CN108626315B - Dotted line meshing worm lifting mechanism - Google Patents
Dotted line meshing worm lifting mechanism Download PDFInfo
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- CN108626315B CN108626315B CN201810558390.2A CN201810558390A CN108626315B CN 108626315 B CN108626315 B CN 108626315B CN 201810558390 A CN201810558390 A CN 201810558390A CN 108626315 B CN108626315 B CN 108626315B
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Classifications
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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
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
- F16H1/206—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members characterised by the driving or driven member being composed of two or more gear wheels
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/14—Power transmissions between power sources and drums or barrels
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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
- F16H55/0806—Involute profile
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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
- F16H55/0826—Novikov-Wildhaber profile
-
- 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
-
- 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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gears, Cams (AREA)
- Gear Transmission (AREA)
Abstract
The invention relates to the technical field of mechanical transmission, in particular to a dotted line meshing worm lifting mechanism. The tooth shapes of the worm and the worm wheel and the gear in the invention have involute and circular arcs, namely, half of the tooth height of the gear teeth is an involute convex tooth profile, the other half is a concave tooth profile of a transition curve, and when the worm and the worm wheel are in operation, different tooth profile curves are meshed to present different meshing effects. When the transition curve tooth profile is meshed with the involute tooth profile, the transition curve tooth profile is in point contact; when the involute profile meshes with the involute profile, the involute profile exhibits line contact. The invention is characterized in that: 1) The dotted line meshing of the gears is promoted to the dotted line meshing of the worm and the worm wheel, so that a theoretical system of the dotted line meshing of the gears is further enriched, and the application range of worm transmission is widened. 2) The worm is meshed with the dotted line of the bevel gear, so that the processing difficulty is reduced, and the connotation and the extension of worm transmission are expanded. 3) The dotted line meshed worm gear has the double advantages of an involute worm gear and an arc worm gear, and the strength is higher.
Description
Technical Field
The invention relates to the technical field of mechanical transmission, in particular to a dotted line meshing worm lifting mechanism.
Background
Worm drive is widely used because of its advantages of large drive ratio, stable drive, small vibration, low noise, etc. The quality of worm drive performance and the quality thereof ultimately affect the quality of machine products.
Failure modes of worm drive are often manifested as tooth surface pitting, gluing, tooth surface wear, tooth breakage, and the like. For material and structural reasons, the strength of the worm screw tooth portion is always higher than the strength of the worm gear teeth, so that failure often occurs on the worm gear teeth.
Disclosure of Invention
In order to solve the problem that the gear teeth of the worm wheel or the bevel gear are easy to fail when the worm wheel or the bevel gear is matched with the worm in the prior art, the invention provides a dotted line meshing worm lifting mechanism capable of improving the bending strength of the tooth root of the worm wheel or the bevel gear.
The technical scheme adopted for solving the technical problems is as follows:
the utility model provides a dotted line meshing worm hoist mechanism, includes intermeshing's first helical gear and second helical gear, second helical gear center be fixed with first connecting axle, the other end of first connecting axle be fixed with first bevel gear, first bevel gear on the meshing have second bevel gear, second bevel gear on be fixed with the second connecting axle, the other end of second connecting axle be fixed with the worm, the worm on the meshing have the drive wheel, the drive wheel be worm wheel or third helical gear, the drive wheel on be fixed with the third connecting axle, the third connecting axle on be fixed with the fourth helical gear, the fourth helical gear on the meshing have the fifth helical gear, the fifth helical gear terminal surface on be fixed with the cylinder, and the axis of revolution coincidence of cylinder and fifth helical gear, the cylinder on twine have the haulage rope that makes the heavy object promote or descend, hoist mechanism need satisfy following condition:
1) Taking the number of teeth, normal surface modulus, end surface modulus, normal surface pressure angle, end surface pressure angle and pitch angle of the first helical gear and the second helical gear to be z respectively 1 、z 2 、m n1 、m n2 、m t1 、m t2 、α n1 、α n2 、α t1 、α t2 、β 1 、β 2 Wherein z is 1 、z 2 The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root; beta 1 、β 2 Usually takes 8-20 degrees and satisfies beta 1 ＝β 2 ；m n1 、m n2 、α n1 、α n2 The values can be self-defined or can be taken from a gear manual according to the requirements, but the requirements must be satisfied: m is m n1 cosα t1 /cosβ 1 ＝m n2 cosα t2 /cosβ 2 ，α t1 ＝arctg(tgα n1 /cosβ 1 )，α t2 ＝arctg(tgα n2 /cosβ 2 )；
2) Taking the number of teeth, the modulus of the big end and the pressure angle of the big end of the first conical gear and the second conical gear to be z respectively 3 、z 4 、m 3 、m 4 、α 3 、α 4 Wherein z is 3 、z 4 The value of (2) is not satisfiedUnder the condition of undercut, the cutting machine can be self-determined according to the requirement; m is m 3 、m 4 、α 3 、α 4 Can be self-determined or take values from a gear manual as required, but must satisfy m 3 cosα 3 ＝m 4 cosα 4 ；
3) Taking the number of heads, the diameter coefficient, the axial surface modulus and the axial surface pressure angle of the worm to be z respectively 5 、q 5 、m x5 、α x5 Wherein z is 5 Typically 1, 2, 4, 6; q 5 The value of (2) can refer to a gear design manual; m is m x5 、α x5 The value can be self-determined or can be taken from a gear manual according to the requirement, but the specific value is related to the end face modulus and the end face pressure angle of the driving wheel (6); pitch circle lead angle gamma of worm 5 ＝arctanz 5 /q 5 A degree;
4) Taking the number of teeth, pitch angle, end surface modulus and end surface pressure angle of a driving wheel to be z respectively 6 、β 6 、m t6 、α t6 When the driving wheel is a worm wheel, z 6 The value range of (2) is usually 28-80; when the driving wheel is a third bevel gear, z 6 The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root; beta 6 Can be self-determined according to the needs; m is m t6 、α t6 The values can be self-defined or can be taken from a gear manual according to the requirements, but the requirements must be satisfied: m is m x5 cosα x5 ＝m t6 cosα t6 And alpha is x5 ＜α t6 . Under the condition that the included angle between the worm and the two shafts of the driving wheel is 90 degrees, beta is also satisfied 6 ＝γ 5 ；
5) Taking the number of teeth, normal surface modulus, end surface modulus, normal surface pressure angle, end surface pressure angle and pitch angle of the fourth helical gear and the fifth helical gear to be z respectively 7 、z 8 、m n7 、m n8 、m t7 、m t8 、α n7 、α n8 、α t7 、α t8 、β 7 、β 8 Wherein z is 7 、z 8 The value can be self-determined according to the need under the condition of meeting the condition of not cutting root; beta 7 、β 8 Usually takes 8-20 degrees and satisfies beta 7 ＝-β 8 ；m n7 、m n8 、α n7 、α n8 The values can be self-defined or can be taken from a gear manual according to the requirements, but the requirements must be satisfied: m is m n7 cosα t7 /cosβ 7 ＝m n8 cosα t8 /cosβ 8 ，α t7 ＝arctg(tgα n7 /cosβ 7 )，α t8 ＝arctg(tgα n8 /cosβ 8 )。
Further, the first bevel gear and the second bevel gear are internally meshed.
Further, the first bevel gear, the second bevel gear, the worm, the driving wheel, the fourth bevel gear and the fifth bevel gear are provided with tooth profiles of teeth of the involute, and half of the tooth profiles are provided with convex tooth profiles of transition curve tooth profiles.
The beneficial effects are that:
1) The dotted line meshing of the gears is promoted to the dotted line meshing of the worm and the worm wheel, so that a theoretical system of the dotted line meshing of the gears is further enriched, and the application range of worm transmission is widened; 2) The worm is meshed with the dotted line of the bevel gear, so that the processing difficulty is reduced, and the connotation and the extension of worm transmission are expanded; 3) The dotted line meshed worm gear has the double advantages of an involute worm gear and an arc worm gear, and the strength is higher. Therefore, compared with the conventional worm drive mechanism, the worm drive mechanism has the advantages of large bearing capacity, long service life, high reliability, difficult tooth breakage, convenient processing and the like.
Drawings
The invention will be described in further detail with reference to the drawings and the detailed description.
FIG. 1 is a schematic view of the dotted line meshing worm lift mechanism of the present invention;
fig. 2 is a dotted line engagement of the dotted line engagement worm lifting mechanism of the present invention.
Wherein, 1, a first bevel gear, 2, a second bevel gear, 3, a first bevel gear, 4 and a second bevel gear, 5, a worm, 6, a driving wheel, 7, a fourth helical gear, 8, a fifth helical gear, 9, a roller, 10 and a weight.
Detailed Description
As shown in fig. 1, a dotted line meshing worm lifting mechanism comprises a first helical gear 1 and a second helical gear 2 which are meshed with each other, a first connecting shaft is fixed at the center of the second helical gear 2, a first conical gear 3 is fixed at the other end of the first connecting shaft, a second conical gear 4 is meshed on the first conical gear 3, a second connecting shaft is fixed on the second conical gear 4, a worm 5 is fixed at the other end of the second connecting shaft, a driving wheel 6 is meshed on the worm 5, the driving wheel 6 is a worm wheel or a third helical gear, a third connecting shaft is fixed on the driving wheel 6, a fourth helical gear 7 is fixed on the third connecting shaft, a fifth helical gear 8 is meshed on the fourth helical gear 7, a roller 9 is fixed on the end face of the fifth helical gear 8, the roller 9 coincides with the rotation axis of the fifth helical gear 8, a traction rope for lifting or lowering a weight 10 is wound on the roller 9, and the lifting mechanism needs to meet the following conditions:
1) Taking the number of teeth, normal surface modulus, end surface modulus, normal surface pressure angle, end surface pressure angle and pitch angle of the first helical gear 1 and the second helical gear 2 to be z respectively 1 、z 2 、m n1 、m n2 、m t1 、m t2 、α n1 、α n2 、α t1 、α t2 、β 1 、β 2 Wherein z is 1 、z 2 The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root; beta 1 、β 2 Usually takes 8-20 degrees and satisfies beta 1 ＝β 2 ；m n1 、m n2 、α n1 、α n2 The values can be self-defined or can be taken from a gear manual according to the requirements, but the requirements must be satisfied: m is m n1 cosα t1 /cosβ 1 ＝m n2 cosα t2 /cosβ 2 ，α t1 ＝arctg(tgα n1 /cosβ 1 )，α t2 ＝arctg(tgα n2 /cosβ 2 )；
2) Taking the number of teeth, the large end modulus and the large end pressure angle of the first conical gear 3 and the second conical gear 4 to be z respectively 3 、z 4 、m 3 、m 4 、α 3 、α 4 Wherein z is 3 、z 4 The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root; m is m 3 、m 4 、α 3 、α 4 Can be self-determined or take values from a gear manual as required, but must satisfy m 3 cosα 3 ＝m 4 cosα 4 ；
3) Taking the number of heads, the diameter coefficient, the axial surface modulus and the axial surface pressure angle of the worm 5 as z 5 、q 5 、m x5 、α x5 Wherein z is 5 Typically 1, 2, 4, 6; q 5 The value of (2) can refer to a gear design manual; m is m x5 、α x5 The value can be self-determined or can be taken from a gear manual according to the requirement, but the specific value is related to the end face modulus and the end face pressure angle of the driving wheel 6; pitch circle lead angle gamma of worm 5 5 ＝arctanz 5 /q 5 A degree;
4) Taking the number of teeth, pitch angle, end surface modulus and end surface pressure angle of the driving wheel 6 to be z respectively 6 、β 6 、m t6 、α t6 When the driving wheel 6 is a worm wheel, z 6 The value range of (2) is usually 28-80; when the driving wheel 6 is a third bevel gear, z 6 The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root; beta 6 Can be self-determined according to the needs; m is m t6 、α t6 The values can be self-defined or can be taken from a gear manual according to the requirements, but the requirements must be satisfied: m is m x5 cosα x5 ＝m t6 cosα t6 And alpha is x5 ＜α t6 . Under the condition that the included angle between the two shafts of the worm 5 and the driving wheel 6 is 90 degrees, beta is also satisfied 6 ＝γ 5 ；
5) Taking the number of teeth, normal surface modulus, end surface modulus, normal surface pressure angle, end surface pressure angle and pitch angle of the fourth helical gear 7 and the fifth helical gear 8 to be z respectively 7 、z 8 、m n7 、m n8 、m t7 、m t8 、α n7 、α n8 、α t7 、α t8 、β 7 、β 8 Wherein z is 7 、z 8 The value can be self-determined according to the need under the condition of meeting the condition of not cutting root; beta 7 、β 8 Usually takes 8-20 degrees and satisfies beta 7 ＝-β 8 ；m n7 、m n8 、α n7 、α n8 The values can be self-defined or can be taken from a gear manual according to the requirements, but the requirements must be satisfied: m is m n7 cosα t7 /cosβ 7 ＝m n8 cosα t8 /cosβ 8 ，α t7 ＝arctg(tgα n7 /cosβ 7 )，α t8 ＝arctg(tgα n8 /cosβ 8 )。
In the present invention, the first helical gear 1 and the second helical gear 2 are internally meshed.
The tooth profiles of the gear teeth of the first helical gear 1, the second helical gear 2, the first conical gear 3, the second conical gear 4, the worm 5, the driving wheel 6, the fourth helical gear 7 and the fifth helical gear 8 are involute and arc, namely half of the tooth heights of the gear teeth are involute convex tooth profiles, and the other half of the tooth heights of the gear teeth are concave tooth profiles of transition curves. In operation, different tooth profile curves will exhibit different meshing effects. When the transition curve tooth profile is meshed with the involute tooth profile, the transition curve tooth profile is in point contact; when the involute profile meshes with the involute profile, the involute profile exhibits line contact. As shown in FIG. 2, two intermeshing gears are defined herein as gear 1 and gear 2, where O is the point of tangency P, O 1 O 2 Is the central line, N 1 N 2 For engagement segments, J is the engagement point.
It should be understood that the above-described specific embodiments are only for explaining the present invention and are not intended to limit the present invention. Obvious variations or modifications which extend from the spirit of the present invention are within the scope of the present invention.
Claims (1)
1. A dotted line meshing worm hoist mechanism, its characterized in that: including intermeshing's first helical gear (1) and second helical gear (2), second helical gear (2) center be fixed with first connecting axle, the other end of first connecting axle be fixed with first bevel gear (3), first bevel gear (3) on mesh have second bevel gear (4), second bevel gear (4) on be fixed with the second connecting axle, the other end of second connecting axle be fixed with worm (5), worm (5) on mesh have drive wheel (6), drive wheel (6) be worm wheel or third bevel gear, drive wheel (6) on be fixed with the third connecting axle, the third connecting axle on be fixed with fourth helical gear (7), fourth helical gear (7) on mesh have fifth helical gear (8), the terminal surface of fifth helical gear (8) be fixed with cylinder (9), and the axis of revolution coincidence of cylinder (9) and fifth helical gear (8), cylinder (9) on twine have and be used for making lifting means of lifting heavy object (10) or haulage rope down, required condition is satisfied.
1) Taking the number of teeth, normal surface modulus, end surface modulus, normal surface pressure angle, end surface pressure angle and pitch angle of the first helical gear (1) and the second helical gear (2) as respectively
、
、
、
、
、
、
、
、
、
、
、
Wherein
、
The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root;
、
Usually 8-20 DEG, and satisfy +.>
=
；
、
、
、
The gear manual can be self-determined or can take values according to the requirements, but the gear manual needs to meet the following conditions:
2）
=
，
=
；
3) Taking the number of teeth, the large end modulus and the large end pressure angle of the first conical gear (3) and the second conical gear (4) as follows
、
、
、
、
、
Wherein->
、
The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root;
、
、
、
Can be self-determined or take values from gear manuals as required, but must meet +.>
；
4) Taking the number of heads, diameter coefficient, axial surface modulus and axial surface pressure angle of the worm (5) as respectively
、
、
、
Wherein->
Typically 1, 2, 4, 6;
The value of (2) can refer to a gear design manual;
、
The value can be self-determined or can be taken from a gear manual according to the requirement, but the specific value is related to the end face modulus and the end face pressure angle of the driving wheel (6); pitch angle of pitch circle of worm (5)
A degree;
5) Taking the number of teeth, pitch angle, end surface modulus and end surface pressure angle of a driving wheel (6) respectively
、
、
、
When the driving wheel (6) is a worm wheel, < >>
The value range of (2) is usually 28-80; when the driving wheel (6) is a third bevel gear, < >>
The value of (2) can be self-determined according to the need under the condition of meeting the condition of not cutting root;
Can be self-determined according to the needs;
、
The values can be self-defined or can be taken from a gear manual according to the requirements, but the requirements must be satisfied:
And->
In the followingThe angle between the worm (5) and the driving wheel (6) is 90 degrees, and the requirement of +.>
=
；
6) Taking the number of teeth, normal surface modulus, end surface modulus, normal surface pressure angle, end surface pressure angle and pitch angle of the fourth helical gear (7) and the fifth helical gear (8) as respectively
、
、
、
、
、
、
、
、
、
、
、
The value can be self-determined according to the need under the condition of meeting the condition of not cutting root;
、
Usually 8-20 DEG is taken and the +.>
=-
；
、
、
、
The gear manual can be self-determined or can take values according to the requirements, but the gear manual needs to meet the following conditions:
，
，
；/>
The first bevel gear (1) is internally meshed with the second bevel gear (2);
the tooth profiles of the first bevel gear (1), the second bevel gear (2), the first bevel gear (3), the second bevel gear (4), the worm (5), the driving wheel (6), the fourth bevel gear (7) and the fifth bevel gear (8) are involute and arc, namely half of tooth heights of the gear teeth are convex tooth profiles of involute tooth shapes, and the other half of tooth heights of the gear teeth are concave tooth profiles of transition curve tooth shapes.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810558390.2A CN108626315B (en) | 2018-06-01 | 2018-06-01 | Dotted line meshing worm lifting mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810558390.2A CN108626315B (en) | 2018-06-01 | 2018-06-01 | Dotted line meshing worm lifting mechanism |
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| Publication Number | Publication Date |
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| CN108626315A CN108626315A (en) | 2018-10-09 |
| CN108626315B true CN108626315B (en) | 2023-04-28 |
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