WO2013084838A1 - ウォームギヤ機構 - Google Patents
ウォームギヤ機構 Download PDFInfo
- Publication number
- WO2013084838A1 WO2013084838A1 PCT/JP2012/081254 JP2012081254W WO2013084838A1 WO 2013084838 A1 WO2013084838 A1 WO 2013084838A1 JP 2012081254 W JP2012081254 W JP 2012081254W WO 2013084838 A1 WO2013084838 A1 WO 2013084838A1
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- WIPO (PCT)
- Prior art keywords
- tooth
- worm
- wheel
- hob
- line
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
- F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19828—Worm
Definitions
- the present invention relates to an improved technique for a worm gear mechanism.
- a worm gear mechanism is mounted on a power steering device of a vehicle (see, for example, Patent Document 1 (FIG. 14)).
- a worm gear mechanism as shown in Patent Document 1 includes a worm connected to an electric motor via a worm shaft and a worm wheel meshing with the worm, and the auxiliary torque generated by the electric motor is transferred from the worm to the worm. It is a transmission mechanism that boosts and transmits to the wheel.
- the worm when a force is applied in the direction in which the worm rotates and pushes the worm wheel, the worm receives a reaction force from the worm wheel at the contact point between the worm and the worm wheel. If the strength of the worm gear mechanism can be increased, it is desirable to extend the life of the worm gear mechanism.
- An object of the present invention is to provide a technique capable of increasing the strength of the worm gear mechanism.
- a worm gear mechanism comprising a worm and a worm wheel meshing with the worm
- at least the end surface of the worm tooth is formed in an arc shape
- the radius of the arc of the end surface is set.
- the center is located closer to the center line of the worm than the pitch line of the worm
- the worm wheel is a hob used for gear cutting of the worm wheel
- at least the end surface of the teeth of the hob is formed in an arc shape
- the center of the radius of the arc of the end face is closer to the center line of the hob than the pitch line of the hob, and is tooth-cut by the hob, and engages the worm and the worm wheel.
- the disengagement length of the worm gear mechanism to be adjusted is the distance of the worm gear mechanism consisting of an involute tooth worm and an involute tooth worm wheel. Than the length fit is set to be larger, and wherein the.
- At least the teeth of the worm wheel are made of a resin molded product.
- the surface pressure near the base circle can be reduced. Further, since the tooth profile on the tooth bottom side of the base circle can be eliminated, the tooth bottom side of the base circle can also be a meshing surface. As a result, the meshing rate can be increased without increasing the diameter of the tooth tip of the worm wheel, so that the strength of the worm gear mechanism can be increased.
- the resin worm wheel has a small elastic coefficient, the teeth are easily bent.
- the lower the mesh height the greater the shared load of the meshed teeth.
- the contact area of the portion with low meshing height can be increased, the surface pressure can be lowered.
- FIG. 1 is a schematic diagram of an electric power steering device equipped with a worm gear mechanism according to the present invention. It is a whole block diagram of the electric power steering apparatus shown by FIG.
- FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 2.
- FIG. 4 is a sectional view taken along line 4-4 of FIG. It is a figure which compares the worm wheel shown in FIG. 4 with the conventional worm wheel. It is a figure explaining the improvement measure of the conventional worm wheel shown in FIG.
- FIG. 6 is a diagram for formulating a tooth root shape of the conventional worm wheel shown in FIG. 5. It is the figure which modeled for formulation of the tooth root shape of the conventional worm wheel shown in FIG.
- FIG. 16 is a diagram for explaining a state in which a worm modified based on the worm shown in FIG. 15 and a worm wheel using the tooth profile shown in FIG. 14 are engaged with each other. It is a figure which compares mesh
- FIG. 22 compares the worm wheel shown in FIG. 21 with the worm wheel without undercut shown in FIG. 4.
- FIG. 26 is a diagram for explaining the meshing between the worm wheel and the worm shown in FIG. 25. It is a figure explaining the gear cutting tool (hob) for forming the worm wheel shown by FIG. It is a figure explaining the tooth profile of the worm wheel formed by the hob shown in FIG. It is a figure explaining mesh
- FIG.5 It is a figure explaining mesh
- the electric power steering apparatus 10 includes a steering system 20 that extends from a steering wheel 21 of a vehicle to steering wheels 29 and 29 (for example, front wheels) of the vehicle, and an auxiliary torque that applies auxiliary torque to the steering system 20.
- Mechanism 40 that extends from a steering wheel 21 of a vehicle to steering wheels 29 and 29 (for example, front wheels) of the vehicle, and an auxiliary torque that applies auxiliary torque to the steering system 20.
- a pinion shaft 24 is connected to a steering wheel 21 via a steering shaft 22 and universal shaft joints 23, 23, and a rack shaft 26 is connected to the pinion shaft 24 via a rack and pinion mechanism 25.
- the left and right steering wheels 29 and 29 are connected to both ends of 26 via left and right tie rods 27 and 27 and knuckle 28 and 28, respectively.
- the rack and pinion mechanism 25 includes a pinion 31 formed on the pinion shaft 24 and a rack 32 formed on the rack shaft 26.
- the left and right steering wheels 29, 29 can be steered by the steering torque via the rack and pinion mechanism 25 and the left and right tie rods 27, 27. it can.
- the auxiliary torque mechanism 40 detects the steering torque of the steering system 20 applied to the steering wheel 21 by the steering torque sensor 41, and generates a control signal by the control unit 42 based on the torque detection signal of the steering torque sensor 41.
- An auxiliary torque corresponding to the steering torque is generated by the electric motor (electric motor) 43 based on the signal, the auxiliary torque is transmitted to the pinion shaft 24 via the worm gear mechanism 44, and the auxiliary torque is further transmitted from the pinion shaft 24 to the steering system 20.
- This is a mechanism for transmitting to the rack and pinion mechanism 25.
- the steering torque sensor 41 detects the torque applied to the pinion shaft 24 and outputs it as a torque detection signal, and is composed of, for example, a magnetostrictive torque sensor or a torsion bar torque sensor.
- the steering wheels 29 and 29 can be steered by the rack shaft 26 by a combined torque obtained by adding the auxiliary torque of the electric motor 43 to the steering torque of the driver.
- the housing 51 extends in the vehicle width direction (left-right direction in the figure) and accommodates the rack shaft 26 so as to be slidable in the axial direction.
- Tie rods 27 and 27 are connected to the rack shaft 26 via ball joints 52 and 52 at both ends in the longitudinal direction protruding from the housing 51.
- the electric power steering apparatus 10 houses the pinion shaft 24, the rack and pinion mechanism 25, the steering torque sensor 41, and the worm gear mechanism 44 in the housing 51, and the upper opening of the housing 51 is formed in the upper cover portion 53. It was closed with.
- the steering torque sensor 41 is attached to the upper cover portion 53.
- the housing 51 has an upper portion 24u, a longitudinal center portion 24m, and a lower end portion 24d of the pinion shaft 24 extending vertically through three bearings (a first bearing 55, a second bearing 56, and a third bearing 57 in order from top to bottom). Further, the electric motor 43 is attached and a rack guide 60 is provided. As the three bearings 55 to 57, rolling bearings are used.
- the rack guide 60 is a rack pressing means that includes a guide portion 61 that contacts the rack shaft 26 from the side opposite to the rack 32 and an adjustment bolt 63 that presses the guide portion 61 via a compression spring 62.
- the electric motor 43 is attached to the side surface of the housing 51 and includes a lateral motor shaft (output shaft) 43a.
- the motor shaft 43 a extends into the housing 51 and is connected to the worm shaft 46 by a shaft coupling 45.
- the housing 51 supports both end portions 46a and 46b of the worm shaft 46 extending horizontally through bearings 47 and 48 while restricting movement in the axial direction.
- the two bearings 47 and 48 are both rolling bearings.
- the worm gear mechanism 44 is an auxiliary torque transmission mechanism that transmits the auxiliary torque generated by the electric motor 43 to the pinion shaft 24, that is, a booster mechanism. More specifically, the worm gear mechanism 44 includes a worm 70 and a worm wheel 80 that meshes with the worm 70.
- the worm wheel 80 is hereinafter abbreviated as “wheel 80”.
- the center line CL of the wheel 80 is disposed substantially perpendicular to the center line WL of the worm 70.
- the center line CL of the wheel 80 is also the center line CL of the pinion shaft 24.
- the worm 70 is a metal product integrally formed with the worm shaft 46, for example, a steel product such as a carbon steel material for machine structure (JIS-G-4051).
- the wheel 80 is a resin product such as a nylon resin as a whole or at least a portion of the teeth 81. Since the resin product wheel 80 is meshed with the metal product worm 70, meshing can be made relatively smooth and noise can be further reduced.
- the thread 71 (that is, the tooth 71) of the worm 70 is set to one.
- a plurality of teeth 81 having an equal pitch are formed over the entire circumference.
- the wheel 80 is attached such that relative movement in the axial direction is restricted with respect to the pinion shaft 24 and relative rotation is restricted.
- the wheel 80 is connected to the pinion shaft 24 by a serration or a spline in the rotational direction, and is attached by a retaining ring in the axial direction.
- Such a worm gear mechanism 44 is required to have various performances. For example, one of them is an improvement in meshing rate and an increase in strength. Details will be described in the following figures.
- the tooth profile of the worm wheel 220 of the worm gear mechanism 200 is an involute tooth profile having a tooth tip 221a, a tooth bottom 221c, a base circle 301, and a pitch circle (meshing pitch circle) 302.
- the tooth thickness at the portion where the thickness of the tooth 221 is maximum is W2.
- the tooth base 221b is cut down and undercut occurs.
- the tooth thickness is W1 at the portion where the thickness of the tooth 221 is minimum.
- the tooth thickness W1 is smaller than W2.
- the bending strength of the teeth 221 decreases.
- the tooth profile of the wheel 220 has a convex shape with a small radius of curvature in the vicinity of the basic circle 301. Since the convex shape has a small radius of curvature, the contact area in contact with the worm is reduced. As a result, the meshing contact surface pressure increases. That is, when the tooth height HT of the involute tooth wheel 220 is increased, the bending strength and the surface pressure strength tend to decrease.
- the tooth shape of the wheel 220 is formed by a hob (hob cutter) 230.
- the pitch center 231Ce of the teeth 231 of the hob 230 is located at the site of the line 312 (pitch height 312).
- the locus of the pitch center 231Ce is indicated by a line 311.
- the teeth 231 of the hob 230 move so as to roll on the pitch circle 302 of the wheel 220 to create (form) a tooth profile of the wheel 220.
- the tooth tip 231a of the hob 230 is scooping out the lower part (surface near the tooth bottom) of the tooth 220 of the wheel 220 from the base circle 301.
- the corner of the tooth tip 231a of the tooth 231 of the hob 230 is formed in an arc shape having a predetermined small radius of curvature.
- the locus of the arc center 231b at the corner of the tooth tip 231a is indicated by a line 313.
- the present inventors have obtained the knowledge that the surface of the tooth root 221 is formed into a concave shape (necked shape) by moving the arc center 231b to draw a ring. That is, the locus 313 of the center of the arc 231b at the corner of the tooth tip 231a draws a ring at a position closer to the center than the basic circle 301, and as a result, it is considered that this is a factor that causes the undercut phenomenon (undercut). .
- the length from the line 312 to the center 231b of the curved shape is h.
- the length h is referred to as an arm length.
- the locus 313 of the center 231b of the arc at the corner of the tooth tip 231a of the tooth 231 of the hob 230 will be considered again.
- the locus 313 depicts a “negative dislocation trochoid curve”.
- the present inventors considered that the reason why the locus 313 draws a negative dislocation trochoid curve is that the center 231b of the arc of the corner exists on the tooth tip 231a side with respect to the pitch height 312. That is, when the locus 313 draws a negative dislocation trochoid curve, the corner of the tooth tip 231a of the hob 230 performs a gear cutting action so as to draw a ring on the center side of the basic circle 301.
- the surface of the tooth root 221 b is cut down by the corner of the tooth tip 231 a of the hob 230. As a result, an undercut occurs on the surface of the tooth base 221b.
- FIG. 25A schematically shows the pitch circle 302 of the conventional wheel 220 shown in FIG. 22 and the tooth profile of the tooth 231 of the hob 230 for gear cutting the wheel 220.
- the teeth 231 of the hob 230 are shown larger than the wheel 220.
- the tooth profile of the tooth 231 of the conventional hob 230 is an involute tooth profile, and the corner of the tooth tip 231a is formed in an arc shape.
- the center 231 b of the arc is located on the tooth tip 231 a side (the tooth root side of the wheel 220) with respect to the pitch line 312 of the hob 230. In this case, the locus 313 of the center 231b draws a negative dislocation trochoid curve.
- FIG. 25B schematically shows the pitch circle 112 of the wheel 80 of the embodiment shown in FIG. 4 and the tooth profile of the tooth 91 of the hob 90 for gear cutting the wheel 80.
- the teeth 91 of the hob 90 are shown larger than the wheel 80.
- the tooth profile of the tooth 91 of the hob 90 of the embodiment is an involute tooth profile.
- the end surface 91c of the tooth 91 is modified into an arc shape having a large curvature radius. This is to prevent the locus 313 of the arc center 93 (hereinafter referred to as “the tooth center 93”) of the tooth surface 91c from becoming a negative dislocation trochoid.
- the center 93 of the end surface 91 c is located closer to the center line (axis line) WL ′ of the hob 230 than the pitch line 94.
- trajectory 313 of the center 93 of the surface of an addendum draws a normal dislocation trochoid. That is, by using a normal dislocation trochoid, a trajectory that draws a conventional ring can be suppressed.
- the tooth 91 of the hob 90 of the embodiment has at least the end surface 91c formed in an arc shape.
- the center 93 of the arc radius of the end surface 91 c is located closer to the center line (axis line) WL ′ of the hob 90 than the pitch line 94 of the hob 90.
- the worm 70 meshing with the wheel 80 is also formed in the same shape as the hob 90. That is, at least the end surface 71c of the tooth 71 of the worm 70 is formed in an arc shape.
- the center 73 of the radius of the arc of the end surface 71 c is located closer to the center line (axis line) WL ′′ of the worm 70 than the pitch line 74 of the worm 70.
- the locus of the center 93 of the end surface of the wheel 80 of the embodiment draws a normal dislocation trochoid curve as indicated by a line 313.
- the teeth 81 of the wheel 80 formed by the hob 90 that moves along the line 313 (the locus 313) are formed in a shape that is not cut down at the tooth base 81c.
- 81 a is a tooth tip of the tooth 81 of the wheel 80.
- 81b is the root of the tooth 81.
- the trajectory of a point (coordinates X, Y) in the moving circle 402a is obtained as follows for the moving circle 402a rolling on the fixed circle 401.
- the fixed circle 401 is a circle assuming a pitch circle of the wheel 80.
- Reference numeral 402 a denotes a moving circle that rolls on the fixed circle 401.
- Reference numeral 402b denotes a moving circle that rolls on the fixed circle 401 by a predetermined distance from 402a.
- a line 403 indicates the locus of the point (X, Y) in the moving circle 402.
- the line 403 is a trochoid curve.
- P1 refers to a point on the line 403 in the moving circle 402a and is referred to as an arm tip.
- h is the length (arm length) from the point P1 to the fixed circle 401.
- the locus of the point (X, Y) in the moving circle 402b that is, the trochoid curve is obtained as follows.
- FIG. 29 shows the meshing state of the conventional worm gear mechanism 200.
- the worm gear mechanism 200 includes a worm 210 and a worm wheel 220.
- the tooth profile of each tooth of the worm 210 and the wheel 220 is an involute tooth profile.
- the intersection of the tooth tip of the worm 210 and the basic circle 301 of the wheel 220 is defined as a first intersection P11.
- the intersection of the pitch line 332 of the worm 210 and the pitch circle 302 of the wheel 220 is defined as a second intersection P12.
- a straight line passing through the first intersection P11 and the second intersection P12 is referred to as a mesh line 321.
- An intersection point between the mesh line 321 and the tip circle 305 of the wheel 220 is defined as a third intersection point P13.
- the length from the first intersection point P11 to the third intersection point P13 is referred to as "meshing length".
- the worm 210 and the wheel 220 can mesh with each other within a meshing length range on the meshing line 321.
- the base circle 301 of the wheel 220 is uniquely determined by the module, the number of teeth, and the twist angle in the involute tooth profile. For this reason, the position of the third intersection P13 is also uniquely determined.
- the conventional worm gear mechanism 200 when used in an electric power steering device for a vehicle, a resin material is often used for the teeth 221 of the wheel 220.
- the teeth 221 are easily bent because the elastic coefficient of the material is small.
- the lower the meshing height the greater the shared load of the meshing teeth 221. That is, the load applied to each tooth 221 increases.
- the tooth profile of the conventional hob tooth 231 indicated by an imaginary line in FIG. 30 was an involute shape in which the meshing tooth surface is a straight line.
- a part of the end surface 91c is made thinner than the involute shape.
- a part of the end surface 91c of the tooth 91 of the hob 90 of the embodiment is formed in a substantially arc shape in contact with the involute curve, and the tooth thickness is reduced.
- the tooth 221 of the conventional wheel 220 shown by an imaginary line in FIG. 31 is cut by a conventional hob 230 (see FIG. 30).
- a lowering phenomenon occurs on the surface of the tooth base.
- the tooth surface of the tooth 221 has a remarkable convex shape in the vicinity of the basic circle 301.
- the tooth 81 of the wheel 80 of the embodiment shown by a solid line in FIG. 31 is cut by the hob 90 of the embodiment.
- the tooth thickness of the teeth 91 of the hob 90 is thin.
- the tooth 81 of the wheel 80 is not subject to a depressing phenomenon (undercut) on the surface of the tooth base.
- the tooth surface of the tooth 81 does not have a convex shape in the vicinity of the basic circle 111.
- the surface pressure acting on the tooth surface of the tooth 81 can be reduced.
- FIG. 32 shows the meshing state of the conventional worm gear mechanism 200, corresponding to FIG.
- the worm 210 and the wheel 220 mesh with each other in the vicinity of the base circle 301 (on the meshing line 321), as indicated by a white arrow in FIG.
- FIG. 33 shows the meshing state of the worm gear mechanism 44 of the embodiment, and corresponds to FIG.
- the worm 70 and the wheel 80 mesh with each other at a position closer to the bottom of the tooth than the basic circle 111, as indicated by a hollow arrow in FIG.
- Reference numeral 121 denotes a meshing line between the wheel 80 and the worm 70.
- FIG. 36 shows a change in the tooth profile of the tooth 81 of the wheel 80 by changing the correction amount of the tooth thickness of the hob tooth.
- the tooth 221 of the conventional wheel 220 indicated by an imaginary line in FIG. 36 has a concave root surface. That is, an undercut has occurred on the surface of the tooth base. This is because the teeth of the teeth 231 of the hob 230 (see FIG. 23) are not corrected at all.
- the teeth 91 of the hob 90 were modified as shown in FIG.
- the tooth profile of the tooth 81 of the wheel 80 when the correction amount of the tooth 91 is small is shown by a thin solid line in FIG.
- the tooth thickness at the base of the tooth 81 is larger than the conventional one.
- the tooth profile of the tooth 81 of the wheel 80 when the correction amount of the tooth 91 is large is indicated by a thick solid line in FIG.
- the tooth thickness at the base of the tooth 81 is further increased.
- the dent surface of the tooth 81 of the wheel 80 disappears and the tooth thickness of the tooth base increases.
- the radius of curvature of the tooth surface of the tooth 81 in the vicinity of the base circle 111 increases. That is, the tooth surface of the tooth 81 is near the basic circle 111 and does not have a large convex shape as in the prior art.
- the teeth 81 of the wheel 80 of the above embodiment can be the teeth 81X of the wheel 80X of the modified example shown in FIG.
- the tooth 81 ⁇ / b> X of the wheel 80 ⁇ / b> X of the modified example has a tooth thickness of at least a part of the tooth base set larger than the tooth thickness of the tooth root of the tooth 221 of the conventional wheel 220. Therefore, the tooth 81X of the modified example can obtain the same effect as the tooth 81 of the embodiment. More specifically, the tooth profile of the tooth 221 of the conventional wheel 220 is indicated by an imaginary line in FIG.
- the tooth profile of the tooth 81 of the wheel 80 of the embodiment is shown by a thin solid line in FIG.
- the tooth profile of the tooth 81X of the wheel 80X of the modified example is shown by a thick solid line in FIG.
- the tooth profile of the tooth 81X of the modification is formed in an intermediate shape between the tooth profile of the conventional tooth 221 and the tooth profile of the tooth 81 of the embodiment.
- the height of the root of the tooth 81 of the embodiment is the same as the height of the root of the conventional tooth 221.
- the height of the root of the tooth 81X of the modified example is smaller than the height of the root of the tooth 81 of the embodiment.
- the tooth thickness of the tooth base of the modified tooth 81X is larger than the tooth thickness of the tooth base of the conventional tooth 221 and smaller than the tooth thickness of the tooth base of the tooth 81 of the embodiment.
- the root surface of the tooth 81X of the modified example has no dent.
- the modified tooth 81X has a special tooth profile and cannot be produced by a machine that creates an involute tooth profile such as a hobbing machine, but can be created directly by injection molding using a mold or milling. it can. That is, in the embodiment, the surface pressure strength and the bending strength of the tooth 81 are increased by an indirect method in which the tooth 81 of the wheel 80 is created by the hob whose tooth thickness is corrected. On the other hand, in the modified example, the tooth 81X can be directly created to increase the surface pressure strength and bending strength of the tooth 81X. For this reason, the tooth profile of the desired tooth 81X can be designed directly and finely. Therefore, the tooth 81 of the embodiment can be further improved. For example, the gear tooth height, the radius of curvature of the tooth bottom, and the tooth thickness can be finely changed.
- the minimum correction amount of the tooth 91 of the hob 90 that is necessary to prevent the root 221b from being cut down is generated.
- ⁇ (see FIG. 38), that is, the minimum correction amount ⁇ is obtained as follows. That is, with reference to FIG. 38, the minimum correction amount ⁇ of the teeth 91 of the hob 90 is obtained by the following equation (8).
- the tooth profile of the wheel 80 is based on the involute tooth profile Tim. The wheel 80 is assumed to rotate in the rotational movement direction Rr (the clockwise direction Rr in the figure). The teeth 91 of the hob 90 move in parallel with respect to the pitch line Lhp (movement direction Ds).
- the tooth profile of the tooth 91 of the hob 90 is indicated by the line Hc.
- the intersection point between the involute action line Lia of the tooth 81 of the wheel 80 and the involute tooth profile Tim of the tooth 81 is a cutting point Ps.
- the point at which the tooth 81 of the wheel 80 starts to be cut down by the hob 90, that is, the cut-down point is Pr.
- the intersection of the involute action line Lia of the tooth 81 of the wheel 80 and the pitch line Lhp of the tooth 91 of the hob 90 is defined as Px.
- a straight line from the center CL of the wheel 80 to the intersection Px is defined as a reference line Lp.
- Py be the intersection of the tooth surface Th1 of the tooth 91 of the hob 90 corrected by the minimum correction amount ⁇ and the basic circle 111 of the tooth 81 of the wheel 80.
- a straight line passing through the center CL of the wheel 80 and the intersection point Py is defined as a correction reference line Lt.
- the inclination angle (correction angle) of the correction reference line Lt with respect to the reference line Lp is defined as ⁇ .
- the correction angle ⁇ is required to be larger than the pressure angle ⁇ of the tooth 81 of the wheel 80 (of the tooth 91 of the hob 90) ( ⁇ > ⁇ ).
- m Module of wheel 80
- Z Number of teeth of wheel 80
- Rb Radius of base circle 111 of wheel 80 Rp; Radius of pitch circle 112 of wheel 80 Rp ⁇ Rb ⁇ cos ⁇ ; Intersection from pitch line Lhp of teeth 91 of hob 90 Height to Py (however, ⁇ > ⁇ ).
- the region for correcting the tooth profile is the height from the pitch line Lhp of the hob 90 to the tooth tip direction, that is, from the pitch line Lhp of the tooth 91 of the hob 90.
- the tooth surface has a height up to the intersection Py in the range of “Rp ⁇ Rb ⁇ cos ⁇ ” or more. Then, at the intersection Py where the height from the pitch line Lhp is “Rp ⁇ Rb ⁇ cos ⁇ ”, the tooth 91 is corrected by a minimum correction amount ⁇ or more in the direction in which the tooth thickness decreases.
- the tooth surface of the tooth 91 corrected by the minimum correction amount ⁇ is indicated by a curve Th1.
- the involute action line Lia of the tooth 81 of the wheel 80 is extended to the action line L1 on the base circle 111.
- the tooth surface when the correction amount of the tooth 91 is larger than the minimum correction amount ⁇ is indicated by a curve Th2.
- the involute action line Lia of the tooth 81 of the wheel 80 is extended to the action line L2 inward of the base circle 111.
- the main problem of the conventional research was the examination of the optimal worm tooth profile that positively elastically deforms the worm wheel. For this reason, there was still room for improvement in the tooth profile of the worm wheel.
- the engagement rate is geometrically improved by increasing the module and the torsion angle.
- the worm wheel diameter had to be simply increased.
- the present inventors have been working on increasing the strength of a small worm wheel.
- further downsizing of the worm wheel was challenged, and attention was paid to the tooth root shape of the worm wheel.
- the idea has been reached to improve the meshing rate by effectively meshing the worm below the base circle of the worm wheel.
- the geometric shape below the basic circle formed by actual processing was considered. Based on this consideration, the theory that meshes effectively up to the base circle is called MUB (Meshing Under Base-circle) theory.
- MUB Messhing Under Base-circle
- the tooth profile of the tooth 221 of the conventional worm wheel 220 shown in FIG. 5A is an involute tooth profile.
- a cut-down portion U (Undercut) cut down by the conventional hub 230 is generated on the tooth surface of the tooth 221.
- the tooth profile of the tooth 81 of the worm wheel 80 of the embodiment shown in FIG. 5B is a tooth profile of a new shape (New Profile Formed by MUB Theory) based on the MUB theory. Based on the MUB theory, a worm wheel 80 (hereinafter referred to as wheel 80) was actually manufactured, and the meshing length was measured to verify the effect of the MUB theory. We report on the findings obtained in the course of this research.
- Fig. 6 shows a conventional worm gear mechanism in which a worm and a wheel mesh with each other (Contact, Line, of Worm, Tooth, Tip, Corner, Radius, Contact, Line, of Involute, Worm, Wheel).
- the size of the wheel 220 is increased, and the meshing line 321 is extended in the direction of the tooth tip 221a to improve the meshing rate.
- the mesh line 321 can be extended in the direction of the tooth root 221b, the mesh rate can be improved without increasing the size. In order to achieve this, we worked on a new tooth profile that meshes well even below the basic circle 301.
- Fig. 7 shows the locus of the hob (Locus of Hob Cutter).
- the root shape formed by the conventional involute hob 230 is formulated and analyzed.
- an ideal tooth profile that effectively meshes even below the basic circle 301 is searched.
- the datum line 312 (Datum Line) of the hob 230 rolls without sliding on the gear pitch circle of the wheel 220.
- the center 231Ce of the tooth (blade) 231 of the hob 230 draws an epitrochoid curve 311.
- the envelope formed when the hob 230 moves along the epitrochoid curve 311 forms the tooth profile of the tooth 221 of the wheel 220.
- the shape of the tooth root 221 b below the basic circle 301 is formed by the tooth tip 231 a of the hob 230.
- WP indicates the working point of the hob 230 (Hob Cutter Working Point).
- Reference numeral 307 denotes an involute profile portion of the wheel 220.
- Reference numeral 308 denotes a tooth base portion (Dedendum Formed by Corner Radius) of the wheel 220.
- Fig. 8 shows the envelope of the tooth of the hob (Envelope of Hob Tooth Tip).
- FIG. 8 modeling for formulation of the tooth root shape was performed. First, a line 313 drawn by the tooth tip arc center T of the hob 230 is obtained, and then an envelope 314 when a circle with a radius rh moves on the line 313 is obtained.
- an envelope 314 at the center of the tooth tip arc is obtained.
- the point E on the envelope 314 is on the normal 315 of the line 313 (trochoid curve) passing through the point T. Since the distance TE is a point that coincides with the hob tooth tip radius rh, it can be expressed as the following equations (3) to (5).
- the trochoid curves in FIG. 9A is a curve that draws a ring.
- the zero-dislocation trochoid in FIG. 9B is a substantially V-shaped curve having a corner at the intersection with the pitch circle 302.
- the normal dislocation trochoid in FIG. 9C is a substantially V-shaped curve having both a concave shape and a low curvature convex shape.
- FIG. 10 shows an envelope by a negative dislocation trochoid and an action line of a gear using the envelope as a tooth profile (Meshing of Gears Formed by Negative Shifted Trochoid).
- the horizontal axis corresponds to the tooth thickness direction (Tooth Thickness Direction)
- the vertical axis corresponds to the tooth tip direction (Tooth Tip Direction).
- the action line 316 (Line ⁇ of Action) can be extended from the basic circle 301 to the center side.
- the pressure angle (Pressure Angle) of the contact point P5 (Contact Point) is 75 deg (see P6) and increases to the vicinity of 90 deg. For this reason, the worm self-locks and cannot rotate (see SL).
- PP indicates a pitch point (Pitch Point).
- the pitch point is a point where the normal line of the tooth surface at the meshing contact point of the gear always passes.
- a line 317 is a worm tooth profile (Worm Profile).
- Fig. 11 shows the envelope of zero dislocation trochoid and its action line (Meshing of Gears Formed by Zero Shifted Trochoid).
- the horizontal axis corresponds to the tooth thickness direction
- the vertical axis corresponds to the tooth tip direction.
- the envelope 314 below the basic circle 301 is an arc-shaped Nobikov tooth profile. For this reason, the front meshing rate is less than 1, and the constant velocity that is the mechanical condition of the gear cannot be satisfied. In order to transmit the constant speed rotation, it is necessary to make the overlapping meshing ratio 1 or more by the multi-row worm, so that the wheel becomes large.
- MS is a simultaneous meshing (Meshing Simultaneously) region.
- Fig. 12 shows the envelope of the normal dislocation trochoid and its action line (Meshing of Gears Formed by Positive Shifted Trochoid).
- the horizontal axis corresponds to the tooth thickness direction
- the vertical axis corresponds to the tooth tip direction.
- the action line 316 can be extended from the basic circle 301 to the center side. Since the normal line 315 of the envelope 314 at the contact point always passes through the pitch point PP, the mechanical condition of the gear can be satisfied and meshed effectively.
- FIG. 13 shows the shape of the tooth base (Profile of Dendendum). As shown in FIG. 12 and FIG. 13, from the above consideration, the conventional involute tooth profile cannot be meshed with the basic circle 301 or less because the shape of the tooth root is formed by the negative dislocation trochoid. all right.
- FIG. 14 shows a wheel in which a tooth root is formed by a normal dislocation trochoid (MUB Profile of Worm Wheel).
- FIG. 15 shows the meshing of the worm using the tooth profile.
- the wheel tip 81a has the same involute meshing line as before (please put a sign in the drawing), and the tooth root can mesh up to the base circle 111 or less along the action line of the normal dislocation trochoid. it can.
- These two lines of action please add a sign to the drawing) are connected smoothly and meet the mechanical conditions of the gear in all contact areas, so you can see that this new tooth profile provides an effective mesh. It was.
- the new tooth profile can extend the distant meshing length from the conventional limit LOA to LOAmod, and can improve the meshing rate compared to the involute tooth profile.
- the distant meshing length refers to the meshing length from the pitch point to the vicinity of the tooth tip of the worm.
- the meshing theory that effectively meshes even below the basic circle 111 is named MUB (Meshing Under Base-circle) theory.
- the shared load concentrates on the A tooth 81A having a low meshing height as shown in FIG. 15, so conventionally, the tooth thickness of the worm tooth tip surface is corrected in the minus direction to concentrate the load.
- the other meshing teeth 81B and 81C were dispersed in the other meshing teeth 81B and 81C.
- the actual meshing action line at the time of torque application can be moved in the direction of the pitch circle 112 of the wheel.
- the modified worm and the wheel 80 based on the MUB theory are engaged with each other, the result is as shown in FIG. 16, and the inclination of the engagement action line 121 can be reduced. ).
- the meshing rate which was 2.2 in the past, can be designed to be 3.0 or more without increasing the size of the wheel.
- FIG. 17 shows a comparison between a conventional involute tooth profile and a tooth profile based on the MUB theory.
- the vertical axis shows the contact height above the pitch line (Contact Height Above Pitch Line).
- the upper side of the drawing is the addendum direction, and the lower side of the drawing is the dedendum direction.
- a line 341 connecting the points plotted by the black diamond shows the conventional result.
- a line 342 connecting the points plotted by white circles indicates the result according to the MUB theory.
- a line 343 is a line (Base Line) indicating the meshing height of the base circle.
- the area indicated by the slanting line to the right is the contact area in both conventional and MUB theory.
- the region indicated by the slanting line at the lower left is a contact region in the MUB theory only.
- the blue paste BP is applied to the tooth surface of the worm 70, meshed with the wheel 80, torque is applied to the worm 70, and the shape of the peeled area of the blue paste BP is measured. did.
- FIG. 19 (a) shows a worm 70 coated with blue paste BP.
- S is a point where contact with the wheel 80 has started (Start Point of Mesh).
- E is the point where the contact with the wheel 80 is finished (End Point of Mesh).
- CAa is a part where the blue paste BP is peeled off, that is, a part in contact with the wheel 80 (Contact (Area of Worm).
- FIG. 19B shows a wheel 80 meshed with the worm 70.
- CAb is a part to which the blue paste BP is attached, that is, a part in contact with the worm 70 (Contact Area of Worm Wheel). It can be seen that the worm 70 is in contact with the center circle 111 to the center side.
- FIG. 20 shows the contact range of the worm (Contact Area of Worm). On the horizontal axis, the rotation angle of the worm (Rotation Angle of Worm) is shown. The vertical axis indicates the contact height (Contact Height).
- the diamond shape plot shows the measurement result (Actual Measurement of Involute Gear) when using a wheel with an involute tooth profile. What is indicated by the triangular plot is a calculated value (Calculated Point) when the wheel according to the embodiment is used. What is indicated by the round-shaped plot is a measurement result (Actual Measurement) when the wheel according to the example is used.
- the area outside the point plotted with the diamond shape and inside the point plotted with the round shape, that is, the area indicated by the diagonal lines, corresponds to the extent that the meshing area is expanded by the wheel according to the embodiment.
- the rotation direction of the worm when the meshing progresses from the tooth root of the worm to the tooth tip direction is defined as the positive direction with reference to the phase of the worm where the meshing starts geometrically. It was verified that the rotational angular velocity of the wheel was 1.0 rps and the input torque of the worm was 3.2 Nm.
- the meshing area of the worm tooth surface corresponds to about 1080 deg of the worm rotation phase, it was verified that the meshing rate was 3.0.
- the meshing rate was improved by 36% over the conventional tooth profile with a meshing rate of 2.2.
- the meshing area of the wheel could be expanded well below the basic circle.
- the MUB theory is effective as a design method for an electric power steering device (EPS) that requires mounting of a small and high-strength worm gear mechanism.
- EPS electric power steering device
- the tooth root shape of the wheel can be classified into three types according to the dislocation direction of the center point of the tooth tip arc of the hob. It was found that the tooth profile formed by the negative dislocation trochoid self-locks and cannot effectively engage below the base circle. Since the tooth profile formed by the zero dislocation trochoid is an arc tooth profile below the basic circle, it was found that a multi-row worm was required to satisfy the constant velocity of the gear, and the wheel was enlarged. According to the MUB theory in which the root tooth profile is formed by the normal dislocation trochoid, the wheel can be effectively meshed even below the basic circle that did not mesh with the involute tooth profile without increasing the size of the wheel. By applying the MUB theory, it has been proved by a meshing test that a high meshing rate of 3.0 can be achieved even in a single worm which is generally considered to have a low meshing rate.
- a worm gear mechanism can also be mounted in another apparatus and is not restricted to an electric power steering apparatus.
- the worm gear mechanism of the present invention is suitable for use in an electric power steering device for a vehicle.
- Worm gear mechanism 70 ... Worm, 71 ... Worm teeth, 71c ... Worm end surface, 74 ... Worm pitch line, 80 ... Worm wheel, 90 ... Hob, 91 ... Hob tooth, 91c ... Hob tooth End of tooth surface, 93 ... Center of end surface of hob, 94 ... Pitch line of hob, WL ... Center line of worm, 210 ... Worm of involute tooth profile, 220 ... Worm wheel of involute tooth profile, 200 ... Conventional worm gear Mechanism, WL ′: Hob center line, L: Distant engagement length, Llim: Conventional distant engagement length.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Thermal Sciences (AREA)
- Gears, Cams (AREA)
- Power Steering Mechanism (AREA)
- Gear Transmission (AREA)
Abstract
Description
Z;ホイール80の歯数
Rb;ホイール80の基礎円111の半径
Rp;ホイール80のピッチ円112の半径
Rp-Rb・cosθ;ホブ90の歯91のピッチ線Lhpから交点Pyまでの高さ(但し、θ>α)。
図17には、従来のインボリュート歯形とMUB理論に基づく歯形の比較が示されている。横軸には、ホイールの接触高さ(Contact Height of Worm Wheel)が示されている。縦軸には、ピッチ線を基準とした接触高さ(Contact Height Above Pitch Line)が示されている。図面上側が歯先(addendum)方向であり、図面下側が歯元(dedendum)方向である。黒のダイヤによってプロットされた点を結んだ線341は、従来の結果を示している。白の○によってプロットされた点を結んだ線342は、MUB理論による結果を示している。線343は、基礎円の噛み合い高さを示す線(Base Line)である。右下がりの斜線によって示される領域は、従来及びMUB理論の両方における接触領域(Contact Area)である。左下がりの斜線によって示される領域は、MUB理論のみにおける接触領域である。MUB理論によるホイールを採用することにより、より広くの領域において接触領域を得ることができる
図18(b)に示されるような、MUB理論に基づくホイール80は、切下げを発生させないため、基礎円111以下まで良好に噛合い領域を拡大できる。
Claims (2)
- ウォームと、該ウォームに噛合うウォームホイールと、から成るウォームギヤ機構において、
前記ウォームの歯の少なくとも歯末の面は円弧状に形成され、該歯末の面の円弧の半径の中心は、前記ウォームのピッチ線よりも前記ウォームの中心線寄りに位置し、
前記ウォームホイールは、該ウォームホイールの歯切り加工用に用いるホブにおいて、該ホブの歯の少なくとも歯末の面が円弧状に形成され、該歯末の面の円弧の半径の中心が、前記ホブのピッチ線よりも前記ホブの中心線寄りに位置している、前記ホブによって歯切り加工されたものであり、
前記ウォームと前記ウォームホイールとを噛合わせる前記ウォームギヤ機構の遠のき噛合い長さは、インボリュート歯形のウォームとインボリュート歯形のウォームホイールとから成るウォームギヤ機構の遠のき噛合い長さよりも、大きく設定されている、
ことを特徴とするウォームギヤ機構。 - 前記ウォームホイールの少なくとも歯は、樹脂の成形品によって構成されている、請求項1記載のウォームギヤ機構。
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CN201280059855.0A CN103998821B (zh) | 2011-12-06 | 2012-12-03 | 蜗轮蜗杆副机构 |
BR112014013577A BR112014013577A2 (pt) | 2011-12-06 | 2012-12-03 | mecanismo de engrenagem espiralada |
IN4926CHN2014 IN2014CN04926A (ja) | 2011-12-06 | 2012-12-03 | |
JP2013548221A JP5734458B2 (ja) | 2011-12-06 | 2012-12-03 | ウォームギヤ機構 |
DE112012005088.6T DE112012005088T5 (de) | 2011-12-06 | 2012-12-03 | Schneckengetriebemechanismus |
US14/362,749 US9512898B2 (en) | 2011-12-06 | 2012-12-03 | Worm gear mechanism |
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JP2011-267389 | 2011-12-06 | ||
JP2011267389 | 2011-12-06 |
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PCT/JP2012/081254 WO2013084838A1 (ja) | 2011-12-06 | 2012-12-03 | ウォームギヤ機構 |
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US (1) | US9512898B2 (ja) |
JP (1) | JP5734458B2 (ja) |
BR (1) | BR112014013577A2 (ja) |
DE (1) | DE112012005088T5 (ja) |
IN (1) | IN2014CN04926A (ja) |
WO (1) | WO2013084838A1 (ja) |
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DE102021208421A1 (de) * | 2021-08-03 | 2023-02-09 | Brose Fahrzeugteile Se & Co. Kommanditgesellschaft, Bamberg | Verstellantrieb für ein Verstellelement eines Kraftfahrzeugs und Verwendung einer Schnecke |
EP4194716A1 (de) * | 2021-12-09 | 2023-06-14 | IMS Gear SE & Co. KGaA | Zahnradgetriebe sowie sitzlängsverstellung für ein kraftfahrzeug |
CN115929872B (zh) * | 2022-12-30 | 2023-10-20 | 江苏鑫和利精工有限公司 | 一种耐磨型蜗轮及其加工工艺 |
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Also Published As
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CN103998821A (zh) | 2014-08-20 |
US20140331802A1 (en) | 2014-11-13 |
JP5734458B2 (ja) | 2015-06-17 |
US9512898B2 (en) | 2016-12-06 |
JPWO2013084838A1 (ja) | 2015-04-27 |
DE112012005088T5 (de) | 2014-08-21 |
BR112014013577A8 (pt) | 2017-06-13 |
BR112014013577A2 (pt) | 2017-06-13 |
IN2014CN04926A (ja) | 2015-09-18 |
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