected to the outermost portion of the columnar portion. The parts shown in FIG. 6 are the same as those shown in FIG. 2 except for the involute tooth formed on the inner surface of the hub 37, and therefore the same parts are marked with the same reference numerals of FIG. The explanation is omitted here.

Referring again to FIG. 1, the right edge of the rotation input side 11 is provided with an angle warp, and the first outer tooth 41 is completely fixed thereto.

Similarly, the front end portion of the crank pin 31 has a second outer tooth 43 which has a square leg and is engaged with the first outer tooth 41 and has more teeth than the first outer tooth 41. The lid 47 is secured to the hub 37 by bolts 45 so that the lid is positioned outside of the gears 41 and 43. In addition, the oil seal 49 is disposed outside the bearing 36a rotatably supporting the hub 37 to prevent the lubricant from leaking out of the reducer.

The rotation of the output shaft of the hydraulic motor, that is, the rotational input shaft of the reducer, is fixed to the rotational input shaft 11 while the rotational speed is reduced in accordance with the ratio of the dimensions between the first and second external teeth 43 and 41. It is transmitted to the second outer tooth through 41.

When the second outer tooth 43 is rotated, the crank portion 31a of the crank pin 31, which is rotatably supported at the support block 13, generates a rotational movement, and as a result of the rotational movement thereof, its pinhole. The pinion 33 is eccentrically rotated so that 33b is in contact with the crank portion 31a via the bearing 35.

By the eccentric rotation of the pinion 33, the outer tooth 33a (FIG. 2) formed on the periphery of the pinion 33 meshes with the pin 39 of the pin gear (not shown) formed in the hub 37. Thus, the hub 37 is rotated at a reduced rotational speed. As a result, the drive device of the crawler vehicle is driven by the sprocket 7 attached to the hub 37. According to the first embodiment of the speed reducer shown in FIG. 1, FIG. 2, FIG. 3, and FIG. 4, the present invention is described in Japanese Patent Publication No. 25398/64 when the gear ratio and the outer diameter of the apparatus are the same. It is possible to generate 10 times the torque than the conventional apparatus.

In the above-described embodiments, the reducer having three crank pins has a star-shaped support block composed of three pillars and a pinion having a star-shaped groove 33c according to the shape of the support block. The invention is also adaptable to reducers with three or more crank pins.

If there are three or more crank pins, the column heads can be arranged in two positions between adjacent crank pins instead of the column heads at each position between adjacent crank pins.

In the embodiment described above, the support block 13 is also used as a casing of the hydraulic motor 3. However, the present invention can also be applied to a speed reducer arranged separately from the motor. In this case, the support block 13 is separated from the hydraulic prime mover 13. Instead of the hydraulic motor used in the above embodiment, an electric motor or an air motor may be used.

In the embodiment described above, the output torque is taken from the hub 37. However, the hub 37 of the reducer according to the present invention may be made stationary and the output may be taken from a support block coaxially arranged in the input shaft. An example is shown in FIG. 7, where parts like those shown in the first embodiment in FIGS. 1, 2, 3, and 4 are denoted by the same reference numerals and detailed descriptions thereof. The description is omitted here and only the differences from the first embodiment are shown below.

The hub 37 is firmly fixed to the casing of the hydraulic motor 3 by bolts 46. Further, in this embodiment, the output shaft 11 of the hydraulic motor 3 is used as the rotational input shaft of the reducer.

The length of the input shaft 11 is made as short as possible so that the end face of the shaft does not pass through the support block 13 and the first outer tooth 41 faces the hydraulic motor 3.

As in the first embodiment, the support block 13 is composed of a star-shaped portion 19 and a single plate 25 including three columnar portions connected with the disc portion 17. However, their arrangement is opposite to that of the first embodiment. In other words, the single plate 25 faces the first outer tooth 41.

The crank pin 31 having the second outer tooth 43 is supported by the beam means by the bearings 27 and 29 provided on the support block 13, the shape of the columnar portion of the support block in the first embodiment. same.

The right end of the support block 13 has a threaded portion 13a to which the drive gear (not shown) which transmits the output and which the output is transmitted can be fixed in a spiral.

The bearings 36a and 36b are fixed between the outer periphery of the support block 13 and the inner surface of the hub 37 to allow the support block 13 to rotate relative to the stationary hub 37. Thus, the rotational movement of the rotation input shaft 11 generated by the hydraulic motor 3 is transmitted to the second outer tooth 13 through the first outer tooth 31 while the speed is decreased, so that the crank part in the crank pin 31. The rotational movement of 31a is caused to occur. As a result, the pinion 33 is eccentrically rotated, and the toothed outer tooth 33a consisting of an equidistant curve from the pericycloid curve is engaged with the pin gear formed on the inner shaft of the hub 37. Since the hub 37 is stationary, the support block is rotated in a reduced state and output torque is generated in the drive gear.

Claims (1)

A plurality of cranks fixed to an input shaft, a plurality of second external gears engaged with the first external gear, and a plurality of cranks which are connected to the second external gear and receive rotational motions of the second external gears to rotate by themselves Pin, a plurality of pin holes are formed at intervals in the circumferential direction, the outer pin is formed in the outer periphery, the crank pin is inserted into the pin hole so that the rotational movement of the crank pin is the eccentric revolution of the pinion Wherein the pinion has a plurality of through-holes formed between adjacent pinholes, the speed reducer comprising a hub which includes an inner tooth engaging and engaging the outer tooth of the pinion. The columnar portion is formed by forming a plurality of columnar portions extending in the circumferential direction and the second portion radially extending radially from the first portion. At the same time, the pinion is loosely inserted into the through hole of the pinion, and both ends thereof are supported between the support block freely supporting the crank pin and the support block and the hub so that relative rotation between the support block and the hub is achieved. Reducer comprising at least one bearing to be allowed.

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