Novel involute small-tooth-difference speed reducer

Abstract

The utility model provides a novel involute small-tooth-difference speed reducer, which relates to the technical field of transmission devices and is characterized in that three eccentric wheels are arranged along the axial direction of an eccentric cam shaft, and an outer gear disc A, an outer gear disc B and an outer gear disc C are respectively sleeved on the corresponding eccentric wheels and are uniformly distributed at an angle of 120 degrees in the eccentric direction; an involute inner gear ring is machined on the inner wall of the shell and connected with outer teeth of the outer gear disc A, the outer gear disc B and the outer gear disc C in a meshed mode to form a small-tooth-difference meshing pair. The novel involute small-tooth-difference speed reducer has the beneficial effects that the novel involute small-tooth-difference speed reducer is mainly meshed with the inner gear through three groups of outer gear discs which are distributed at 120 degrees, so that the load is uniformly distributed, the bearing capacity is improved, and three supporting meshing points are designed, so that the effects of dispersing the force, reducing the deformation of a transmission system and greatly improving the torsional rigidity are achieved; in addition, the speed reducer is provided with the two crossed roller bearings, overturning load force can be borne at the same time, deformation caused by overturning bending moment is reduced, and the overall overturning rigidity is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to transmission device technical field especially a new speed reducer of little tooth difference of involute. BACKGROUND

[0002] The involute little tooth difference speed reducer is a kind of high efficiency, compact transmission device, is widely used in industrial machinery, automation equipment, robot etc. Its core feature lies in using involute gear and little tooth difference principle to realize high reduction ratio and accurate transmission. Involute little tooth difference speed reducer is mainly composed of the following components:

[0003] Involute gear: adopt involute tooth profile, ensure the stability and high precision of transmission.

[0004] Little tooth difference mechanism: realize high reduction ratio through the tooth number difference (usually 1~4 teeth) of inner and outer gears.

[0005] Output shaft: the power after reduction is transmitted to load end.

[0006] Housing: support and protect internal gear assembly.

[0007] Its working principle is to convert the high-speed rotation of input shaft into low-speed high-torque movement of output shaft through the little tooth difference meshing of inner and outer gears. Because the tooth number difference is small, the reduction ratio can reach dozens or even hundreds of times.

[0008] But the current involute little tooth difference new speed reducer has the shortcomings of uneven load, poor bearing capacity and low overall overturning rigidity, and urgently needs to be improved. UTILITY MODEL CONTENTS

[0009] The utility model overcomes the shortcomings in the prior art and provides an involute little tooth difference new speed reducer, which has the effects of high bearing capacity, high rigidity and high overturning rigidity.

[0010] To solve the above technical problems, the utility model is implemented by the following technical solutions:

[0011] An involute little tooth difference new speed reducer, comprising:

[0012] An eccentric camshaft and a housing, wherein:

[0013] Three eccentric wheels are arranged along the axial direction of the eccentric camshaft, and the eccentric amounts of the three eccentric wheels are the same;

[0014] The outer gear disc A, the outer gear disc B and the outer gear disc C are respectively sleeved on the corresponding eccentric wheels, the eccentric directions of the three are uniformly distributed at 120°, and the three are rotationally connected with the eccentric wheels through the needle rollers;

[0015] The inner wall of the shell is processed with a involute inner gear ring, and is connected with the outer teeth of the outer gear plate A, the outer gear plate B and the outer gear plate C to form a few-tooth-difference meshing pair;

[0016] The rear cover and the output flange are rotatably connected with the eccentric cam shaft through a deep groove ball bearing, and are also rotatably connected with the shell through a cross roller bearing;

[0017] The bolt passes through the mounting holes of the outer gear plate A, the outer gear plate B and the outer gear plate C from the rear cover, and is fixed on the output flange, and a bushing is sleeved on the bolt at the corresponding mounting hole.

[0018] Further, it also comprises:

[0019] The pressing plate A is connected with the output flange;

[0020] The pressing plate B is connected with the rear cover;

[0021] The pressing plate A and the pressing plate B are respectively connected with the corresponding cross roller bearings, so that the cross roller bearing (9) is stable.

[0022] Further, the pressing plate A and the outer gear plate A, the outer gear plate A and the outer gear plate B, the outer gear plate B and the outer gear plate C, and the outer gear plate C and the pressing plate B are all provided with friction plates.

[0023] Further, it also comprises:

[0024] The first oil seal is arranged between the output flange and the rear cover and the eccentric cam shaft;

[0025] The second oil seal is arranged between the output flange and the rear cover and the shell.

[0026] Compared with the prior art, the progressive line few-tooth-difference novel speed reducer has the beneficial effects that:

[0027] The progressive line few-tooth-difference novel speed reducer mainly comprises three outer gear plates which are distributed at 120° and are meshed with an inner gear, so that the load is uniformly distributed and the bearing capacity is improved, three supporting meshing points are designed to disperse the force, the deformation of the transmission system is reduced, and the torsional rigidity can be greatly improved; in addition, the speed reducer is provided with two cross roller bearings, which can simultaneously bear the overturning load force, reduce the deformation caused by the overturning bending moment, and improve the overall overturning rigidity. BRIEF DESCRIPTION OF DRAWINGS

[0028] The accompanying drawings are used to provide a further understanding of the present application, together with the embodiments of the present application, to explain the present application, and do not constitute a limitation on the present application, and in the drawings:

[0029] Figure 1 It is the overall structure of the progressive line few-tooth-difference novel speed reducer Figure 1;

[0030] Figure 2 It is the overall structure of the involute few-tooth-difference new reducer Figure 2 ;

[0031] Figure 3 It is the sectional view of the involute few-tooth-difference new reducer;

[0032] Figure 4 It is the structural schematic view of eccentric camshaft;

[0033] Figure 5 It is the explosion view of the involute few-tooth-difference new reducer.

[0034] In the figure:

[0035] 1, eccentric camshaft; 101, eccentric wheel; 2, shell; 3, outer gear plate A; 4, outer gear plate B; 5, outer gear plate C; 6, needle roller; 7, back cover; 8, output flange; 9, cross roller bearing; 10, bolt; 11, bushing; 12, deep groove ball bearing; 13, pressing plate A; 14, pressing plate B; 15, friction plate; 16, first oil seal; 17, second oil seal. DETAILED DESCRIPTION

[0036] The preferred embodiments of the utility model are described below in conjunction with the drawings, and it should be understood that the preferred embodiments described herein are only used to illustrate and explain the utility model, and are not used to limit the utility model.

[0037] As Figures 1 to 5 shown, the utility model claims a kind of involute few-tooth-difference new reducer, comprising: eccentric camshaft 1 and shell 2, eccentric camshaft 1 is located in center position, as power input component, shell 2 is located in the outermost side, for fixed on external pedestal;Wherein:

[0038] Three eccentric wheels 101 are provided along the axial direction of eccentric camshaft 1, and the eccentric amount of three eccentric wheels 101 is same;And outer gear plate A 3, outer gear plate B 4, outer gear plate C 5 are respectively set on corresponding eccentric wheel 101, and the eccentric direction of three is 120 ° evenly distributed, and rotationally connected with eccentric wheel 101 by needle roller 6;Gradual line inner ring gear is processed in the inner wall of shell 2, and is connected with the outer tooth of outer gear plate A 3, outer gear plate B 4, outer gear plate C 5 Meshing connection constitutes few-tooth-difference meshing pair.

[0039] The bolt 10 penetrates the mounting holes of the outer gear plate A3, the outer gear plate B4 and the outer gear plate C5 from the rear cover 7, and is fixedly connected to the output flange 8; the bushing 11 is sleeved on the bolt 10 at the corresponding mounting hole, and the bushing 11 is interposed between the bolt 10 and the mounting hole, not only to resist the movement wear between the bolt 10 and the mounting hole, but also to help balance the stress distribution under the eccentric load condition, so that the overall operation is stable.

[0040] Therefore, the rotation of the eccentric camshaft 1 drives the outer gear plate A3, the outer gear plate B4 and the outer gear plate C5 to move, and when the outer gear plate A3, the outer gear plate B4 and the outer gear plate C5 are engaged with the involute inner gear ring on the inner wall of the housing 2, the relative sliding movement is generated due to the difference in the number of teeth, the engagement point continuously migrates along the involute tooth profile, and finally drives the output flange 8 to rotate, thereby realizing high-efficiency deceleration and high-torque output.

[0041] The rear cover 7 and the output flange 8 are rotatably assembled on the eccentric camshaft 1, and specifically, the rear cover 7 and the output flange 8 are rotatably connected to the eccentric camshaft 1 through the installation of the deep groove ball bearing 12; the rear cover 7 and the output flange 8 are rotatably connected to the housing 2 through the cross roller bearing 9. The deep groove ball bearing has the characteristics of large carrying capacity, high running precision and small friction coefficient, and the cross roller bearing 9 has the advantages of high precision and strong anti-overturning capability.

[0042] Further comprising:

[0043] The pressing plate A13 is connected to the output flange 8, and the pressing plate B14 is connected to the rear cover 7.

[0044] The pressing plate A13 and the pressing plate B14 are respectively connected to the corresponding cross roller bearing 9, so as to stabilize the cross roller bearing 9 and enhance the stability of the fixation of the cross roller bearing 9.

[0045] Friction plates 15 are arranged between the pressing plate A13 and the outer gear plate A3, between the outer gear plate A3 and the outer gear plate B4, between the outer gear plate B4 and the outer gear plate C5, and between the outer gear plate C5 and the pressing plate B14, and the arrangement of the friction plates 15 has the effects of load balancing, vibration suppression and noise control.

[0046] The involute few-tooth difference speed reducer further comprises a first oil seal 16 arranged between the output flange 8 and the rear cover 7 and the eccentric camshaft 1, and a second oil seal 17 arranged between the output flange 8 and the rear cover 7 and the housing 2, and the arrangement of the first oil seal 16 and the second oil seal 17 not only prevents the lubricating oil inside the speed reducer from leaking in the axial direction, but also blocks the external pollutants from polluting the inside of the speed reducer.

[0047] The new type of involute few-tooth-difference reducer mainly passes through three groups of outer gear plates (outer gear plate A3, outer gear plate B4 and outer gear plate C5) distributed at 120° and meshing with the inner gear to evenly distribute the load, improve the bearing capacity, design three supporting meshing points to achieve the dispersion of force, reduce the deformation of the transmission system, and greatly improve the torsional stiffness; in addition, the reducer is provided with two crossed roller bearings which can simultaneously bear the overturning load force, reduce the deformation caused by the overturning bending moment, and improve the overall overturning stiffness.

[0048] Finally, it should be noted that: the above is only the preferred embodiment of the present application, and is not intended to limit the present application, although the present application is described in detail with reference to the embodiments, for those skilled in the art, the technical solutions recorded in the foregoing embodiments can be modified, or some technical features can be replaced, but any modification, equivalent replacement, improvement, etc. within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A new type of reducer with involute and small tooth difference, characterized in that, The eccentric camshaft (1) and the shell (2) are included, wherein: Three eccentric wheels (101) are arranged along the axis of the eccentric camshaft (1), and the eccentric amounts of the three eccentric wheels (101) are the same; The outer gear plate A (3), the outer gear plate B (4), and the outer gear plate C (5) are respectively sleeved on the corresponding eccentric wheels (101), and the eccentric directions of the three are uniformly distributed at 120°, and the rotation connection is realized through the needle roller (6) and the eccentric wheel (101); The inner wall of the shell (2) is processed with an involute inner ring gear, and is in meshing connection with the outer teeth of the outer gear plate A (3), the outer gear plate B (4), and the outer gear plate C (5) to form a few-tooth-difference meshing pair; The rear cover (7) and the output flange (8) are rotationally connected with the eccentric camshaft (1) through the installation of the deep groove ball bearing (12), and are also rotationally connected with the shell (2) through the cross roller bearing (9); The bolt (10) penetrates the mounting hole of the outer gear plate A (3), the outer gear plate B (4), and the outer gear plate C (5) from the rear cover (7), and is fixedly connected on the output flange (8); the bushing (11) is sleeved on the corresponding mounting hole of the bolt (10). Further comprising:

2. The new type of involute low tooth difference speed reducer according to claim 1, characterized in that, The pressing plate A (13) is connected on the output flange (8); The pressing plate B (14) is connected on the rear cover (7); The pressing plate A (13) and the pressing plate B (14) are respectively connected with the corresponding cross roller bearing (9), so that the cross roller bearing (9) is stable. The friction plate (15) is arranged between the pressing plate A (13) and the outer gear plate A (3), between the outer gear plate A (3) and the outer gear plate B (4), between the outer gear plate B (4) and the outer gear plate C (5), and between the outer gear plate C (5) and the pressing plate B (14).

3. The new type of involute low tooth difference speed reducer according to claim 2, characterized in that, Further comprising:

4. The new type of involute low tooth difference speed reducer according to claim 1, characterized in that, The first oil seal (16) is arranged between the output flange (8) and the rear cover (7) and the eccentric camshaft (1); The second oil seal (17) is arranged between the output flange (8) and the rear cover (7) and the shell (2). ​

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