JPH0756324B2 - Conical rolling equal tooth bevel gear device and processing method of the same device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention is applied to a planetary speed reducer, a ring cone speed reducer, a coronet, a cycloid speed reducer, or a bevel gear mechanism or a mysterious planetary gear mechanism currently in use. Instead, it is stronger than rolling conduction such as ring cone reducer, resistance does not increase much even if preload is applied, it can operate with zero backlash, and conduction efficiency is close to rolling conduction. The present invention relates to a gear device for a speed machine.

(Prior Art) Generally, the motion of a friction wheel that makes rolling contact is quiet, but strong conduction exceeding the friction force cannot be performed. Gears must be used for strong conduction.

Regardless of the tooth profile of the gear, sliding friction occurs on the tooth surface, heat generation and noise generation are inevitable, and the precision improvement of the involute tooth type cutter has reached the limit with current technology, and it is essential for gears. The backlash is usually 0.2 to 0.5 mm, and the diameter of the special grade cylindrical spur gear of the Japan Gear Manufacturers Association is 100 mm and the backlash is 80 to 200 microns. Further, vibrations and noises due to machining and assembling errors occur remarkably every time the reduction ratio is increased, and now they are becoming a major social problem in various fields.

(Problems to be solved by the invention) As automation, unmanned operation, robotization, etc. in various fields have progressed in recent years, reduction gears have been used in ultra-precision machining machines,
There are many problems in vibration, noise or durability, oil leakage resistance, etc. as well as the accuracy. However, as described above, it is not practical for a friction wheel, and noise and heat generation due to backlash are inevitable with ordinary gears.

Japanese Patent Application No. 2867 (November 1, 1991) filed by the inventor first
The electric differential thrust generator of No. 65 also requires a double-sided bevel gear mechanism, and even if both bevel gears are close to crown gears, the spherical involute whose base cone is conical is flat. Can not. On the other hand, even in the case of a eccentric surface gear close to a crown gear, it is an involute tooth crest, and the one having a pitch cone line or curve that is not parallel to the pitch cone line of the regular surface gear in the tooth cross section in the tooth trace direction is used as the eccentric surface. As it is defined as a gear, its tooth profile is also a curved involute tooth profile, but it becomes a pseudo involute to cut teeth with a straight blade cutter, inevitably requires a lap on the lap base, and the rolling contact is the pitch cone part. Therefore, since slippage occurs on all other surfaces, it was inevitable that a pitch error would occur due to abrasion during lap. Moreover, since the involute tooth profile faces mesh with each other by convex shapes, there is a drawback that the pressure receiving capability thereof is low due to the stress of Hertz. Therefore, an object of the present invention is to provide a double-sided bevel gear with bevel gears, which eliminates the above-mentioned various drawbacks.

(Means for Solving the Problems) In order to achieve the above object, the present invention provides an intersection of a plane perpendicular to the rolling pitch line of each facing bevel gear in a double-sided differential bevel gear device and each conical center line. Consider a spur gear with a back cone distance AP, BP shown in Fig. 6 as the radius of the pitch circle and develop an involute of the same circle pitch on this pitch circle. Considering the tooth profile, this is regarded as a corresponding spur gear, and the involute tooth profile obtained from this spur gear can be developed approximately on a plane. Therefore, it is not possible to create a spherical involute with a linear blade cutter, but it becomes an Octoid tooth profile created with a linear blade cutter based on the involute tooth profile that can be developed approximately on this plane, and there is a slight difference from the spherical involute. I could get a tooth profile. Therefore, even if the backlash can be minimized, the danger of heat generation is inevitable. Therefore, in order to obtain a transmission performance comparable to or better than the performance of the involute tooth profile of the equivalent spur gear, thrust needles or thrust roller bearings on the rolling surfaces with the N ₁ , N ₂ conical surfaces and N ₃ , N ₄ conical surfaces. The same arbitrary cylindrical roller or the same needle roller is formed, and the shape of the cross-section of the roller perpendicular to the axis is set to a load state like a combination angular contact ball bearing or deep groove ball bearing, and this groove is circular arc or githic arc. The radius of the shape. By selecting this shape, the backlash is brought close to zero by the high preload and self-centering function, and the accuracy of the cutter shape is improved to 10 to several tens of times that of the conventional one by adopting a cylinder or needle roller as a true arc. In addition, high load transmission, which is rigid and minimizes deformation (hysteresis) due to the elasticity of the material at the time of reversal, was able to obtain high performance that is close to rolling transmission.

Embodiment An embodiment of the present invention will be described below with reference to the drawings. First Embodiment
In the figure, (1) is an input motor, (2) is an input eccentric tilt shaft, (3) is a double-sided input bevel gear with a U-shaped cross section, (4) is a fixed bevel gear, (5) is an output conical shaft, (6) is a feed screw nut, and (7) is an output feed screw shaft, which shows an embodiment of a conical rolling equal tooth thickness bevel gear device according to the present invention to a mechatronic cylinder. In this case, if (6) and (7) are integrated, an ordinary output rotary shaft is formed, and the embodiment thereof is a specific example as a general speed reducer shown in FIG. In the drawing, (8) is a rolling transmission cylindrical roller or a needle roller, and the roller has the same action as a thrust needle bearing or a thrust roller bearing, and as shown in FIG. 11, each slip occurs during rotation. Since the surface can be hardened and superfinished, a stable transmission effect can be obtained with the same effect as the slide bearing. Further, FIG. 3 shows the pitch cones of the bevel gears by the triangles O ₁ AP and O ₂ BP, and the pitch cones of the output bevel gears by O ₃ CQ and O ₄ DQ. It is drawing which shows a rolling motion on the basis of Q point. When the input tilted eccentric shaft (2) shown in FIG. 1 makes a half rotation, the input double-sided bevel gear (3) moves as shown by the broken line in FIG.
It has perfect rolling conduction so that points A, B and C, D respectively match. Therefore, the fixed gear side and the output bevel gear side are opposite to each other and have similar shapes. Therefore, in detail on one side, (4) and (5) are fixed or the output bevel gear and (3) are shown in FIG. Input double-sided bevel gear, shaded area (T) in the figure
Is the tooth width. The rolling power is inferior to that of a ring-cone type friction wheel, and the transmission force is inferior, so if a bevel gear is made with this surface as the reference, it will surely mesh. In order to develop the tooth profile of this bevel gear on a plane, there is an approximation method of the Tredgold method in the conventional shaft reversal type bevel gear, so when developed to the axial rotation type (both main and slave shafts rotate in the same direction) of this bevel gear, The corresponding number of teeth of the spur gear is, as described in claim (1), The same goes for the opposite side Got As a result, the involute tooth profile of the equivalent spur gear can be developed approximately on a plane. Moreover, the pressure angle, which was conventionally set to 20 ° to 25 ° due to work such as dislocation, increases the equivalent diameter of the equivalent spur gear.
Since it can be reduced to less than °, the rolling bearing load inside the input double-sided bevel gear due to the reaction force can be reduced.

Further, FIG. 5 is a drawing in which a cylindrical roller is installed on the rolling surface, and FIG. 6 also depicts these cylindrical rollers or needle rollers. Next, as shown in FIG. 7, by forming the input double-sided bevel gear (3) in a U shape, it is possible to generate a flexural deformation of an arbitrary ΔB by applying a preload particularly in the axial direction. This amount of flexural deformation can be made to correspond to the absorption allowance for machining errors during machining or assembly, or the axial reaction force (TS) during strong transmission (Fig. 5-1). There is no other method than zero rolling preload by using a cylindrical roller or a needle-shaped cylindrical roller to set the backlash to zero. In reality, it can be arbitrarily set to about 2.5 to 250 microns. The U-shaped disc portion is guaranteed to have sufficiently strong rigidity in the rotational direction, so that zero backlash can be surely achieved and hysteresis of the material can be reduced. In this way, each tooth profile can be developed in a plane, so the roller arrangement under the same conditions as the tooth profile of the corresponding spur gear is
It could be installed arbitrarily as shown in the figure.

Next, FIG. 8 is an explanatory view of claim 3 and shows that the tooth groove of the input double-sided bevel gear (3) is being processed. Cutter axis (6
6) and the machining shaft (61) are synchronized with the gears (67) and (62) according to the combination of the gears so that the cutter spindle (64) is synchronized with the left and right reciprocating synchronism, and the cutter spindle (64) is machined to the work vehicle (3).
It is processed by reciprocating according to the tooth trace of
Reciprocates a dimension (L) slightly longer than the tooth width.

Further, FIG. 9 is a more detailed one, and in particular, it is processed in a state in which the groove for the cylindrical roller is preloaded, and only the (N ₂ ) surface is arbitrarily preloaded by ΔB in FIG. Create with wheel (63). At this time, the cutter wheel (6) is also engaged under the same (N ₁ ) and (N ₂ ) meshing conditions as in the assembled state.
If the groove is processed in 3), it will be reproduced as it is at the time of assembly as it is as the assembly dimension. While machining one groove, the cutter shaft (66) and the machining shaft (61) are completely synchronized and rotate left and right, and the cutter wheel (63) is reciprocally machined according to the tooth groove (L).
When the index pin (71) is used to sequentially machine the tooth groove, the (N ₂ ) surface is completed when the index pin (71) makes one revolution, and then the (N ₂ ) surface is completed. Complete the input double-sided bevel gear by following the same procedure for the N ₄ ) plane. Similarly, the (N ₃ ) face gear is also a device that can be machined. The indexing pin (7
Naturally, 1) etc. can be replaced by an automatic indexing machine (NC machine).

(Operation and Effect) Since the present invention is configured as described above, it exerts the excellent operation and effect as described below.

An electric differential thrust generator according to Japanese Patent Application No. 1-286765 of Nov. 1, 2001, which is being applied by the above-mentioned inventor, even if the involute tooth profile, the cylindrical roller or the needle roller with the pressure angle of 14.5 degrees is applied. The same reduction ratio and torque ratio can be obtained.

For example, in Fig. 4, if the number of involute tooth profiles or cylindrical rollers is N ₁ = 59N ₂ = 60N ₃ = 61N ₄ = 60 To get If N ₁ = 29N ₂ = 30N ₃ = 29N ₄ = 29 To get The friction coefficient due to sliding is μ = 0.1 in the involute tooth profile, but in the case of a cylindrical roller, μ = 0.001 to 0.01, which is close to that of the bearing roller, is obtained, so complete reversal is possible.

Further, in FIG. 1, if the feed screw nut (6), the output feed screw shaft (7) is replaced with the input side and the input eccentric tilt shaft (2) is replaced with the output side, ultra-high speed acceleration can be achieved, and heat generation is a mystery of the past. The load is smaller than that of the gear mechanism and the deflection surface gear mechanism, and the higher the load conduction becomes. In the case of this cylindrical roller, the surface pressure is 10th
As shown in the figure, the internal contact is reduced to 1/3 of the external contact. The life of the tooth surface is inversely proportional to the 9th power of the Hertz stress. For example, if the Hertz stress is 1/3, the life is extended 20,000 times. If the surface pressure becomes low, oil lubrication from the oil tank, which was conventionally required, can be performed only with the same grease as the bearing. This is an epoch-making invention that makes it possible to use a powerful reducer in a vacuum such as space if powder grease is used.

Further, the effect of 30% or more over the conventional planetary gear type multi-stage type has a national energy saving effect. Furthermore, by making the batch lash to zero, the robot equipment etc. becomes larger and has a larger capacity, and the system is improved and the rolling resistance coefficient due to quenching and super finishing is reduced by 10 to several tens of times, and vibration and noise are significantly reduced. In addition, it is an invention that exerts immeasurable effects such as further miniaturization, ultra-precision, and drastic energy saving.

[Brief description of drawings]

FIG. 1 is a front view showing a cross section of an embodiment of a mechatronics cylinder of a conical rolling equal-thickness gear device of the present invention, FIG. 2 is a front view of a cross section as a speed reducer, and FIG. 3 is a conical rolling surface of each gear. Fig. 4 shows the rolling motion of Fig. 4, Fig. 4 shows the method of drawing the back cone of the rolling surface explained in Fig. 3, and Fig. 4-1 shows an example in which an equi-thick tooth profile is created on the rolling surface. FIG. 5 shows an example in which a cylindrical roller is installed on the rolling surface and meshes as shown in (A) and (B) of FIG. FIG. 5A is a detailed sectional view of FIGS. 5 (X) and (Y), and FIG. 6 shows a tooth profile of the back cone developed by providing a tooth profile on the rolling surface. FIG. 7 is a sectional view of the input double-sided bevel gear, showing the deformation amount ΔB due to an arbitrary preload. FIG. 8 shows a synchronous generating gear cutting device according to claim 3. FIG. 9 shows machining in the preload state in FIG. Fig. 10 shows a comparison of the contact pressure between the internally contacting tooth profile with an arcuate tooth profile and the conventional externally contacting tooth profile. FIG. 11 shows a thrust needle and a roller bearing. 1 ... Input motor, 2 ... Input tilted eccentric shaft, 3 ... Input double-sided bevel gear, 4 ... Fixed bevel gear, 5 ... Output conical shaft,
6 ... Feed screw nut, 7 ... Output feed screw shaft, 8 ...
Cylindrical roller, needle roller, O ₁ AP, O ₂ BP, O ₃ CQ, O ₄ DQ …… Pitch cone of each gear, T …… Tooth width, TS …… Reaction force due to dislocation tooth profile, 61 …… Processing axis , 62 …… Machining shaft gear, 63 …… Cutter wheel, 64 …… Cutter spindle, 65 …… Cutter shaft guide, 66 …… Cutter shaft gear, 70 …… Preload arm, 71 …… Indexing pin, L …… Machining reciprocating dimension, N ₁ , N ₂ , N ₃ , N ₄ …… Number of teeth of cylindrical roller tooth profile

Claims (3)

[Claims] 1. A power transmission device comprising a fixed bevel gear having one or a plurality of tooth differences and an input double-sided bevel gear, wherein a rear surface portion of the input double-sided bevel gear has a flexible axial section. In the above-mentioned gears, the angle formed by each conical shape and the plane perpendicular to the rolling surface in each of the above gears is a fixed bevel gear δ ₁ , and the angles of the double-sided bevel gears are δ ₂ , δ _{3 of the} output bevel gears, respectively. Let it be δ _4, and the number of teeth is N ₁ , N ₂ , N ₃ , and
N ₄ , and the equivalent gear pitch circle radii whose radius is the distance to the intersection of the fixed gear, the surface perpendicular to the rolling surface on the input side of the double-sided bevel gear and the gear cone center line, and RVO _{1 and} RVO ₂ , respectively.
If the equivalent number of teeth is NV ₁ and NV ₂ , If the equivalent number of teeth on the output side rolling surface of the input double-sided bevel gear is NV ₃ and NV ₄ , The equi-thickness tooth is formed in the tooth width direction with a cutter of the tooth profile on any one of the rolling surfaces facing the involute obtained by the equivalent spur gear represented by A conical rolling equal-thickness bevel gear device characterized by being created and transferred. 2. The center of rotation of a conical roller or a needle-shaped roller instead of the involute tooth profile is made to match or come close to the rolling conical surface of each conical rolling bevel gear, and the roller is loosely fitted or fitted to any one surface facing each other. Fitting and holding, a groove that meshes with the roller is machined on the mating surface, and an arbitrary preload is applied in the axial direction of the input double-sided bevel gear with U-shaped cross section, and the backlash is made zero in the state where it is elastically deformed to the specified extent. The conical rolling equal tooth thick bevel gear device according to claim 1, wherein an arc tooth profile is formed. 3. A U-shaped input double-sided bevel gear is elastically deformed in the axial direction, and a cutter wheel having the same locus as the rolling locus of a cylindrical roller or a needle roller is used in the axial direction of the roller. The reciprocating motion cutting process and the synchronous rolling reciprocating motion over a distance equal to or more than the entire length of the roller to create and transfer a groove for engagement in a mating rolling conical surface along a locus. A method for processing a conical rolling equal-thickness bevel gear device.