KR101576279B1

KR101576279B1 - Back lash zeroise controling gearing system for helical gear

Info

Publication number: KR101576279B1
Application number: KR1020150055928A
Authority: KR
Inventors: 김명수
Original assignee: 김명수
Priority date: 2014-04-21
Filing date: 2015-04-21
Publication date: 2015-12-11
Also published as: KR20150121674A

Abstract

A backlash zeroing apparatus for an input / output type helical gear is disclosed. A pair of helical gears formed by a combination of a single pinion gear and a single ring gear divided into a drive gear and a slip gear; Wherein the pinion gear includes a pinion gear engaged with a ring gear having a different number of teeth, the pinion gear having an engagement of a slip gear to reduce a gap between gears of the ring gear with respect to the pinion gear, The number of teeth of the drive gear is one or more larger than the number of teeth of the drive gear and the axial support for supporting the slip gear reduces the gap generated at the point where the pinion gear and the drive gear meet, .

Description

BACK LASH ZEROISE CONTROLLING GEARING SYSTEM FOR HELICAL GEAR BACKGROUND OF THE INVENTION 1. Field of the Invention [0001]

The present invention relates to a backlash zeroing apparatus for an input / output type helical gear, and more particularly, to a backlash zeroing apparatus for an input / output type helical gear for reducing backlash generated when an output side ring gear meshes with an input side pinion gear.

In combination with gear engagement, a back lash is placed in order to smoothly rotate a pair of gears smoothly. Backlash is a gap between teeth that is required to rotate a pair of rotating gears, and is a gap between teeth when a pair of gears is engaged. The backlash varies depending on the type and characteristics of the gear. Normally, the backlash is designed according to the backlash calculation numerical table so that it is designed according to the design standard. Fig. 1 is a JIS class 0 and class 5 backlash calculation numerical table of a helical gear. Referring to Fig. 1, there is shown a method of obtaining backlash of a JIS class 0 helical gear.

The backlash generated from a pair of driven and driven gear bites reduces the accuracy by varying the theoretical output value and the starting output value depending on the direction of the gear, based on the arc of the gear.

For example, in repeated operations in robots and precision machines, a precision speed reducer is used when the power of the servomotor is insufficient, and helical gears and bevel gears are used to change the power direction. These meshing driven gears control backlash . In practice, ISO and DIN specify the amount of backlash based on the gear grade. In addition, backlash elimination is required even for a precision robot, a machine tool, a servo decelerator, and a split index, and various methods of backlash removal are applied, but the effect is inferior to the cost.

The backlash of the gear is formed by a circumferential direction, a normal direction, an angle, a radius, an axial clearance (not shown), etc. according to the backlash reference in FIG. Calculation of the bite strength, tolerance and output error from backlash can be predicted to some extent.

On the other hand, in order to reduce an output error caused by backlash, gears including a gear to adjust the backlash to small or separate structures have been proposed, but the backlash has not been sufficiently removed. As a method of adjusting the backlash of the gear to a small extent, there is a method of adjusting the center distance of the gear. This can be applied to a helical gear or the like. However, since the center distance of the gear is made small to adjust the clearance in the radial direction to reduce the backlash, there is a problem that the structure for adjusting the center distance becomes complicated.

Fig. 3 is a view showing a construction of a scissors gear for reducing backlash. In this method, a backlash is forcibly pulled by pulling the gear of a counter gear with the force of a spring or the like in a gear in which circumferential backlash is divided into two parts. However, since the gears are bitten when they are pushed in, the lubrication needs to be paid attention so that the oil film is not broken. This method is not suitable for gears with large tooth sliding, and there is a risk of abrupt tooth friction when the oil film is broken at a large sliding surface.

The backlash of the gear has so far been assumed to occur for the potential and the smooth gear rotation. However, it has been difficult to satisfy the cost and the reliability, and the proposal for the backlash removal disclosed in domestic or overseas The use of various materials is required and the processing cost is high.

It is expected that the design of the gear with precise backlash control will enable high precision position control of the total robot position accuracy within the range of about 0.3mm to 0.01mm due to improvement of the robot joint precision. In the CNC control machine tool, It is possible to reduce the use of the encoder, and the cost of operating the machine tool system can be drastically reduced.

Patent Document 1. Korean Patent Application No. 10-2005-0062101

Patent Document 2. Korean Patent Application No. 10-2012-0080568

Patent Document 3. Korean Patent Application No. 10-2011-0107126

Patent Document 4: Korean Patent Application No. 10-2011-0045290

SUMMARY OF THE INVENTION It is an object of the present invention to provide a pinion gear of a helical gear and an input / output type helical gear that induces a drive gear of a ring gear to have a close- To provide a backlash zeroing apparatus.

Another object of the present invention is to provide a backlash zeroing apparatus for an input / output single-stage helical gear which reliably removes backlash generated from a helical gear that rotates in engagement with a pinion gear in a simple and low-cost manner.

It is still another object of the present invention to provide a backlash zeroing apparatus for an input / output single-stage helical gear that removes backlash of a ring gear from one shaft.

According to the present invention, there is provided a backlash zeroing apparatus for an input / output type helical gear which is divided into a single input side for generating a rotational force and a single output side for receiving a rotational force from the input side, A pair of helical gears composed of a combination of a single ring gear divided into slip gears; Wherein the pinion gear includes a pinion gear which is engaged with a ring gear having a different number of teeth, the pinion gear having a pinion gear meshing with the ring gear of the slip gear so as to reduce a gear gap of the ring gear with respect to the pinion gear, And an axial support for supporting the slip gear, wherein the axial support comprises: a base having a slide groove formed therein and supporting the shaft; A disk inserted in a shaft passing through the ring gear and supported by the base; A thrust bearing spaced apart from the disk and supporting the shaft at the base; And a resilient member elastically urging the disc between the disc and the thrust bearing to elastically contact the disc, wherein a circumferential surface of the disc is coupled along the slide groove of the disc to restrict axial rotation of the disc, Of the helical gear of the input / output type helical gear.
Further, according to the embodiment of the present invention, the teeth of the slip gear and the drive gear are aligned in the same direction about the axis.

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Further, according to the embodiment of the present invention, the drive gear is engaged with the shaft and is an output side that drives the shaft by the rotational force transmitted from the pinion gear on the input side.

Also, according to an embodiment of the present invention, the axial support of the slip gear comprises: a base structure supporting the shaft; And a thrust bearing which is press-fitted into the base to support and fix the shaft and to support the surface of the slip gear in close contact with the surface of the drive gear.

Further, according to the embodiment of the present invention, the slip gear may include a friction surface composed of a surface subjected to a sliding process or a friction pad, the surface facing the surface of the drive gear.

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Further, according to the embodiment of the present invention, the disk may include a surface on which a surface facing the slip gear is subjected to a threading process, or a friction portion having a friction pad.

According to the embodiment of the present invention, the ring gear is configured such that the tooth surface width of the drive gear is narrower than or equal to the tooth surface width of the slip gear, or the tooth surface width of the slip gear is wider Lt; / RTI >

The backlash zeroing apparatus for an input / output single-phase helical gear according to the present invention has the effect of guiding gear engagement to approach zero backlash by narrowing the gap between the pinion gear and the ring gear formed of the helical gear.

Further, the backlash generated in the helical gear which rotates in engagement with the pinion gear is reliably removed.

In addition, since backlash can be reduced through an existing structure-dependent or structure-dependent manner that reduces the backlash of the helical gear, it prevents malfunction and malfunction of the device for backlash removal.

Fig. 1 is a backlash calculation numerical reference chart of gears. Fig.
2 is a backlash reference diagram of a gear.
Fig. 3 is a view of a scissors gear with zero backlash.
FIG. 4 is a schematic view showing an input / output type single helical gear engaged state according to an embodiment of the present invention; FIG.
5 is an exploded perspective view showing a backlash zeroing apparatus for an input / output type helical gear according to an embodiment of the present invention.
Fig. 6 is an exemplary view of the coupled state of Fig. 5; Fig.
7 is an application example of a backlash elimination joint of an input / output single-stage helical gear according to an embodiment of the present invention.
8 is an exploded perspective view showing a backlash zeroing apparatus for an input / output type helical gear according to another embodiment of the present invention.
Fig. 9 is an exemplary view of the coupling state of Fig. 8; Fig.
10 is an application example of a backlash elimination joint of an input / output single-phase helical gear according to another embodiment of the present invention.
FIG. 11A is a view showing a ring gear having a width t of the drive gear tooth surface and a width t1 of the slip gear tooth surface t> t1, according to an embodiment of the present invention, (B) is an example of a ring gear with t = t1, and (c) is a comparative example of a ring gear with t < t1.
12 is an explanatory diagram relating to backlash elimination gear engagement of an input / output type helical gear according to an embodiment of the present invention;
Fig. 13 is a calculation formula and a calculation table of the 10t-58t tooth square-shaped potential helical gear of Fig. 12;
Fig. 14 is a calculation formula and a calculation table of the 10t-59t tooth orthogonal method potential helical gear of Fig. 12;
Fig. 15 is a calculation formula and a calculation table of the 10t-60t tooth right angle type potential helical gear of Fig. 12;
Fig. 16 is a calculation formula and a calculation table of the 10t-61t tooth angle-wise method helical gear of Fig. 12;
Fig. 17 is a calculation formula and a calculation table of the 10t-62t tooth rectangular-shaped potential helical gear of Fig. 12;
FIG. 18 is a calculation formula and a calculation table of the 10t-63t tooth angle-wise method helical gear of FIG. 12;

Hereinafter, the structure of a backlash zeroing apparatus for an input / output type helical gear according to an embodiment of the present invention will be described with reference to FIGS. 4 to 11. FIG.

4 is a schematic diagram illustrating a pair of helical gear engagement in accordance with an embodiment of the present invention.

4, a backlash zeroing apparatus for an input / output type helical gear according to an embodiment of the present invention includes one pinion gear 200 and one ring gear 100 in a pair of helical gears H, And a single input / output system composed of a coupling structure of FIG.

A ring gear 100 that meshes with the pinion gear 200 may be two corresponding helical gears coupled along the shaft 110.

The ring gear 100 is combined with two corresponding helical gears along a shaft 110 and one is a slip gear 300 that meshes with the pinion gear 200 and rotates about the shaft 110 And the other one is a drive gear D that receives power input from the pinion gear 200 and rotates about the shaft 110 to drive the shaft 110. [ The slip gear 300 and the drive gear D are arranged side by side in the same direction in the same direction as the teeth of the corresponding helical gear. However, when the number of teeth of the drive gear D is different from the number of teeth of the slip gear 300, the position of the gears may be dislocated due to the difference in the number of teeth.

The ring gear 100 is a pair of two helical gears that receive rotation of the pinion gear 200 and interlock with each other, and the respective gears of the ring gear 100 combined with the pair of helical gears share roles. The input side is the pinion gear 200 and the output side is the drive gear D and the pinion gear 200 directly transmits the power to the drive gear D and the drive gear D is powered by the pinion gear 200 The axis 110 is rotated. The slip gear 300 rotates about the shaft 110 by the pinion gear 200 and removes the backlash formed between the pinion gear 200 and the drive gear D during the rotation.

Therefore, the ring gear 100 includes means for reducing the backlash, which is the interval that occurs at the point where the gear meets.

The means for reducing the backlash is a mechanism for reducing the backlash by frictionally rotating along the shaft 110 while facing the drive gear D that rotates about the shaft 110 and cooperates with the shaft 110 in response to rotation input from the pinion gear 200 And a slip gear 300.

5 is an exploded perspective view showing a main part of a backlash zeroing apparatus for a helical gear according to an embodiment of the present invention.

5, specifically, the engagement of the pair of helical gears H engaged along the shaft 110 is transmitted to the pinion gear 200 and the ring gear 100).

The pair of helical gears H are formed in a bite structure in which the number of teeth of the drive gear D and the slip gear 300 constituting the ring gear 100 are different from each other so that they are engaged with the pinion gear 200.

The engaging structure includes a slip gear 300 that changes the engagement of the drive gear D of the ring gear 100 with the pinion gear 200 to reduce the backlash, which is a gap generated at the point where the teeth of the pinion gear meet .

And an axial support portion 400 for supporting the slip gear 300 in the axial direction. The slip gear 300 having the axial support portion 400 is engaged with the drive gear D engaged with the pinion gear 200 by the frictional force during rotation and is pushed in the direction of reducing the backlash during the rotation process.

Here, the pinion gear 200 and the ring gear 100 meshing with each other are helical gears divided into cylindrical gears. The ring gear 100 is divided into a drive gear D and a slip gear 300 .

In general, helical gears are twisted around the wheel and have helical teeth. The helical teeth appear in either the right angle module or the front module, and thrust is applied to the axial direction when a rotational force is applied to the helical teeth. The spiral teeth are inclined obliquely with a sawtooth line. The relative position of the two axes is parallel to the spur gear but the teeth are inclined so that the thrust is applied in the axial direction. The magnitude of the thrust is the tooth inclination of the helical gear . &Lt; / RTI >

When the slip gear 300 is engaged with the driving gear D and the axial supporting portion 400 supporting the slip gear 300 is coupled to the shaft 110, The frictional force is generated and the backlash which is a gap between the drive gear and the pinion gear can be reduced.

The shaft hole of the slip gear 300 that contacts the outer diameter of the shaft 110 to suppress the excessive slip rotation of the slip gear 300 on the shaft 110 and to induce the friction rotation, The friction member 310 of the shaft 110 may be mounted to induce a shaft friction force on the slip gear 300 contacting the outer diameter of the shaft 110. [ However, it is preferable to apply it in consideration of rotational load of the shaft. As the friction member 310, an elastic member, a brake pad-based material, or a surface-treated member having a rough surface may be appropriately processed and applied, though not shown in the drawings.

Reference numerals 110a and 110a denote the 'axis' and the 'key groove' of the pinion gear, respectively. 150 is a hollow formed in the drive gear.

6 is a perspective view showing gear engagement of a backlash zeroing device of a helical gear according to an embodiment of the present invention. 7 is an application example of backlash elimination of a helical gear according to an embodiment of the present invention.

4 to 7, the ring gear 100 includes a slip gear 300 that meshes with the pinion gear 210 as a helical gear and rotates about the shaft 110, a pinion gear 200, And a drive gear (D) that receives power input from the drive shaft (110) and rotates about the shaft (110) and drives the shaft (110).

Here, the slip gear 300 is combined with an axis 110 arranged side by side with the drive gear D to receive and rotate the rotational force transmitted through the pinion gear 200 at the same time as the drive gear D. The drive gear D and the slip gear 300 are coupled to an axis 110, but are divided. The drive gear D is an output side gear that rotates the shaft 110.

The slip gear 300 is a helical gear that rotates along the shaft 110 to eliminate backlash generated at a point where the teeth of the drive gear D engage with the pinion gear 200, The gap between the pinion gear 200 and the drive gear D is reduced by frictional rotation to thereby eliminate the backlash.

The drive gear D is engaged with the key 130 on the shaft 110 and is configured to receive the rotational force from the pinion gear to drive the shaft 110.

The ring gear 100 composed of the drive gear and the slip gear is not shown in the figure, but may be composed of the ring gear 100 in which the number of the slip gears 300 is one or more. The figure shows an example in which one slip gear 300 is combined with one drive gear.

The slip gear 300 may be constituted by a ring gear 100 facing either one surface or both surfaces of the drive gear D. [

7, the pinion gear 200 and the ring gear 100 are helical gears, and the axial thrust force W applied to the shaft 110 during rotation is transmitted to the structure base 500 and the thrust bearings 400a .

The specific structure and operation of the backlash zeroing device of the helical gear according to the embodiment of the present invention will be described with reference to FIGS. 4 to 11. FIG.

7, the ring gear 100 is divided into a drive gear D and a slip gear 300. The ring gear 100 is axially supported by a shaft 110, The slip gear 300 may be installed to support the base 500 in the axial direction to induce the friction rotation of the slip gear 300. The shaft 110 to which the thrust W is applied is supported through the structure base 500 and the thrust bearing 400a.

The axial support of the ring gear 100 including the slip gear 300 is supported by the thrust bearing 400a press-fitted into the base 500. [ The thrust bearing 400a is pushed into the base 500 to support and fix the shaft 110 without any flow and is positioned at a position where the surface of the slip gear 300 is brought into close contact with the surface of the drive gear D

The slip gear 300 which is axially supported by the structure base 500 and the thrust bearing 400a is provided with a frictional force due to a helical gear due to the helical gear characteristic and a slip gear contacting the outer diameter of the shaft 110, The frictional force between the inner surface (including the friction member selectively) contact surface and the friction surface between the drive gear and the surface contact surface of the slip gear is added, and the slip gear 300 reduces the gap generated at the point where the drive gear and the pinion gear meet, You can give. Here, the frictional force between the drive gear D and the surface contact surface of the slip gear 300 may change the frictional force when the friction portion 320 is placed on the slip gear 300.

8 is an exploded perspective view showing a main part of a backlash zeroing apparatus for a helical gear according to an embodiment of the present invention. 9 is a view illustrating an engaged state of a backlash zeroing apparatus for a helical gear according to an embodiment of the present invention. 10 is an application example of backlash elimination of a helical gear according to another embodiment of the present invention.

As shown in FIGS. 8 to 10, the slip gear 300 is frictionally rotated by driving a ring gear 100, which is divided into a drive gear D and a slip gear 300, And the shaft 110 may be installed to be guided in the axial direction on the structure base 500 and guided.

Specifically, the slide groove 510 is formed in the structure base 500 supporting the shaft 110, the disk 410 is assembled along the slide groove 510, and elastic force is applied to the rotation of the slip gear 300 It is a type that induces friction.

The main part includes a structure base 500 for supporting the shaft 110, a disc 410 supported by the base 500 by being inserted in a shaft 110 passing through the ring gear 100, A thrust bearing 400a which is spaced from the disc 410 and supports the shaft 110 to the base 500 and a thrust bearing 400b which is spaced from the thrust bearing 400a by a resilient force to elastically contact the disc 410 with the slip gear 300 between the disc 410 and the thrust bearing 400a Member 430 as shown in FIG. As the elastic member 430, various types of coil springs, leaf springs, and the like can be selectively applied. The figure shows an example of a coil spring.

The disk 410 is coupled to the shaft but is not rotated by the shaft and moves axially along the slide groove 510 of the base 500. The force for applying the pressure to the slip gear 300 is changed according to the elastic force of the elastic member 430, which determines the frictional force acting on the slip gear 300. Therefore, the rotation friction force of the slip gear 300 can be adjusted through the use of the appropriate elastic member 430.

At least two or more stoppers 410a are provided on the circumferential surface of the disk 410 to engage with the slide groove 510 of the base 500 to interlock the axial rotation and induce the axial movement. An elastic force acts on the disk 410 at all times and moves in the elastic force acting direction thereof and is brought into close contact with the surface of the slip gear 300. Thus, when the slip gear 300 rotates, a frictional force corresponding to the elastic force is generated.

The frictional force between the contact surface of the drive gear D and the slip gear 300 and the frictional force between the slip gear 300 and the disk 410 are set such that when the frictional parts 320 and 420 are rotated, Can be varied.

However, it is preferable to adjust the frictional force in consideration of the rotational load of the shaft or the drive gear. Although not shown in the drawing, the friction portion 320 may be formed by selectively processing various structures and materials including a brake pad-based material, a surface processed to have a rough surface, and the like, and may be applied as needed .

The friction portion 320 of the slip gear 300 may be configured to have a knurled surface or a friction pad on a surface facing the surface of the drive gear D. Likewise, in the case of the friction portion 420 of the disk 410, the surface facing the surface of the slip gear 300 can be easily configured with a sliding surface treatment or a friction pad.

It is preferable that the number of teeth T of the drive gear D and the number of teeth T1 of the slip gear 300 constituting the ring gear 100 have a difference of one or more, It is more advantageous to reduce the distance between the pinion gear 200 and the drive gear D at the point where the pinion gear 200 and the drive gear D meet when the number of teeth T1 of the gear is larger than the number of teeth T of the drive gear. In this case, the drive gear and the slip gear are always shifted as shown in the figure.

As described above, the ring gear 100, which is a combination of the drive gear D and the slip gear 300, is engaged with the pinion gear 200 due to the difference in the number of teeth of the gear, The bite itself acts to narrow the gap between the gears.

The slip gear 300 rotates together with the drive gear D along the shaft 110, and when the pinion gear is engaged with the pinion gear, a difference in angular velocity and rotational angle is generated depending on the number of gear teeth, Reduce.

11 (a) is a view showing a ring gear having a width t and a slip gear tooth surface width t1 of t> t1 in a combination of ring gears according to an embodiment of the present invention, (B) is an example of a ring gear with t = t1, and (c) is a comparison example of a ring gear with t < t1.

(a) is an example of the ring gear 100 in which the tooth surface width t of the drive gear D is combined with a width t> t1, which is relatively wider than the tooth surface width t1 of the slip gear 300 .

5B shows an example of the ring gear 100 in which the tooth surface width t of the drive gear D and the tooth surface width t1 of the slip gear 300 are combined to have the same width t = t1.

(c) shows an example of the ring gear 100 in which the tooth surface width t1 of the slip gear 300 is wider than the tooth surface width t of the drive gear D.

Referring to FIG. 11, it can be seen that the tooth surface width or the thickness of the drive gear and the slip gear of the ring gear can be adjusted by selectively adjusting the tooth surface width as required. The difference in the relative tooth widths of the drive gear and the slip gear may induce a change in thrust and frictional force in the engagement of the pinion gear and the ring gear, which are helical gears having a helical tooth profile.

For example, FIG. 11 (c) shows a case in which the tooth width of the slip gear 300 is relatively wider than that of the drive gear. In this case, the friction induction of the slip gear may be more advantageous than the case without.

On the other hand, the single-pinion gear 200 transmits the input power to the ring gear 100, and includes a driving pinion gear for deceleration of the speed reducer, a differential pinion gear for engaging with the side gear of the car to smooth the turning, A pinion gear that transmits the rotational force of the handle to the rack, a pinion gear that transmits the rotational force to the engine in the starting motor, a pinion gear that rotates the upper rotator of the construction machine, a pinion gear that is combined with the planetary gear of the automatic transmission, And may be a gear used as a driving pinion gear.

FIG. 12 is an explanatory view of backlash elimination of a helical gear according to an embodiment of the present invention, and shows a tooth cross section at a right angle to reduce backlash.

12, the number of teeth of the input-side pinion gear 200 is '10T', the number of teeth of the drive gear D engaged with the teeth is 60T, and the number of teeth 63T of the slip gear 300 of the ring gear 100 The drive gear D forms a constant engagement ratio with the pinion gear 200 when the tooth cross-section for reducing the backlash is 58T, 59T, 60T, 61T, 62T and 63T. Here, as a constant biting ratio, the backlash is reduced, and the rotation of the pinion gear 200 is transmitted to the drive gear D to be output.

That is, when the number of teeth of the gear except the gear radius is in a gear ratio of 1/6, which is the pinion gear 10T and the drive gear 60T, one rotation of the pinion gear is transmitted to the drive gear at 1/6 of the rotation amount. The actual engagement ratio of a general helical gear permitting backlash has a value of ± 1/6 due to backlash.

The engagement ratio forms a stable engagement ratio that eliminates backlash such as detail -58T, detail -59T, detail -60T, detail -61T, detail -62T, detail -63T in FIG. The rotating drive gear D and the slip gear 300 rotating in the same direction are arranged such that the gears of the slip gear 300 are located at intervals between the gears forming the backlash, Can be reduced.

12 shows a pair of helical gear engagement states in which the number of teeth of the input side pinion gear is 10T and the number of output side drive gear teeth is 60T and the number of teeth of the slip gear is 63T and the number of teeth of the drive gear D and the slip gear 300 is different The backlash generated in the helical gear engagement can be removed by adjusting the axial distance between the pinion gear 200 and the electric potential by the difference in the number of teeth.

For example, the number of teeth (T) of the drive gear D: the number of teeth T1 of the slip gear 300 is 10T on the input side and the number of teeth on the output side drive gear is 58 to 63T. The number of teeth T and the number of teeth T1 of the slip gear may have a difference of 1 to 5 ranges. Under these conditions, the number of slip gear teeth can be increased proportionally to the number of teeth of the drive gear, based on the number of teeth of the drive gear, such as one at 58T, and five at 63T.

FIGS. 13 to 18 are diagrams for explaining the design of the helical gear for backlash zeroing according to the embodiment of the present invention. In FIG. 13 to FIG. 18, when the number of teeth of the pinion gear is 10T and the number of teeth of the slip gear The number of gear teeth, tooth angle module, reference pressure angle, root clearance ratio, and torsion angle are shown as examples of the formula reflected in the helical gear engagement design divided into 58T, 59T, 60T, 61T, 62T, (FIG. 14), 10T-60T (FIG. 15), 10T-61T (FIG. 16), 10T-62T (FIG. 17), and 10T- And is an example of the calculation table showing this as an example.

According to the above example, values are calculated by substituting the tooth angle module, the reference pressure angle, the root gap ratio, and the twist angle except for the number of teeth of the gear teeth in Table 1 below.

Calculation item Output value Right angle module 2 Reference pressure angle 20 Percentage of root gap 0.35 Twist angle 28

Table 2 shows the results obtained by extracting frontal contact pressure angle, end circle diameter, and bite factor that directly affect backlash.

division Front Bite Pressure Angle (°) Diameter of end circle (mm)
Bite rate Pinion Ring gear Pinion Ring gear 10T-58T 0.0343 26.0886 26.289 139.908 1.185 10T-59T 0.0274 24.3109 26.559 139.908 1.269 10T-60T 0.0212 22.4025 26.651 139.908 1.337 10T-61T 0.0157 20.3250 26.553 139.908 1.391 10T-62T 0.0108 18.0210 26.246 139.909 1.435 10T-63T 0.0066 15.3872 25.702 139.908 1.473

According to the tables of FIGS. 13 to 18 and Table 2, the value of the " end circle diameter " of the output side ring gear including the slip gears varying in the number of teeth of the teeth is '139.908' 139.909 '. It can be seen that a value equal or close to the "diameter of the end circle" of the ring gear results in a stable engagement ratio that eliminates the backlash formed by the gap between the input gear (pinion) and the output gear (drive gear) .

A backlash zeroing device for a helical gear according to the present invention is a device for guiding a backlash of a helical gear so as to have a bite that narrows a gap generated between a pinion gear formed of a helical gear and a tooth of a drive gear, . And since the slip gear for reducing the backlash is integrated into the ring gear, the ring gear can be simply finished with a small processing cost, and the device for backlash elimination is simplified.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is clearly understood that the same is by way of illustration and example only and is not to be taken by way of illustration, .

D: drive gear H: a pair of helical gears
100: ring gear 110: shaft
120: key groove 130: key
200: Pinion gear 300: Slip gear
310: Friction member 320: Friction member
400: Axial support part 400a: Thrust bearing
410: Disk 410a: Stopper
420: friction portion 430: elastic member
500: Base 510: Slide groove

Claims

An input / output type helical gear backlash zeroing apparatus, which is divided into a single input side for generating a rotational force and a single output side for receiving a rotational force from the input side and turning the shaft, comprising: a single pinion gear, A pair of helical gears, Wherein the pinion gear includes a pinion gear which is engaged with a ring gear having a different number of teeth, the pinion gear having a pinion gear meshing with the ring gear of the slip gear so as to reduce a gear gap of the ring gear with respect to the pinion gear, And an axial support for supporting the slip gear, wherein the number of teeth is one or more than the number of teeth of the drive gear,
Wherein the axial supporting portion includes: a structure base having a slide groove formed therein and supporting the shaft; A disk inserted in a shaft passing through the ring gear and supported by the base; A thrust bearing spaced apart from the disk and supporting the shaft at the base; And a resilient member elastically urging the disc between the disc and the thrust bearing to elastically contact the disc, wherein the circumferential surface of the disc is coupled along the slide groove of the disc to restrict axial rotation of the disc, And the at least two stoppers for guiding the stoppers to the at least two stoppers.

The backlash zeroing apparatus of claim 1, wherein the slip gears of the drive gear and the slip gears are aligned in the same direction.

2. The backlash zeroing device of claim 1, wherein the drive gear is engaged with a key on an axis.

2. The bearing of claim 1, wherein the axial support of the slip gear comprises: a base structure for supporting the shaft; And a thrust bearing which is press-fitted into the base to support and fix the shaft, and to support the surface of the slip gear in close contact with the surface of the drive gear.

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2. The backlash zeroing device of an input / output type helical gear according to claim 1, wherein the slip gear includes a friction surface formed by a surface subjected to a threading process or a friction pad facing the surface of the drive gear.

2. The backlash zeroing device of claim 1, wherein the disk comprises a friction surface having a surface subjected to a threading process or a friction pad facing the surface of the slip gear.

The drive gear according to any one of claims 1 to 3, wherein the ring gear is configured such that the tooth surface width of the drive gear is narrower than or equal to the tooth surface width of the slip gear, or the tooth surface width of the slip gear is wider than the tooth surface width of the drive gear Backlit zeroing device of one input / output single helical gear.