CN111878557A - Double-arc herringbone-tooth planetary gear transmission mechanism - Google Patents

Double-arc herringbone-tooth planetary gear transmission mechanism Download PDF

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Publication number
CN111878557A
CN111878557A CN202010852578.5A CN202010852578A CN111878557A CN 111878557 A CN111878557 A CN 111878557A CN 202010852578 A CN202010852578 A CN 202010852578A CN 111878557 A CN111878557 A CN 111878557A
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gear
double
bearing
arc
tooth
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Pending
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CN202010852578.5A
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张友军
彭勇
王涛涛
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Xian Shiyou University
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Xian Shiyou University
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Priority to CN202010852578.5A priority Critical patent/CN111878557A/en
Publication of CN111878557A publication Critical patent/CN111878557A/en
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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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • 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
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • 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
    • F16H2057/0087—Computer aided design [CAD] specially adapted for gearing features ; Analysis of gear systems
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces

Abstract

A double-arc herringbone gear planetary gear transmission mechanism is characterized in that a sun gear, a planet gear and an inner gear ring are double-arc herringbone gears, the sun gear is fixedly connected to an output shaft, the planet gear is positioned on a planet carrier through a bearing, the left half part and the right half part of the planet carrier are connected through bolts, the inner gear ring is fixed on a machine base, a machine shell on the left side and the right side is fixedly connected to the machine base through bolts, an input shaft and the output shaft are positioned through the bearing, the input shaft is a hollow shaft, the output shaft is embedded and sleeved in the input shaft through the bearing, and a belt; the power is input by the belt pulley, is transmitted to the planet wheel through the input shaft and the planet carrier, the planet wheel rotates around the axis of the planet wheel and the axis of the inner gear ring, and finally the sun wheel drives the output shaft to output from two ends; the invention has the advantages of large bearing capacity, large transmission ratio, stable transmission and compact structure, and simultaneously, the power is output from two ends, thereby being particularly suitable for the transmission mechanism of the low-stroke-frequency heavy-duty oil pumping unit.

Description

Double-arc herringbone-tooth planetary gear transmission mechanism
Technical Field
The invention relates to the technical field of transmission reducers of oil well pumping units, in particular to a double-arc herringbone-tooth planetary gear transmission mechanism.
Technical Field
The development of the internal external gear transmission technology is more and more diversified, and high bearing capacity, high speed, high transmission efficiency, high reliability, high precision, low noise, low vibration, low cost and compact structure are important directions for the development of the transmission technology. Particularly in the petroleum field, larger bearing capacity and transmission ratio are often needed, and compact structure and stable transmission can be ensured; and it is difficult for a conventional decelerator to simultaneously satisfy these requirements.
Disclosure of Invention
In order to solve the technical problems, the invention aims to provide a double-circular-arc herringbone-tooth planetary gear transmission mechanism which combines the advantages of high bearing capacity, stable herringbone-tooth transmission, large transmission ratio of a planetary gear train and compact structure, can meet the requirements of high bearing capacity, large transmission ratio, stable transmission and compact structure, can realize power output at two ends, and is particularly suitable for an oil pumping unit, especially a low-stroke-frequency heavy-load oil pumping unit.
In order to achieve the purpose, the invention is realized by the following technical scheme:
a double-arc herringbone-tooth planetary gear transmission mechanism comprises a left casing 2 and a right casing 8, one end of the left casing 2 and one end of the right casing 8 are fixed on a base 17 through bolts, the other ends of the left casing 2 and the right casing 8 are respectively connected with a left end cover 1 and a right end cover 9 and are also fixed on the base 17 through the left end cover 1 and the right end cover 9, an inner gear ring 6 is fixed in the center of the base 17, a planet wheel 4 is arranged on the inner gear ring 6, the planet wheel 4 is positioned on a left planet carrier 5 and a right planet carrier 7 through bearings, the left planet carrier 5 and the right planet carrier 7 are connected through bolts 18 to form a cavity double-side plate split structure, the right planet carrier 7 is connected with an input shaft 11 through bolts 16, the input shaft 11 is a hollow shaft, an output shaft 20 is embedded in the input shaft 11, the output shaft 20 is fixedly connected with a sun wheel 3 and is positioned through an A bearing 13, a B bearing 14 and a D, the input shaft 11 is positioned radially through an A bearing 13, a B bearing 14 and a C bearing 15, the belt pulley 10 is fixedly connected to the input shaft 11 and positioned axially through an end cover 12 and an inclined surface of the input shaft 11, and input power of the belt pulley 10 is transmitted to the planet wheels 4 through the input shaft 11 and the right planet carrier 7, so that the planet wheels 4 rotate around the axis of the belt pulley and the axis of the inner gear ring 6.
The tooth profiles of the sun gear 3, the planet gear 4 and the inner gear ring 6 are double-arc herringbone teeth, and the end face tooth profile equation of the double-arc gear is as follows:
x＝(ρsinα+e+r)cosΦ±(ρcosα+ecotα)cosβsinΦ
Figure BDA0002645223660000022
Figure BDA0002645223660000021
wherein: x-arc gear end face tooth profile abscissa, y-arc gear end face tooth profile ordinate, r-pitch circle radius, beta-helix angle, rho-arc radius of each section, e-displacement of circle center of each section, alpha-included angle between radial line of each section of arc and pitch line, and N-included angle between circle center of each section of arc tooth profile and selected coordinate axis xnThe offset of (2); the upper surface of the double positive signs corresponds to a left tooth surface, the lower surface of the double positive signs corresponds to a right tooth surface, and the left side and the right side are based on a tooth surface tooth profile symmetry axis.
The planet gears 4 are provided with 3-5 groups, the moduli of the sun gear 3, the planet gears 4 and the inner gear ring 6 must be consistent, and the helix angles of the sun gear 3, the planet gears 4 and the inner gear ring 6 must be consistent.
The invention has the advantages that:
1. the invention has the advantages of planetary gear train, double circular arc tooth shape and herringbone tooth, and can achieve the purposes of large bearing capacity, large transmission ratio, stable transmission and compact structure.
2. Compared with the existing involute herringbone tooth planetary gear transmission mechanism, the bearing capacity of the double-arc herringbone tooth planetary gear transmission is doubled compared with that of the involute herringbone tooth planetary gear transmission, or the volume of the transmission mechanism is reduced by one third by using a new transmission scheme under the condition of the same bearing capacity.
3. Because the output shaft is embedded in the input shaft, the invention can be input through a single power end and output through a double power end, and is particularly suitable for the transmission mechanism of a low-stroke-frequency heavy-duty oil pumping machine.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is a schematic structural view of the double-arc herringbone gear of the present invention.
FIG. 3 is a schematic representation of a bi-arc herringbone tooth profile of the present invention.
Fig. 4 is a schematic transmission diagram of the sun gear 3 and the planet gears 4.
Detailed Description
The following detailed description of the embodiments of the present invention will be made with reference to the accompanying drawings, but the present invention is not limited to these embodiments, and any modifications or substitutions in the basic spirit of the embodiments will still fall within the scope of the present invention as claimed in the claims.
Referring to fig. 1, a double-arc herringbone planetary gear transmission mechanism comprises a left casing 2 and a right casing 8, one end of the left casing 2 and one end of the right casing 8 are fixed on a base 17 through bolts, the other ends of the left casing 2 and the right casing 8 are respectively connected with a left end cover 1 and a right end cover 9 and are also fixed on the base 17 through the left end cover 1 and the right end cover 9, an inner gear ring 6 is fixed in the center of the base 17, a planetary gear 4 is arranged on the inner gear ring 6, the planetary gear 4 is positioned on a left planet carrier 5 and a right planet carrier 7 through bearings, the left planet carrier 5 and the right planet carrier 7 are connected through bolts 18 to form a cavity double-side plate-separated structure, the right planet carrier 7 is connected with an input shaft 11 through bolts 16, the input shaft 11 is a hollow shaft, an output shaft 20 is embedded in the input shaft 11, the output shaft 20 is fixedly connected with a sun gear 3 and is connected through, The B bearing 14 and the D bearing 19 realize positioning, the input shaft 11 realizes radial positioning through the A bearing 13, the B bearing 14 and the C bearing 15, the belt pulley 10 is fixedly connected on the input shaft 11 and realizes axial positioning through the end cover 12 and the inclined plane of the input shaft 11, the input power of the belt pulley 10 is transmitted to the planet wheel 4 through the input shaft 11 and the right planet carrier 7, so that the planet wheel 4 rotates around the axis of the belt pulley 10 and the axis of the inner gear ring 6 fixed on the base 17, and the D bearing 19 and the C bearing 15 are fixed through the left end cover 1 and the right end cover 9.
Referring to fig. 2, 3 and 4, the tooth profiles of the sun gear 3, the planet gear 4 and the inner gear ring 6 are double-arc herringbone teeth, and the end face tooth profile equation of the double-arc herringbone gear is as follows:
x＝(ρsinα+e+r)cosΦ±(ρcosα+ecotα)cosβsinΦ
Figure BDA0002645223660000042
Figure BDA0002645223660000041
wherein: x-arc gear end face tooth profile abscissa, y-arc gear end face tooth profile ordinate, r-pitch circle radius, beta-helix angle, rho-arc radius of each section, e-displacement of circle center of each section, alpha-included angle between radial line of each section of arc and pitch line, and N-included angle between circle center of each section of arc tooth profile and selected coordinate axis xnThe offset of (2); the upper side corresponds to a left tooth surface, the lower side corresponds to a right tooth surface, and the left side and the right side are based on the symmetry axis of tooth surface tooth profile (teeth are called tooth profile when the teeth are convex, and grooves are called tooth profile when the teeth are concave).
The planet gears 4 are provided with 3-5 groups, the moduli of the sun gear 3, the planet gears 4 and the inner gear ring 6 must be consistent, and the helix angles of the sun gear 3, the planet gears 4 and the inner gear ring 6 must be consistent.
The working principle of the invention is as follows:
referring to fig. 4, power is input through a belt pulley 10, and is transmitted to the planet wheel 4 through the input shaft 11 and the right planet carrier 7, the planet wheel 4 rotates around the axis of the planet wheel 4 and the axis of the inner gear ring 6, the planet wheel 4 drives the sun wheel 3 to rotate, and finally, the sun wheel 3 drives the output shaft 20 to output power from two ends.
The transmission mechanism is lubricated by an oil sump, and the sun gear 3, the planet gear 4 and the inner gear ring 6 are double-arc herringbone teeth, so that the transmission mechanism has the advantages of double-arc tooth shapes and herringbone teeth, and can achieve the effects of large bearing capacity, large transmission ratio, stable transmission and compact structure.

Claims (3)

1. A double-arc herringbone-tooth planetary gear transmission mechanism comprises a left side machine shell (2) and a right side machine shell (8), one end of the left side machine shell (2) and one end of the right side machine shell (8) are fixed on a machine base (17) through bolts, the other ends of the left side machine shell (2) and the right side machine shell (8) are respectively connected with a left end cover (1) and a right end cover (9) and are also fixed on the machine base (17) through the left end cover (1) and the right end cover (9), the double-arc herringbone-tooth planetary gear transmission mechanism is characterized in that an inner gear ring (6) is fixed at the center of the machine base (17), a planetary gear (4) is arranged on the inner gear ring (6), the planetary gear (4) is positioned on a left planetary carrier (5) and a right planetary carrier (7) through bearings, the left planetary carrier (5) and the right planetary carrier (7) are connected through bolts (18) to form a cavity double-side plate split structure, the right planetary, the input shaft (11) is a hollow shaft, the output shaft (20) is embedded in the input shaft (11), the output shaft (20) is fixedly connected with the sun wheel (3) and realizes positioning through an A bearing (13), a B bearing (14) and a D bearing (19), the input shaft (11) realizes radial positioning through the A bearing (13), the B bearing (14) and a C bearing (15), the belt pulley (10) is fixedly connected to the input shaft (11) and realizes axial positioning through an end cover (12) and an input shaft (11) inclined plane, and input power of the belt pulley (10) is transmitted to the planet wheel (4) through the input shaft (11) and the right planet carrier (7), so that the planet wheel (4) rotates around the axis of the planet wheel and the axis of the inner gear (6).
2. The double-circular-arc herringbone-tooth planetary gear transmission mechanism is characterized in that the tooth profiles of the sun gear (3), the planet gear (4) and the inner gear ring (6) are all double-circular-arc herringbone teeth, and the tooth profile equation of the end face of the double-circular-arc gear is as follows:
x＝(ρsinα+e+r)cosΦ±(ρcosα+ecotα)cosβsinΦ
Figure FDA0002645223650000021
Figure FDA0002645223650000022
wherein: x-abscissa of end face tooth profile of the circular arc gear, y-ordinate of end face tooth profile of the circular arc gear, r-pitch radius, beta-helix angle, rho-radius of each section of circular arc, e-displacement of circle center of each section of circular arc, alpha-included angle between radial line of upper point of each section of circular arc and pitch line, and N-offset of circle center of each section of circular arc profile relative to selected coordinate axis xn; the upper surface of the double positive signs corresponds to a left tooth surface, the lower surface of the double positive signs corresponds to a right tooth surface, and the left side and the right side are based on a tooth surface tooth profile symmetry axis.
3. A double circular arc herringbone gear planetary transmission mechanism according to claim 1, characterized in that the planetary gears (4) are provided with 3-5 groups, the modulus of the sun gear (3), the planetary gears (4) and the inner gear ring (6) must be consistent, and the helix angles of the sun gear (3), the planetary gears (4) and the inner gear ring (6) must be consistent.
CN202010852578.5A 2020-08-21 2020-08-21 Double-arc herringbone-tooth planetary gear transmission mechanism Pending CN111878557A (en)

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CN202010852578.5A CN111878557A (en) 2020-08-21 2020-08-21 Double-arc herringbone-tooth planetary gear transmission mechanism

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Application Number Priority Date Filing Date Title
CN202010852578.5A CN111878557A (en) 2020-08-21 2020-08-21 Double-arc herringbone-tooth planetary gear transmission mechanism

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