CN107701705A - The outer/inner engagement of straight-tooth, the outer/inner accurate bevel gear transmission of engagement of helical teeth - Google Patents

The outer/inner engagement of straight-tooth, the outer/inner accurate bevel gear transmission of engagement of helical teeth Download PDF

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Publication number
CN107701705A
CN107701705A CN201710844835.9A CN201710844835A CN107701705A CN 107701705 A CN107701705 A CN 107701705A CN 201710844835 A CN201710844835 A CN 201710844835A CN 107701705 A CN107701705 A CN 107701705A
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China
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roller
bevel gear
tooth
tapered roller
iii
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CN201710844835.9A
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杨荣刚
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Individual
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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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/038—Gearboxes for accommodating bevel gears
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • 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
    • F16H55/17—Toothed wheels

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Nuclear Medicine (AREA)

Abstract

The invention discloses the outer/inner engagement of straight-tooth, the outer/inner accurate bevel gear transmission of engagement of helical teeth, the accurate bevel gear transmission includes shell, bevel gear, key, axle, bearing, tapered roller, needle roller, roller, bearing pin, bolt, fixed dam, positioning baffle, alignment pin；The circumferentially uniform Z of bevel gearcIndividual tooth, Zc≥3；Roller is circumferentially uniformly distributed ZgIndividual hole, Zg≥3.The present invention four kinds of implementations be：1st, straight-tooth external toothing precision bevel gear transmission；2nd, straight-tooth internal messing precision bevel gear transmission；3rd, helical teeth external toothing precision bevel gear transmission；4th, helical teeth internal messing precision bevel gear transmission.The beneficial effect of patent of the present invention is：Accurate bevel gear transmission can realize no back clearance transmission, high transmission accuracy；Gearratio is definite value；The flank of tooth is pure rolling, transmission efficiency；It is simple in construction, bore the flank of tooth and relative slip is not present, wear small, long lifespan, the number of teeth for participating in engaging is more, stable drive；Processing and manufacturing is simple.

Description

Straight tooth external/internal gearing and helical tooth external/internal gearing precision bevel gear transmission mechanism
Technical Field
The invention relates to the technical field of mechanical transmission, in particular to a straight tooth external/internal meshing and helical tooth external/internal meshing precision bevel gear transmission mechanism.
Background
The bevel gear transmission mechanism mainly comprises gears and the like, and is widely applied to industrial production as an important component in transmission machinery. The high-power high-speed bevel gear has a complex transmission structure and high requirement on manufacturing precision; the bevel tooth surfaces slide relatively, so that abrasion is easy to generate; the backlash on the tooth side affects the transmission precision.
Disclosure of Invention
In order to solve the defects in the prior art, the invention provides a straight-tooth external/internal meshing and helical-tooth external/internal meshing precise bevel gear transmission mechanism. A novel tooth form is designed according to a gear enveloping principle, and rolling engagement of bevel gear transmission is realized by mounting a roller pin on a bevel gear. By changing the number of teeth on the gear, the transmission mechanism can be designed into a speed reducer and a speed increaser for use; the transmission ratio is a fixed value; the tooth surface is pure rolling, the transmission efficiency is high, the abrasion is small, and the service life of the transmission mechanism is long; the number of teeth engaged is large, and the transmission is stable; the mechanism has no backlash on the tooth side, and the transmission precision is high; the processing and the manufacturing are simple.
The technical scheme adopted by the invention is as follows:
the precise bevel gear transmission mechanism comprises a shell, a bevel gear, a key, a shaft, a bearing, a tapered roller, a roller pin, a roller wheel, a pin shaft, a bolt, a fixed baffle, a positioning baffle and a positioning pin; bevel gear circumferential uniform distribution Z c Tooth, Z c Not less than 3; roller wheel circumferential uniform distribution Z g Hole, Z g Not less than 3; the intersection point of the geometric central line of the hole and the rotary central line of the roller is O, the maximum base circle is tangent to the maximum rolling circle, the tangent point is Oz, and the angle of the rolling circle rotating around the tangent line is theta and is formed by the element [0, pi ]]The included angle between the connecting line of the point O and the tangent point Oz and the rotation center line of the roller is theta 2 ，θ 2 ∈[0,π/2]The included angle between the connecting line of the point O and the tangent point Oz and the rotation center line of the bevel gear is theta 1 ，θ 1 ∈[0,π/2]The intersection point of the geometric central line of the hole and the rotary central line of the roller is O, the intersection point of the rotary central line of the roller and the rotary central line of the bevel gear is O, the circle center of the circle on the large end surface of the tapered roller is P, the point P is positioned on the short-width rolling circle, l is the distance between the point O and the point P, and the radius of the circle on which the outer cylindrical surface of the tapered roller is positioned at the point P is R z Taper roller with half cone apex angleIs theta b ＝arctan(R z L) the corresponding short radius of the circle at point P is r p The radius of the corresponding round at point P is r g ，m＝r g /R p The corresponding base radius at point P is R j The maximum base circle radius is R, the maximum rolling circle radius is R, R/R = m, K is a short-amplitude coefficient, and K belongs to (0,1)]，r p ＝Kr g 。
A hole is processed on the small end face of the tapered roller, a connecting hole is processed on the positioning baffle, a positioning hole is processed on the positioning baffle, a unthreaded hole is processed on the positioning baffle, and a unthreaded hole is processed on the fixing baffle; the tapered roller is connected with the roller through the roller pin A, the pin shaft is arranged in the tapered roller hole and connected with the positioning baffle through the roller pin B, the tapered roller can rotate around the geometric center line of the tapered roller, the positioning pin is arranged in the connecting hole of the positioning baffle and the positioning hole of the roller to limit the relative rotation of the positioning baffle and the roller, and the bolt is connected with the roller to limit the relative movement of the positioning baffle, the roller, the positioning pin and the fixed baffle.
The relation between the number of the conical rollers and the number of the conical teeth is Z g R p ＝Z c r g ；m&1, the radius of the rolling circle is larger than that of the base circle; 1>m&When 0, the radius of the base circle is larger than that of the rolling circle; when m =1, the radius of the rolling circle is equal to the radius of the base circle.
The conical surface of the tapered roller is tangent to the tooth surface of the bevel gear;
when the roller is a driving wheel, the roller drives the tapered roller to move through the roller pin and the pin shaft, the tapered roller pushes the bevel gear to rotate, the tapered roller is meshed with the tooth surface of the bevel gear in a gapless manner and has no tooth side gap, the tapered roller rolls along the tooth surface of the bevel gear, the change of the rotating speed of the mechanism is realized, and the transmission ratio of the mechanism is a fixed value;
when the bevel gear is a driving part, the tooth surface of the bevel gear pushes the conical roller to move, the conical roller drives the roller to rotate through the roller pin and the pin roll, the conical roller is meshed with the tooth surface of the bevel gear in a gapless mode, no tooth side gap exists, the conical roller rolls along the tooth surface of the bevel gear, the change of the rotating speed of the mechanism is achieved, and the transmission ratio of the mechanism is a fixed value.
The roller, the tapered roller, the bolt, the roller needle, the shaft, the fixing baffle and the positioning baffle form a combined roller, the roller needle eliminates sliding friction between the tapered roller and the roller, the tapered roller can rotate around a self geometric center line, the fixing baffle limits axial movement of the tapered roller, the fixing baffle and the roller limit axial movement of the roller needle, the positioning pin limits relative rotation between the positioning baffle and the roller, and the bolt limits relative movement between the positioning baffle, the roller and the fixing baffle.
When the point O and the rolling circle are on the same side of the plane of the base circle, the rolling circle rolls around the base circle, the included angle between the rolling circle and the base circle is a fixed value, and a part of curved surface formed by a generatrix on a conical surface formed by the point O and the short rolling circle in space is used as the theoretical tooth surface of the outer bevel gear; when the point O and the rolling circle are positioned at two sides of the plane of the base circle, the rolling circle rolls around the base circle, and a part of curved surface formed by a generatrix on a conical surface formed by the point O and the short rolling circle in the space is used as the theoretical tooth surface of the inner bevel gear.
The theoretical tooth surface equation of a single tooth of the bevel gear is
Wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 1 ,h 2 ]，h 1 、h 2 Is the value of delta h corresponding to the end face of the gear, is the value of delta h corresponding to the end face of the bevel gear, h 1 、h 2 As determined by the design requirements,θ∈[0,π]，θ 1 ∈[0,π/2)，according to tan (pi/Z) c ) = X (t, Δ h)/Y (t, Δ h) determination, m&gt, 0,f (Δ h, t) is a function related to Δ h, t.
The actual tooth surface of the bevel gear is an equiangular distance offset surface of a theoretical tooth surface, and the offset angular distance is theta b . The tapered roller is tangent to the actual tooth surface of the bevel gear and rolls along the actual tooth surface of the bevel gear.
When r + Rcos theta is greater than 0 and f (delta h, t) = t, the precision bevel gear transmission mechanism is a straight-tooth external meshing precision bevel gear transmission mechanism; when r + Rcos theta is less than 0 and f (delta h, t) = t, the precision bevel gear transmission mechanism is a straight-tooth internal-meshing precision bevel gear transmission mechanism; when r + Rcos theta is greater than 0 and f (delta h, t) is not equal to t, the precision bevel gear transmission mechanism is a bevel gear external meshing precision bevel gear transmission mechanism; when r + Rcos theta is less than 0 and f (delta h, t) is not equal to t, the precision bevel gear transmission mechanism is a bevel gear internal meshing precision bevel gear transmission mechanism.
The beneficial effects of the invention are: the precision bevel gear transmission mechanism can realize back clearance-free transmission and has high transmission precision; the transmission ratio is a fixed value; the tapered roller and the straight tooth surface roll only, and the tapered roller and the oblique tooth surface roll, so that the transmission efficiency is high; the structure is simple, the abrasion is small, the service life is long, the number of teeth participating in meshing is large, and the transmission is stable; the processing and the manufacturing are simple. The invention can be used as a speed reducer and a speed increaser; according to the difference of the included angle between the input shaft and the output shaft, different precise bevel gear transmission mechanisms can be designed to meet the transmission requirement.
Drawings
FIG. 1 is a schematic structural diagram of a straight-tooth external meshing precision bevel gear transmission mechanism;
FIG. 2 is a schematic diagram of a parameter labeling structure of a straight-tooth external meshing precision bevel gear transmission mechanism;
FIG. 3 is a schematic view of an outer bevel gear configuration;
FIG. 4 is a schematic view of a roller I;
FIG. 5 is a schematic view of a positioning baffle I;
FIG. 6 is a schematic view of a tapered roller configuration;
FIG. 7 is a schematic structural diagram of a straight-tooth internal-meshing precision bevel gear transmission mechanism;
FIG. 8 is a schematic view of the internal bevel gear configuration;
FIG. 9 is a schematic diagram of a parameter labeling structure of the inner bevel gear;
FIG. 10 is a schematic view of the bevel external gearing precision bevel gear drive;
fig. 11 is a schematic view of a helical internal-meshing precision bevel gear transmission mechanism.
In the above drawings: 1. a shell I, 2, an external bevel gear, 3, a key I, 4, a shaft I, 5, a bearing I, 6, a tapered roller I, 7, a roller I, 8, a roller I, 9, a roller II, 10, a pin shaft I, 11, a bolt I, 12, a fixed baffle I, 13, a positioning baffle I, 14, a positioning pin I, 15 keys II, 16, bearings II, 17, shafts II, 18, roller pins III, 19, roller pins IV, 20, a fixed baffle II, 21, keys III, 22, an internal bevel gear, 23, shafts III, 24, bearings III, 25, rollers II, 26, a tapered roller II, 27, bearings IV, 28, shafts IV, 29, keys IV, 30, bolts II, 31, positioning pins II, 32, pin shafts II, 33, positioning baffles II, 34, shells II, 35, helical external bevel gears, 36, helical tapered rollers I, 37, rollers III, 38, bolts III, 39, fixed baffles III, 40, positioning baffles III, 41, positioning pins III, 42, positioning baffles IV, 43, positioning pins IV, 44, bolts IV, 45, fixed baffles IV, 46, helical tapered rollers II, 47, rollers IV, 48 and helical internal bevel gears.
Detailed Description
The invention is described in detail below with reference to the figures and specific examples.
The invention has four specific embodiments:
1. a straight-tooth external-meshing precision bevel gear transmission mechanism is shown in figures 1-6 and comprises a shell I1, an external bevel gear 2, a key I3, a shaft I4, a bearing I5, a tapered roller I6, a roller I7, a roller I8, a roller II 9, a pin shaft I10, a bolt I11, a fixing baffle I12, a positioning baffle I13, a positioning pin I14, a key II 15, a bearing II 16 and a shaft II 17; roller I8 circumferentially and uniformly distributed Z g1 Hole, Z g1 Not less than 3; the outer bevel gears 2 are circumferentially and uniformly distributed Z c1 Tooth, Z c1 Not less than 3; the maximum base radius of the external bevel gear 2 is R 1 The maximum rolling circle radius of the roller I8 is r 1 ，m 1 ＝r 1 /R 1 The small end face of the tapered roller I6 is processed with a hole, the positioning baffle I13 is processed with a connecting hole, the positioning baffle I13 is processed with a positioning hole, the positioning baffle I13 is processed with a unthreaded hole, and the fixing baffle I12 is processed with a unthreaded hole。
Tapered roller I6 is through I7 hookup of kingpin I7 and gyro wheel I8, round pin axle I10 is installed in tapered roller I6 downthehole, round pin axle I10 is through II 9 hookups of kingpin and positioning baffle I13, tapered roller I6 can rotate around self geometric centre line, I14 of locating pin is installed at positioning baffle I13, in the I8 locating hole of gyro wheel, the relative rotation of I13 and gyro wheel I8 of restriction positioning baffle, bolt I11 is linked with I8 of gyro wheel, restriction positioning baffle I13, gyro wheel I8, locating pin I14, baffle I12 relative movement, the relation between the I6 figure of tapered roller and the 2 number of teeth of external bevel gear is Z g1 R＝Z c1 r，r/R＝m 1 ，m 1 &1, the rolling radius of the roller I8 is larger than the base radius of the outer bevel gear 2, 1>m 1 &When the speed is 0, the base radius of the outer bevel gear 2 is larger than the rolling radius of the roller I8, and m is 1 And when the radius is not less than 1, the radius of the rolling circle of the roller I8 is equal to the radius of the base circle of the outer bevel gear 2.
The conical surface of the tapered roller I6 is tangent to the tooth surface of the outer bevel gear 2.
When the roller I8 is a driving wheel, the roller I8 drives the tapered roller I6 to move through the roller I7, the roller II 9 and the pin shaft I10, the tapered roller I6 pushes the outer bevel gear 2 to rotate, the tooth surfaces of the tapered roller I6 and the outer bevel gear 2 are in zero-clearance engagement and have no tooth side clearance, the tapered roller I6 rolls along the tooth surface of the outer bevel gear 2, the change of the rotating speed of the mechanism is realized, and the transmission ratio of the mechanism is a fixed value.
When the outer bevel gear 2 is an active part, the tooth surface of the outer bevel gear 2 pushes the tapered roller I6 to move, the roller I6 drives the roller I8 to rotate through the roller I7, the roller II 9 and the pin shaft I10, the tooth surface of the tapered roller I6 is meshed with the tooth surface of the outer bevel gear 2 in a gapless mode, no tooth side gap exists, the tapered roller I6 rolls along the tooth surface of the outer bevel gear 2, the rotating speed of the mechanism is changed, and the transmission ratio of the mechanism is a fixed value.
The theoretical tooth surface equation of a single tooth of the outer bevel gear 2 is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 1 ,h 2 ]，h 1 、h 2 Is the value of delta h corresponding to the end surface of the outer bevel gear 2, according to tan (pi/Z) c ) = X (t, Δ h)/Y (t, Δ h) determination, θ 1 ∈[0,π/2)，θ∈[0,π]，K 1 Is a short amplitude coefficient, K 1 ∈(0,1]，f(Δh,t)＝t。
The actual tooth surface of the outer bevel gear 2 is an equiangular distance offset surface of the theoretical tooth surface.
Example 1:
fig. 1 shows a specific embodiment of a straight-tooth external-meshing precision bevel gear transmission mechanism disclosed by the invention, 10 holes are uniformly distributed in the circumferential direction of a roller I8, 4 positioning holes are processed in the roller I8, 10 teeth are uniformly distributed in the circumferential direction of an outer bevel gear 2, the maximum base circle radius is 40mm, the maximum rolling circle radius is 40mm, m =1, K =0.95, and holes are processed in the small end face of a tapered roller I6.
Location baffle I13 processing has 10 hookup holes, and location baffle I13 processing has 4 locating holes, and location baffle I13 processing has 1 unthreaded hole.
The tapered roller I6 is connected with the roller I8 through a roller pin I7, the pin shaft I10 is installed in the hole of the tapered roller I6, the pin shaft I10 is connected with the positioning baffle I13 through a roller pin II 9, and the tapered roller I6 can rotate around the geometric center line of the tapered roller.
Locating pin I14 is installed in locating baffle I13, I8 locating hole of gyro wheel, and the relative rotation of restriction locating baffle I13 and gyro wheel I8.
Bolt I11 and I8 hookups of gyro wheel restrict location baffle I13, I8 of gyro wheel, locating pin I14, I12 relative movement of baffle.
The conical surface of the tapered roller I6 is tangent to the tooth surface of the outer bevel gear 2.
Combination gyro wheel is constituteed to gyro wheel I8, kingpin I7, tapered roller I6, kingpin II 9, round pin axle I10, bolt I11, baffle I12, location baffle I13, locating pin I14.
When axle I4 was as the input, axle I4 passed through key I3 and drives outer bevel gear 2 and rotate, and 2 tooth promotion tapered roller I6 of outer bevel gear, tapered roller I6 are along the pure roll of 2 flank of tooth of outer bevel gear, and the combination gyro wheel passes through key II 15 and drives axle II 17 and rotate, and the drive ratio is definite value i =1.
The theoretical tooth surface equation of the outer bevel gear 2 is
Wherein T = sin θ/(m + cos θ), θ = π/2, Δ h ∈ [0,10 ∈ ]]， According to tan (pi/Z) c ) = X (t, Δ h)/Y (t, Δ h), f (Δ h, t) = t.
The actual tooth surface of the outer bevel gear 2 is an equiangular distance offset surface of a theoretical tooth surface.
2. A straight-tooth internal-meshing precise bevel gear transmission mechanism is shown in figures 7-9 and comprises a roller pin III 18, a roller pin IV 19, a fixed baffle II 20, a key III 21, an internal bevel gear 22, a shaft III 23, a bearing III 24, a roller II 25, a tapered roller II 26, a bearing IV 27, a shaft IV 28, a key IV 29, a bolt II 30, a positioning pin II 31, a pin shaft II 32, a positioning baffle II 33 and a shell II 34; roller II 25 is circumferentially and uniformly distributed Z g2 Hole, Z g2 Not less than 3; the inner bevel gears 22 are circumferentially and uniformly distributed Z c2 Tooth, Z c2 Not less than 3; the maximum base radius of the inner bevel gear 22 is R 2 The maximum rolling radius of the roller II 25 is r 2 Short amplitude coefficient K 2 The small end face of the tapered roller II 26 is provided with a hole, and the positioning baffle II 33 is provided with a linkAnd the positioning baffle II 33 is provided with a positioning hole, the positioning baffle II 33 is provided with a unthreaded hole, and the fixing baffle II 20 is provided with a unthreaded hole.
Tapered roller I6 is through I7 hookup of kingpin I7 and gyro wheel I8, round pin axle I10 is installed in tapered roller I6 downthehole, round pin axle I10 is through II 9 hookups of kingpin I13, tapered roller I6 can rotate around self geometric centre line, locating pin I14 is installed at locating baffle I13, in the I8 locating hole of gyro wheel, the relative rotation of restriction locating baffle I13 and gyro wheel I8, bolt I11 is linked with I8 of gyro wheel, restriction locating baffle I13, gyro wheel I8, locating pin I14, baffle I12 relative movement, the relation between II 26 figure of tapered roller and the 22 tooth counts of interior bevel gear is Z g2 R 2 ＝Z c2 r 2 ，m 2 ＝r 2 /R 2 ，m 2 &1, the rolling radius of the roller II 25 is larger than the base radius of the inner bevel gear 22, 1>m 2 &When the speed is 0, the base radius of the inner bevel gear 22 is larger than the rolling radius of the roller II 25, m 2 And if the gear is 1, the rolling radius of the roller II 25 is equal to the base radius of the inner bevel gear 22.
The conical surface of the tapered roller II 26 is tangent to the tooth surface of the inner bevel gear 22.
When the inner bevel gear 22 is a driving part, the tooth surface of the inner bevel gear 22 pushes the tapered roller II 26 to move, the tapered roller II 26 drives the roller II 25 to rotate through the roller III 18, the roller IV 19 and the pin shaft II 32, the tapered roller II 26 is meshed with the tooth surface of the inner bevel gear 22 in a gapless mode, no tooth side gap exists, the tapered roller II 26 rolls on the tooth surface of the inner bevel gear 22 purely, and the mechanism transmission ratio is a fixed value.
When the roller II 25 is a driving part, the roller II 25 drives the tapered roller II 26 to move through the roller III 18, the roller IV 19 and the pin shaft II 32, the tapered roller II 26 pushes the inner bevel gear 22 to rotate, the tapered roller II 26 is meshed with the tooth surface of the inner bevel gear 22 in a gapless mode, no tooth side gap exists, the tapered roller II 26 rolls on the tooth surface of the inner bevel gear 22, and the mechanism transmission ratio is a fixed value.
The theoretical tooth surface equation of a single tooth of the inner bevel gear 22 is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 3 ,h 4 ]h 3 、h 4 The value of deltah corresponding to the end surface of the internal bevel gear 22, according to tan (π/Z) c ) = X (t, Δ h)/Y (t, Δ h) determination, θ 1 ∈[0，π/2)，θ∈[π/2,π]，f(Δh,t)＝t。
The actual tooth surface of the inside bevel gear 22 is an equiangular-distance offset surface of the theoretical tooth surface.
Example 2:
fig. 7 shows a specific embodiment of the straight-tooth internal-meshing precision bevel gear transmission mechanism disclosed by the invention, wherein 10 holes are uniformly distributed in the circumferential direction of the roller ii 25, 4 positioning holes are processed in the roller ii 25, 20 teeth are uniformly distributed in the circumferential direction of the inner bevel gear 22, the maximum base circle radius is 40mm, the maximum rolling circle radius is 20mm, m =0.5, k =0.9, and holes are processed in the small end face of the tapered roller ii 26.
Positioning baffle II 33 processing has 10 hookup holes, and II 33 processing of fixed stop has 4 locating holes, and II 33 processing of positioning baffle has 1 unthreaded hole.
The tapered roller II 26 is connected with the roller II 25 through the roller pin III 18, the pin shaft II 32 is installed in a hole of the tapered roller II 26, the pin shaft II 32 is connected with the positioning baffle II 33 through the roller pin III 19, and the tapered roller II 26 can rotate around the geometric center line of the tapered roller II.
And the positioning pin II 31 is arranged in the positioning holes of the fixed baffle II 20 and the roller II 25 and used for limiting the relative rotation of the fixed baffle II 20 and the roller II 25.
And the bolt II 30 is connected with the roller II 25 to limit the relative movement of the fixed baffle II 20, the roller II 25, the positioning pin II 31 and the positioning baffle I33.
The conical surface of the tapered roller II 26 is tangent to the tooth surface of the inner bevel gear 22.
And a roller II 25, a roller III 18, a tapered roller II 26, a roller IV 19, a pin shaft II 25, a bolt II 30, a positioning baffle II 33, a fixing baffle II 20 and a positioning pin II 31 form a combined roller.
When the shaft III 23 is used as an input end, the shaft III 23 drives the inner bevel gear 22 to rotate through the key III 21, the teeth of the inner bevel gear 22 push the tapered roller II 26, the tapered roller II 26 rolls along the tooth surface of the inner bevel gear 22, the combined roller rotates, the combined roller drives the shaft IV 28 to rotate through the key IV 29, and the transmission ratio is a fixed value i =2.
The theoretical tooth surface equation of the inner bevel gear 22 is
Wherein T = sin θ/(m + cos θ), θ =3 π/4, Δ h ∈ [ -10,0]， According to tan (pi/Z) c ) X (t, Δ h)/Y (t, Δ h) and f (Δ h, t) = t.
The actual tooth surface of the internal bevel gear 22 is an equiangular offset surface of the theoretical tooth surface.
3. The bevel gear external meshing precision bevel gear transmission mechanism comprises a bevel gear external bevel gear 35, a bevel tapered roller I36, a roller III 37, a bolt III 38, a fixed baffle III 39, a positioning baffle III 40 and a positioning pin III 41, as shown in figure 10; a plurality of holes are formed in the roller III 37, the same number of holes are formed in the positioning baffle III 40, oblique tapered rollers I36 are installed in the holes, a plurality of oblique teeth are formed in the oblique-tooth outer bevel gear 35, and the tooth surfaces of the oblique tapered rollers I36 and the oblique-tooth outer bevel gear 35 are tangent.
A large end face shaft of the oblique tapered roller I36 is arranged in a roller III 37 hole, a small end face shaft of the oblique tapered roller I36 is arranged in a positioning baffle III 40 hole, the roller III 37 is connected with the positioning baffle III 40 through a positioning pin III 41, the roller III 37 does not rotate relative to the positioning baffle III 40, the axial degree of freedom of the positioning pin III 41 is eliminated by a fixed baffle III 39, and the fixed baffle III 39 is fixed on the end face of the positioning baffle III 40 through a bolt III 38.
The roller III 37 is a driving part, the roller III 37 drives the positioning baffle plate III 40 to rotate through the positioning pin III 41, the roller III 37 and the positioning baffle plate III 40 drive the oblique tapered roller I36 to move, the oblique tapered roller I36 is meshed with the tooth surface of the oblique tooth outer bevel gear 35 in a gapless mode, no tooth side gap exists, the oblique tapered roller I36 pushes the oblique tooth outer bevel gear 35 to rotate, rotation speed change is achieved, and the transmission ratio is a fixed value.
The helical outer bevel gear 35 is a driving part, the tooth surface of the helical outer bevel gear 35 is meshed with the helical tapered roller I36, the helical tapered roller I36 drives the roller III 37 to rotate, rotation speed change is achieved, and the transmission ratio is a fixed value.
The theoretical tooth surface equation of a single tooth of the helical outer bevel gear is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 5 ,h 6 ]，h 5 、h 6 Is the delta h value corresponding to the end surface of the helical outer bevel gear 35, according to tan (pi/Z) c ) = X (t, 0)/Y (t, 0) determination, θ 1 ∈[0,π/2)，θ∈[0,π]，m&gt, 0,f (Δ h, t) is a function of Δ h, t.
The actual tooth surface of the helical outer bevel gear 35 is an equiangular distance offset surface of the theoretical tooth surface.
Example 3:
fig. 10 shows an embodiment of the bevel gear external-meshing precision bevel gear transmission mechanism disclosed by the invention, wherein 10 holes are formed in a roller iii 37, 10 holes are formed in a positioning baffle iii 40, a bevel tapered roller i 36 is installed in each hole, 10 helical teeth are formed in a bevel outer bevel gear 35, the bevel tapered roller i 36 is tangent to the tooth surface of the bevel outer bevel gear 35, the maximum base circle radius is 40mm, the maximum rolling circle radius is 40mm, m =1, and k =0.95.
The helical tooth external meshing precision bevel gear transmission mechanism operates, the helical tapered roller I36 is in zero-clearance meshing with the tooth surface of the helical tooth external bevel gear 35, and the transmission ratio is a fixed value.
The theoretical tooth surface equation of a single tooth of the helical outer bevel gear is
Wherein T = sin θ/(m + cos θ), θ = π/2, Δ h ∈ [ h ] 1 ,h 2 ]，h 1 ＝0，h 2 ＝10mm， According to tan (pi/Z) c ) Definitionsf (Δ h, t) = pi Δ h/(12 h) X (t, 0)/Y (t, 0) 2 )+t。
The actual tooth surface of the helical outer bevel gear 35 is an equiangular offset surface of the theoretical tooth surface.
4. The bevel-tooth internal-meshing precise bevel gear transmission mechanism comprises a positioning baffle plate IV 42, a positioning pin IV 43, a bolt IV 44, a fixed baffle plate IV 45, a bevel tapered roller II 46, a roller IV 47 and a bevel-tooth internal bevel gear 48, as shown in FIG. 11; a plurality of holes are formed in the roller IV 47, the same number of holes are formed in the positioning baffle IV 42, the tapered roller II 46 is installed in the holes, and the tooth surface of the tapered roller II 46 is tangent to the tooth surface of the tapered-tooth internal bevel gear 48.
The large end shaft of the oblique tapered roller II 46 is arranged in a roller IV 47 hole, the small end shaft of the oblique tapered roller II 46 is arranged in a positioning baffle IV 42, a positioning pin IV 43 is arranged in the positioning baffle IV 42 and the roller IV 47 hole, the positioning pin IV 43 eliminates the relative rotation of the positioning baffle IV 42 and the roller IV 47, and a bolt IV 44 eliminates the relative movement among a fixed baffle IV 45, the positioning baffle IV 42 and the roller IV 47.
The roller IV 47 is a driving part, the roller IV 47 drives the positioning baffle IV 42 to rotate through the positioning pin IV 43, the positioning baffle IV 42 and the roller IV 47 drive the oblique tapered roller II 46 to move, the oblique tapered roller II 46 and the tooth surface of the oblique-tooth inner bevel gear 48 are meshed without a gap and have no tooth side gap, the oblique tapered roller II 46 pushes the oblique-tooth inner bevel gear 48 to rotate, the change of the rotating speed is realized, and the transmission ratio is a fixed value.
The bevel-tooth inner bevel gear 48 is a driving part, the tooth surface of the bevel-tooth inner bevel gear 48 is meshed with the bevel tapered roller II 46 in a gapless mode, no tooth side gap exists, the bevel-tooth inner bevel gear 48 pushes the bevel tapered roller II 46 to move, the bevel tapered roller II 46 drives the roller IV 47 to rotate, the change of the rotating speed is achieved, and the transmission ratio is a fixed value.
The theoretical tooth surface equation of a single tooth of the bevel internal bevel gear is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 7 ,h 8 ]，h 7 、h 8 Is the delta h value corresponding to the end surface of the bevel internal bevel gear 48, according to tan (pi/Z) c ) = X (t, 0)/Y (t, 0) determination, θ 1 ∈[0,π/2)，θ∈[π/2,π]，m&gt, 0,f (Δ h, t) is a function related to Δ h, t.
The actual tooth surface of the bevel internal bevel gear 48 is an equiangular offset surface of the theoretical tooth surface.
Example 4:
fig. 11 shows an embodiment of the bevel-intermeshing precision bevel gear transmission according to the present invention, in which 10 holes are formed in a roller iv 47, 10 holes are formed in a positioning fence iv 42, and tapered rollers ii 46 are mounted in the holes, and the tapered rollers ii 46 are tangent to the tooth surface of a tapered-toothed internal bevel gear 48, and have a maximum base radius of 40mm, a maximum rolling radius of 20mm, m =0.5, and k =0.9.
The helical-tooth internal-meshing precise bevel gear transmission mechanism operates, and the helical tapered roller II 46 is meshed with the tooth surface of the helical-tooth internal bevel gear 48 in a gapless manner.
The theoretical tooth surface equation of a single tooth of the bevel internal bevel gear is
Wherein T = sin θ/(m + cos θ), θ =3 π/4, Δ h ∈ [ -10,0]， According to tan (pi/Z) c ) Definitionsf (Δ h, t) = pi Δ h/(12 h) X (t, 0)/Y (t, 0) 2 )+t。
The actual tooth surface of the bevel internal bevel gear 48 is an equiangular offset surface of the theoretical tooth surface.

Claims (8)

1. Straight-tooth external toothing precision bevel gear drive mechanism, its characterized in that: the device comprises a shell I (1), an outer bevel gear (2), a key I (3), a shaft I (4), a bearing I (5), a tapered roller I (6), a roller pin I (7), a roller I (8), a roller pin II (9), a pin shaft I (10), a bolt I (11), a fixing baffle I (12), a positioning baffle I (13), a positioning pin I (14), a key II (15), a bearing II (16) and a shaft II (17); the method is characterized in that: the rollers I (8) are circumferentially and uniformly distributed Z g1 Hole, Z g1 Not less than 3; the outer bevel gears (2) are circumferentially and uniformly distributed with Z c1 Tooth, Z c1 Not less than 3; the maximum base circle radius of the external bevel gear (2) is R 1 Maximum radius of rolling wheel I (8)Is r 1 ，m 1 ＝r 1 /R 1 The small end face of the tapered roller I (6) is provided with a hole, the positioning baffle I (13) is provided with a connecting hole, the positioning baffle I (13) is provided with a positioning hole, the positioning baffle I (13) is provided with a unthreaded hole, and the fixing baffle I (12) is provided with a unthreaded hole;
tapered roller I (6) is connected with roller I (8) through roller I (7), pin shaft I (10) is installed in tapered roller I (6) hole, pin shaft I (10) is connected with positioning baffle I (13) through roller II (9), tapered roller I (6) can rotate around the geometric center line of self, positioning pin I (14) is installed in positioning baffle I (13), roller I (8) positioning hole, relative rotation of positioning baffle I (13) and roller I (8) is limited, bolt I (11) is connected with roller I (8), positioning baffle I (13) is limited, roller I (8), positioning pin I (14), baffle I (12) moves relatively, the relation between the number of tapered roller I (6) and the number of teeth of outer bevel gear (2) is Z g1 R＝Z c1 r，r/R＝m 1 ，m 1 &When the gear ratio is 1, the rolling radius of the roller I (8) is larger than the base radius of the outer bevel gear (2) by 1>m 1 &When the gear ratio is 0, the base radius of the outer bevel gear (2) is larger than the rolling radius of the roller I (8), and m is 1 When the radius is not less than 1, the radius of the rolling circle of the roller I (8) is equal to the radius of the base circle of the outer bevel gear (2);
the conical surface of the tapered roller I (6) is tangent to the tooth surface of the outer bevel gear (2);
when the roller I (8) is a driving wheel, the roller I (8) drives the tapered roller I (6) to move through the roller I (7), the roller II (9) and the pin shaft I (10), the tapered roller I (6) pushes the outer bevel gear (2) to rotate, the tapered roller I (6) is meshed with the tooth surface of the outer bevel gear (2) in a gapless mode, no tooth side gap exists, the tapered roller I (6) rolls along the tooth surface of the outer bevel gear (2) in a pure rolling mode, the change of the rotating speed of the mechanism is achieved, and the transmission ratio of the mechanism is a fixed value;
when outer bevel gear (2) is the driving part, outer bevel gear (2) flank of tooth promotes tapered roller I (6) motion, tapered roller I (6) drive gyro wheel I (8) through I (7), II (9) of kingpin and round pin axle I (10) and rotate, tapered roller I (6) and outer bevel gear (2) flank of tooth zero clearance meshing, no tooth side clearance, tapered roller I (6) are along outer bevel gear (2) flank of tooth pure roll, the change of rotational speed is realized to the mechanism, mechanism drive ratio is the definite value.
2. The spur external toothing precision bevel gear transmission of claim 1, characterized in that: the theoretical tooth surface equation of a single tooth of the outer bevel gear (2) is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 1 ,h 2 ]，h 1 、h 2 Is a delta h value corresponding to the end surface of the outer bevel gear (2), according to tan (pi/Z) c ) = X (t, Δ h)/Y (t, Δ h) determination, θ 1 ∈[0,π/2)，θ∈[0,π]，K 1 Is a short amplitude coefficient, K 1 ∈(0,1]F (Δ h, t) = t; the actual tooth surface of the outer bevel gear (2) is an equiangular distance offset surface of a theoretical tooth surface.
3. The straight-tooth internal-meshing precise bevel gear transmission mechanism is characterized in that: the novel roller pin structure comprises a roller pin III (18), a roller pin IV (19), a fixed baffle II (20), a key III (21), an inner bevel gear (22), a shaft III (23), a bearing III (24), a roller II (25), a tapered roller II (26), a bearing IV (27), a shaft IV (28), a key IV (29), a bolt II (30), a positioning pin II (31), a pin shaft II (32), a positioning baffle II (33) and a shell II (34); the rollers II (25) are circumferentially and uniformly distributed Z g2 Hole, Z g2 Not less than 3; the inner bevel gears (22) are circumferentially and uniformly distributed with Z c2 Tooth, Z c2 Not less than 3; the maximum base circle radius of the inner cone gear (22) is R 2 The maximum rolling circle radius of the roller II (25) is r 2 Coefficient of shortwave K 2 The small end face of the tapered roller II (26) is provided with a hole, the positioning baffle II (33) is provided with a connecting hole, the positioning baffle II (33) is provided with a positioning hole, the positioning baffle II (33) is provided with a unthreaded hole, and the fixing baffle II(20) Processing a unthreaded hole;
tapered roller I (6) is connected with roller I (8) through roller I (7), pin shaft I (10) is installed in tapered roller I (6) hole, pin shaft I (10) is connected with positioning baffle I (13) through roller II (9), tapered roller I (6) can rotate around the geometric center line of self, positioning pin I (14) is installed in positioning baffle I (13) and roller I (8) positioning hole, relative rotation of positioning baffle I (13) and roller I (8) is limited, bolt I (11) is connected with roller I (8), positioning baffle I (13) is limited, roller I (8), positioning pin I (14) and baffle I (12) move relatively, the relation between the number of tapered roller II (26) and the number of teeth of inner bevel gear (22) is Z g2 R 2 ＝Z c2 r 2 ，m 2 ＝r 2 /R 2 ，m 2 &When the gear ratio is 1, the rolling radius of the roller II (25) is larger than the base radius of the inner bevel gear (22), 1>m 2 &When the gear ratio is 0, the base radius of the inner bevel gear (22) is larger than the rolling radius of the roller II (25), and m is 2 When the radius is 1, the rolling radius of the roller II (25) is equal to the base radius of the inner bevel gear (22);
the conical surface of the tapered roller II (26) is tangent to the tooth surface of the inner bevel gear (22);
when the inner bevel gear (22) is a driving part, the tooth surface of the inner bevel gear (22) pushes the tapered roller II (26) to move, the tapered roller II (26) drives the roller II (25) to rotate through the roller III (18), the roller IV (19) and the pin shaft II (32), the tapered roller II (26) is meshed with the tooth surface of the inner bevel gear (22) in a gapless mode and has no tooth side gap, the tapered roller II (26) rolls on the tooth surface of the inner bevel gear (22) in a pure rolling mode, and the mechanism transmission ratio is a fixed value;
when the roller II (25) is a driving part, the roller II (25) drives the tapered roller II (26) to move through the roller III (18), the roller IV (19) and the pin shaft II (32), the tapered roller II (26) pushes the inner bevel gear (22) to rotate, the tapered roller II (26) is meshed with the tooth surface of the inner bevel gear (22) in a zero-clearance mode, no tooth side clearance exists, the tapered roller II (26) rolls on the tooth surface of the inner bevel gear (22) in a pure rolling mode, and the mechanism transmission ratio is a fixed value.
4. The spur external toothing precision bevel gear transmission of claim 3, characterized in that: the theoretical tooth surface equation of a single tooth of the inner bevel gear (22) is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 3 ,h 4 ]h 3 、h 4 Is a delta h value corresponding to the end surface of the inner bevel gear (22), according to tan (pi/Z) c ) = X (t, Δ h)/Y (t, Δ h) determination, θ 1 ∈[0，π/2)，θ∈[π/2,π]F (Δ h, t) = t; the actual tooth surface of the inner bevel gear (22) is an equal angular distance offset surface of a theoretical tooth surface.
5. The bevel gear external meshing precision bevel gear transmission mechanism is characterized in that: the bevel gear mechanism comprises a bevel gear (35), a bevel tapered roller I (36), a roller III (37), a bolt III (38), a fixed baffle III (39), a positioning baffle III (40) and a positioning pin III (41); a plurality of holes are processed in the roller III (37), the same number of holes are processed in the positioning baffle III (40), oblique tapered rollers I (36) are installed in the holes, a plurality of oblique teeth are processed in the oblique-tooth outer bevel gear (35), and the oblique tapered rollers I (36) are tangent to the tooth surface of the oblique-tooth outer bevel gear (35);
the large end face shaft of the tapered roller I (36) is arranged in the hole of the roller III (37), the small end face shaft of the tapered roller I (36) is arranged in the hole of the positioning baffle plate III (40), the roller III (37) is connected with the positioning baffle plate III (40) through a positioning pin III (41), the roller III (37) and the positioning baffle plate III (40) do not rotate relatively, the axial freedom degree of the positioning pin III (41) is eliminated by the fixing baffle plate III (39), and the fixing baffle plate III (39) is fixed on the end face of the positioning baffle plate III (40) through a bolt III (38);
the roller III (37) is a driving part, the roller III (37) drives the positioning baffle plate III (40) to rotate through the positioning pin III (41), the roller III (37) and the positioning baffle plate III (40) drive the oblique tapered roller I (36) to move, the oblique tapered roller I (36) is meshed with the tooth surface of the oblique tooth outer bevel gear (35) in a gapless mode, no tooth side gap exists, the oblique tapered roller I (36) pushes the oblique tooth outer bevel gear (35) to rotate, rotation speed change is achieved, and the transmission ratio is a fixed value;
the helical outer bevel gear (35) is a driving part, the tooth surface of the helical outer bevel gear (35) is meshed with the helical tapered roller I (36), the helical tapered roller I (36) drives the roller III (37) to rotate, rotation speed change is achieved, and the transmission ratio is a fixed value.
6. The bevel external engagement precision bevel gear transmission of claim 5 wherein: the theoretical tooth surface equation of a single tooth of the helical outer bevel gear is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 5 ,h 6 ]，h 5 、h 6 Is a delta h value corresponding to the end surface of the helical outer bevel gear (35), according to tan (pi/Z) c ) = X (t, 0)/Y (t, 0) determination, θ 1 ∈[0,π/2)，θ∈[0,π]，m&0,f (Δ h, t) is a function related to Δ h, t;
the actual tooth surface of the helical outer bevel gear (35) is an equal angular distance offset surface of a theoretical tooth surface.
7. The bevel gear inner meshing precise bevel gear transmission mechanism is characterized in that: the device comprises a positioning baffle IV (42), a positioning pin IV (43), a bolt IV (44), a fixed baffle IV (45), a tapered roller II (46), a roller IV (47) and a bevel gear (48); a plurality of holes are formed in the roller IV (47), the positioning baffle IV (42) is provided with the same number of holes, oblique tapered rollers II (46) are installed in the holes, and the oblique tapered rollers II (46) are tangent to the tooth surfaces of the oblique-tooth internal bevel gears (48);
the large end shaft of the oblique tapered roller II (46) is arranged in a roller IV (47) hole, the small end shaft of the oblique tapered roller II (46) is arranged in a positioning baffle IV (42), a positioning pin IV (43) is arranged in the positioning baffle IV (42) and the roller IV (47) hole, the positioning pin IV (43) eliminates the relative rotation of the positioning baffle IV (42) and the roller IV (47), and a bolt IV (44) eliminates the relative movement among a fixed baffle IV (45), the positioning baffle IV (42) and the roller IV (47);
the roller IV (47) is a driving part, the roller IV (47) drives the positioning baffle IV (42) to rotate through the positioning pin IV (43), the positioning baffle IV (42) and the roller IV (47) drive the oblique tapered roller II (46) to move, the oblique tapered roller II (46) is meshed with the tooth surface of the oblique tooth inner bevel gear (48) in a gapless mode, no tooth side gap exists, the oblique tapered roller II (46) pushes the oblique tooth inner bevel gear (48) to rotate, the change of the rotating speed is achieved, and the transmission ratio is a fixed value;
the bevel-tooth inner bevel gear (48) is a driving part, the tooth surface of the bevel-tooth inner bevel gear (48) is meshed with the bevel tapered roller II (46) in a gapless mode, no tooth side gap exists, the bevel-tooth inner bevel gear (48) pushes the bevel tapered roller II (46) to move, the bevel tapered roller II (46) drives the roller IV (47) to rotate, the rotating speed is changed, and the transmission ratio is a fixed value.
8. The bevel internal engagement precision bevel gear transmission of claim 7, wherein: the theoretical tooth surface equation of a single tooth of the bevel internal bevel gear is as follows:
wherein T = sin θ/(m + cos θ), Δ h ∈ [ h ] 7 ,h 8 ]，h 7 、h 8 Is a delta h value corresponding to the end surface of the bevel internal bevel gear (48), according to tan (pi/Z) c ) = X (t, 0)/Y (t, 0) trueTheta. Determining 1 ∈[0,π/2)，θ∈[π/2,π]，m&0,f (Δ h, t) is a function related to Δ h, t;
the actual tooth surface of the bevel inner bevel gear (48) is an equal angular distance offset surface of a theoretical tooth surface.
CN201710844835.9A 2017-09-19 2017-09-19 The outer/inner engagement of straight-tooth, the outer/inner accurate bevel gear transmission of engagement of helical teeth Pending CN107701705A (en)

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JPH0835554A (en) * 1991-06-18 1996-02-06 Masahisa Miura Gear with bearing
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CN2427673Y (en) * 2000-06-23 2001-04-25 张进才 Rolling column active toothed wheel gearing device
CN102678880A (en) * 2011-03-08 2012-09-19 苏州晓宇宙齿条科技有限公司 Processing method and matching gear wheel of ultrahigh-precision complex curve rack
CN103697115A (en) * 2013-11-28 2014-04-02 江苏泰隆减速机股份有限公司 Dual-reduction ratio and dual-output speed reducer
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CN112777266A (en) * 2021-02-05 2021-05-11 淮北合众机械设备有限公司 Roller type sweeper capable of aligning
CN112777266B (en) * 2021-02-05 2022-08-26 淮北合众机械设备有限公司 Roller type sweeper capable of aligning

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Application publication date: 20180216