CN110030360A - A kind of design method of gear wheel reversing mechanism and its gear pair - Google Patents
A kind of design method of gear wheel reversing mechanism and its gear pair Download PDFInfo
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- CN110030360A CN110030360A CN201910291114.9A CN201910291114A CN110030360A CN 110030360 A CN110030360 A CN 110030360A CN 201910291114 A CN201910291114 A CN 201910291114A CN 110030360 A CN110030360 A CN 110030360A
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- 230000005540 biological transmission Effects 0.000 claims abstract description 74
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- 208000006011 Stroke Diseases 0.000 claims description 31
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- 230000001133 acceleration Effects 0.000 claims description 9
- 230000007704 transition Effects 0.000 claims description 9
- 238000005086 pumping Methods 0.000 abstract description 18
- 239000003921 oil Substances 0.000 description 10
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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
- 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
- F16H55/17—Toothed wheels
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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
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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Abstract
The invention discloses a kind of gear wheel reversing mechanisms and its gear pair designing method, comprising: input shaft is used to receive power；First transmission shaft, second driving shaft and output shaft, are arranged in parallel with input shaft；First active non-circular gear and the second active non-circular gear are arranged on input shaft；First driven non-circular gear and the second driven non-circular gear, are respectively arranged on second driving shaft and the first transmission shaft, and it is configured to be respectively adapted to be meshed with the first active non-circular gear and the second active non-circular gear；And first roller gear, the second roller gear and third roller gear, it is separately positioned on the first transmission shaft, second driving shaft and output shaft, and the second roller gear, third roller gear are meshed with the first roller gear respectively；The gear wheel reversing mechanism can increase the yield in the unit time to reduce the oil leak amount in oil pumping process；This method is simple and reliable, has flexible adjustable design parameter, improves the flexibility of noncircular gear pair design.
Description
Technical Field
The invention relates to the field of pumping unit equipment, in particular to a gear reversing mechanism for a pumping unit and a design method of a gear pair of the gear reversing mechanism.
Background
Because the traditional beam pumping unit has high energy consumption, large inertia, large vibration impact, unstable operation and large potential safety hazard during operation, long-stroke oil pumping is difficult to realize; on the basis, people also research a vertical oil pumping unit, and the problems are solved by adopting a motor to carry out variable frequency reversing, but the defects of high failure rate, high energy consumption and high electrical maintenance difficulty are still overcome; on the basis, people research the non-circular gear oil pumping unit with high efficiency and reliable reversing. The efficiency can be improved by independently changing the average speed of the upper stroke and the lower stroke under the inspiration of an out-of-phase beam pumping unit, but the symmetry of the single-layer non-circular gear must be ensured when the upper stroke and the lower stroke are equal, and the average speed of the upper stroke and the lower stroke is the same because the rotating speed of an input shaft is constant. However, tests show that the average speed of the upstroke is slightly higher than that of the downstroke, so that the oil leakage in the oil pumping process can be reduced, and the yield of the oil pumping process in unit time can be increased.
Disclosure of Invention
The present invention is directed to solve at least one of the above problems of the prior art, and an object of the present invention is to provide a gear reversing mechanism, which can change the average speed of the up stroke and the down stroke to reduce the oil leakage during the oil pumping process and increase the output per unit time, and has a simple structure, safety and reliability.
Another object of the present invention is to provide a method for designing a non-circular gear pair of the gear reversing mechanism.
A gear reversing mechanism according to a first aspect of the invention comprises: an input shaft for receiving power; the first transmission shaft, the second transmission shaft and the output shaft are arranged in parallel with the input shaft; a first driving non-circular gear and a second driving non-circular gear provided on the input shaft; a first driven non-circular gear and a second driven non-circular gear respectively arranged on the second transmission shaft and the first transmission shaft and configured to be respectively engaged with the first driving non-circular gear and the second driving non-circular gear; the first cylindrical gear, the second cylindrical gear and the third cylindrical gear are respectively arranged on the first transmission shaft, the second transmission shaft and the output shaft, and the second cylindrical gear and the third cylindrical gear are respectively meshed with the first cylindrical gear, wherein in the process that the input shaft rotates for one circle, an upper stroke stage and a lower stroke stage are sequentially carried out, and when the input shaft rotates for one circle, the second driving non-circular gear is meshed with the second driven non-circular gear; when in the down stroke stage, the first driving non-circular gear is meshed with the first driven non-circular gear, and the rotated angles of the second driven non-circular gear and the first driven non-circular gear are equal in the process.
In the technical scheme, a second driving noncircular gear rotates anticlockwise and starts to be meshed with a toothed part of a second driven noncircular gear, a first cylindrical gear coaxially connected with the second driven noncircular gear simultaneously starts to rotate clockwise, a second cylindrical gear meshed with the first cylindrical gear and a first driven noncircular gear coaxially arranged with the second cylindrical gear rotate anticlockwise, when the second driving noncircular gear is meshed with the second driven noncircular gear and continues to rotate anticlockwise to a certain angle, a first transmission shaft, a second driven noncircular gear and the first cylindrical gear on the first transmission shaft rotate clockwise once, a second transmission shaft, a first driven noncircular gear and a second cylindrical gear on the second transmission shaft rotate anticlockwise once, at the moment, the second driving noncircular gear is just disengaged from the second driven noncircular gear, the first driving noncircular gear is just meshed with the first driven noncircular gear, i.e. an up stroke is completed; the first driving noncircular gear continuously rotates anticlockwise and starts to be meshed with a toothed part of the first driving noncircular gear, the first driven noncircular gear and a second cylindrical gear which is coaxially connected start to rotate clockwise, the first cylindrical gear which is meshed with the second cylindrical gear and the first driven noncircular gear which is coaxial with the first cylindrical gear rotate anticlockwise, when the first driving noncircular gear is meshed with the first driven noncircular gear and continues to rotate anticlockwise to a certain angle, the first transmission shaft, the first driven noncircular gear and the second cylindrical gear on the first transmission shaft rotate clockwise once, the first transmission shaft, the second driven noncircular gear on the first transmission shaft and the first cylindrical gear rotate anticlockwise once, at the moment, the first driving noncircular gear is just disengaged from the first driven noncircular gear, the second driving noncircular gear is re-meshed with the second driven noncircular gear, at the moment, a downstroke is completed, and finishing a complete oil pumping process, and then carrying out the next oil pumping cycle.
In addition, the gear reversing mechanism according to the invention can also have the following technical characteristics:
furthermore, the pitch curves of the first driving non-circular gear and the second driving non-circular gear respectively comprise a toothless area, a uniform speed area and two symmetrically arranged speed change areas.
Further, the angle of the first driving non-circular gear non-tooth area is larger than the angle of the second driving non-circular gear non-tooth area.
Preferably, the toothless zone of the first driving non-circular gear is 195 °, the speed change zone is 60 ° and the constant speed zone is 45 °.
Preferably, the toothless zone of the second driving non-circular gear is 165 °, the speed change zone is 60 ° and the constant speed zone is 75 °.
Preferably, when the first driving noncircular gear is initially meshed with a first driven noncircular gear meshed with the first driving noncircular gear, an included angle between a central connecting line of the first driving noncircular gear and the first driven noncircular gear and a symmetrical axis of the first driving noncircular gear is 87.5 degrees; when the second driving noncircular gear is initially meshed with the second driven noncircular gear meshed with the second driving noncircular gear, the included angle between the central connecting line of the second driving noncircular gear and the second driven noncircular gear and the symmetrical axis of the second driving noncircular gear is 87.5 degrees.
According to a second aspect of the present invention, a method for designing a non-circular gear pair includes the steps of:
s10: designing a transmission ratio i according to a pitch curve change rule of the non-circular gear and a motion process that the driving non-circular gear is required to meet the requirements of deceleration, uniform speed and acceleration in a meshing process by combining the driving non-circular gear and a driven non-circular gear meshed with the driving non-circular gear;
s20: calculating the radius r1 of the driving non-circular gear according to the transmission ratio i and the center distance a between the driving non-circular gear and the driven non-circular gear, and forming a pitch curve of the driving non-circular gear under polar coordinates, wherein,
the radius of the driving non-circular gear satisfies the following formula:
wherein a is the center distance between the driving non-circular gear and the driven non-circular gear;
s30: according to the center distance a between the driving non-circular gear and the driven non-circular gear and the radius r of the driving non-circular gear1Obtaining the radius r of the driven non-circular gear2And forming a pitch curve of the driven non-circular gear under polar coordinates.
Preferably, transition areas are further arranged between the deceleration area and the uniform speed area and between the uniform speed area and the acceleration area.
Preferably, the transmission ratio i of the driving non-circular gear and the driven non-circular gear meshed with the driving non-circular gear satisfies the following formula:
wherein,is the angle corresponding to the pitch curve of the driving non-circular gear, i is the transmission ratio, β is the angle of the uniform speed area, the first driving non-circular gear is 45 degrees, the second driving non-circular gear is 75 degrees, A is the maximum transmission ratio, B is the minimum transmission ratio, m is the transmission ratio transition factor, 0.5 is taken, and
according to the design method of the non-circular gear pair, the method is simple and reliable, flexible and adjustable design parameters are provided, and the flexibility of the design of the non-circular gear pair is improved.
Drawings
FIG. 1 is a front view of a gear reversing mechanism;
FIG. 2 is a perspective view of FIG. 1;
FIG. 3 is a schematic view of a first driving non-circular gear;
FIG. 4 is a schematic view of a second driving non-circular gear;
FIG. 5 is a schematic structural diagram of an active non-circular gear pitch curve;
FIG. 6 is a schematic diagram of an active non-circular gear pitch curve incorporating a transition zone.
In the figure, a gear reversing mechanism 100; an input shaft 1; a first driving non-circular gear 11; a second driving non-circular gear 12; a first transmission shaft 2; a second driven non-circular gear 21; a first cylindrical gear 22; a second transmission shaft 3; a first driven non-circular gear 31; a second cylindrical gear 32; an output shaft 4; a third cylindrical gear 41; an axis of symmetry O; a toothless zone A; a deceleration zone B; a uniform velocity region C; and an acceleration zone D.
Detailed Description
The invention will be further explained with reference to the drawings.
The following description is provided with reference to the accompanying drawings to assist in a comprehensive understanding of various embodiments of the invention as defined by the claims. It includes various specific details to assist in this understanding, but these details should be construed as merely exemplary. Accordingly, those of ordinary skill in the art will recognize that changes and modifications of the various embodiments described herein can be made without departing from the scope of the invention, which is defined by the appended claims. Moreover, descriptions of well-known functions and constructions may be omitted for clarity and conciseness.
It will be apparent to those skilled in the art that the following descriptions of the various embodiments of the present invention are provided for illustration only and not for the purpose of limiting the invention as defined by the appended claims.
A gear reversing mechanism 100 according to a first aspect of the present invention, as shown in fig. 1 and 2, includes: an input shaft 1 for receiving power; a first transmission shaft 2, a second transmission shaft 3 and an output shaft 4, which are arranged in parallel with the input shaft 1; a first driving non-circular gear 11 and a second driving non-circular gear 12 provided on the input shaft 1; a first driven non-circular gear 31 and a second driven non-circular gear 21, which are respectively provided on the second transmission shaft 3 and the first transmission shaft 2 and are configured to be respectively engaged with the first driving non-circular gear 11 and the second driving non-circular gear 12; the first cylindrical gear 22, the second cylindrical gear 32 and the third cylindrical gear 41 are respectively arranged on the first transmission shaft 2, the second transmission shaft 3 and the output shaft 4, and the second cylindrical gear 32 and the third cylindrical gear 41 are respectively meshed with the first cylindrical gear 22; during the process that the input shaft 1 rotates for one circle, an upper stroke stage and a lower stroke stage are sequentially carried out, and when the input shaft is in the upper stroke stage, the second driving non-circular gear 12 is meshed with the second driven non-circular gear 21; when in the down stroke stage, the first driving non-circular gear 11 is meshed with the first driven non-circular gear 31, and in the process, the rotated angles of the second driven non-circular gear 21 and the first driven non-circular gear 31 are equal.
In the technical scheme, the second driving noncircular gear 12 rotates counterclockwise and starts to be meshed with the toothed part of the second driven noncircular gear 21, meanwhile, the first cylindrical gear 22 coaxially connected with the second driven noncircular gear 21 starts to rotate clockwise, the second cylindrical gear 32 meshed with the first cylindrical gear 22 and the first driven noncircular gear 31 coaxially arranged with the second cylindrical gear 32 rotate counterclockwise, when the second driving noncircular gear 12 is meshed with the second driven noncircular gear 21 and continues to rotate counterclockwise to a certain angle, the first transmission shaft 2, the second driven noncircular gear 21 and the first cylindrical gear 22 thereon rotate clockwise once, the second transmission shaft 3, the first driven noncircular gear 31 and the second cylindrical gear 32 thereon rotate counterclockwise once, at this time, the second driving noncircular gear 12 and the second driven noncircular gear 21 just disengage, the first driving noncircular gear 11 is just meshed with the first driven noncircular gear 31, and an up stroke is completed; the first driving noncircular gear 11 rotates counterclockwise continuously and starts to be meshed with the toothed part of the first driving noncircular gear, the first driven noncircular gear 31 and the second cylindrical gear 32 which is coaxially connected start to rotate clockwise, the first cylindrical gear 22 which is meshed with the second cylindrical gear 32 and the first driven noncircular gear 31 which is coaxial with the first cylindrical gear 22 rotate counterclockwise, when the first driving noncircular gear 11 is meshed with the first driven noncircular gear 31 and rotates counterclockwise continuously to a certain angle, the first transmission shaft 2 and the first driven noncircular gear 31 and the second cylindrical gear 32 thereon rotate clockwise once, the first transmission shaft 2 and the second driven noncircular gear 21 and the first cylindrical gear 22 thereon rotate counterclockwise once, at the moment, the first driving noncircular gear 11 is just disengaged from the first driven noncircular gear 31, the second driving noncircular gear 12 is re-meshed with the second driven noncircular gear 21, at this point, a down stroke is completed, and the next pumping cycle is performed after a complete pumping process is completed.
Further, as shown in fig. 3 and 4, the pitch curves of the first driving non-circular gear 11 and the second driving non-circular gear 12 both include a toothless zone a, a constant speed zone C and two symmetrically arranged speed change zones; specifically, the first driving noncircular gear 11 and the second driving noncircular gear 12 both sequentially include a toothless zone a, a deceleration zone B, a uniform velocity zone C and an acceleration zone D, the deceleration zone B and the acceleration zone D together form a speed change zone, and are distributed along a symmetry axis O of the first driving noncircular gear 11 or the second driving noncircular gear 12.
Further, the angle of the toothless area a of the first driving noncircular gear 11 is larger than that of the toothless area a of the second driving noncircular gear 12, that is, the gear pair formed by the first driving noncircular gear 11 and the first driven noncircular gear 31 engaged with the first driving noncircular gear 11 completes the up-stroke stage; in order to make the average angular velocity of the up stroke greater than the angular velocity of the down stroke, the angle of the toothless area a of the first driving noncircular gear 11 is made greater than the angle of the toothless area a of the second driving noncircular gear 12 when designing the driving noncircular gears, in the stage where the gear pair formed by the second driving noncircular gear 12 and the second driven noncircular gear 21 engaged therewith completes the down stroke.
Preferably, the toothless zone a of the first driving non-circular gear 11 is 195 °, the speed change zone is 60 ° and the constant speed zone C is 45 °.
Preferably, the toothless zone a of the second driving non-circular gear 12 is 165 °, the speed change zone is 60 ° and the constant speed zone C is 75 °.
Preferably, when the first driving non-circular gear 11 and the first driven non-circular gear 31 engaged with the first driving non-circular gear 11 are initially engaged, an included angle between a central connecting line of the first driving non-circular gear 11 and the first driven non-circular gear 31 and a symmetry axis O of the first driving non-circular gear 11 is 87.5 °; when the second driving noncircular gear 12 is initially meshed with the second driven noncircular gear 21 meshed with the second driving noncircular gear, the included angle between the central connecting line of the second driving noncircular gear 12 and the second driven noncircular gear 21 and the symmetry axis O of the second driving noncircular gear 12 is 87.5 degrees.
In one embodiment of the present invention, the operation process is as follows: the second driving noncircular gear 12 rotates anticlockwise and starts to be meshed with the toothed part of the second driven noncircular gear 21, meanwhile, the first cylindrical gear 22 coaxially connected with the second driven noncircular gear 21 starts to rotate clockwise, the second cylindrical gear 32 meshed with the first cylindrical gear 22 and the first driven noncircular gear 31 coaxially arranged with the second cylindrical gear 32 rotate anticlockwise, when the second driving noncircular gear 12 is meshed with the second driven noncircular gear 21 and continues to rotate anticlockwise to 165 degrees, the first transmission shaft 2, the second driven noncircular gear 21 and the first cylindrical gear 22 thereon rotate clockwise once, the second transmission shaft 3, the first driven noncircular gear 31 and the second cylindrical gear 32 thereon rotate anticlockwise once, at the moment, the second driving noncircular gear 12 is just disengaged from the second driven noncircular gear 21, the first driving noncircular gear 11 is just meshed with the first driven noncircular gear 31, i.e. an up stroke is completed; the first driving noncircular gear 11 continues to rotate anticlockwise and starts to be meshed with a toothed part of the driven noncircular gear, the first driven noncircular gear 31 and the second cylindrical gear 32 which is coaxially connected start to rotate clockwise, the first cylindrical gear 22 which is meshed with the second cylindrical gear 32 and the first driven noncircular gear 31 which is coaxial with the first cylindrical gear 22 rotate anticlockwise, when the first driving noncircular gear 11 is meshed with the first driven noncircular gear 31 and continues to rotate anticlockwise to 195 degrees, the first transmission shaft 2 and the first driven noncircular gear 31 and the second cylindrical gear 32 thereon rotate clockwise once, the first transmission shaft 2 and the second driven noncircular gear 21 and the first cylindrical gear 22 thereon rotate anticlockwise once, at the moment, the first driving noncircular gear 11 is just disengaged from the first driven noncircular gear 31, the second driving noncircular gear 12 is re-meshed with the second driven noncircular gear 21, at this point, a down stroke is completed, and the next pumping cycle is performed after a complete pumping process is completed.
According to a second aspect of the present invention, a method for designing a non-circular gear pair includes the steps of:
s10: designing a transmission ratio i according to a pitch curve change rule of the non-circular gear and a motion process that the driving non-circular gear is required to meet the requirements of deceleration, uniform speed and acceleration in a meshing process by combining the driving non-circular gear and a driven non-circular gear meshed with the driving non-circular gear;
specifically, in combination with the current oilfield transmission requirements, the maximum transmission ratio a is determined to be 2.81, the minimum transmission ratio B is determined to be 1/3, and the variation rule is shown in fig. 5;
preferably, the transmission ratio i of the driving non-circular gear and the driven non-circular gear meshed with the driving non-circular gear satisfies the following formula:
wherein,an angle corresponding to a pitch curve of the driving non-circular gear, i is a transmission ratio, β is an angle of a constant speed area C, the first driving non-circular gear 11 is 45 degrees, the second driving non-circular gear 12 is 75 degrees, A is a maximum transmission ratio, B is a minimum transmission ratio, the maximum transmission ratio A is determined to be 2.81 according to the transmission requirement of the current oil field, the minimum transmission ratio B is set to be 1/3m and is a transmission ratio transition factor, 0.5 is taken, and
s20: calculating the radius r1 of the driving non-circular gear according to the transmission ratio i and the center distance a between the driving non-circular gear and the driven non-circular gear, and forming a pitch curve of the driving non-circular gear under polar coordinates, wherein,
when the two non-circular gears are driven, the center distance of the transmission shaft is kept constant, and the radius of the transmission shaft satisfies the following relation:
r1＝a-rg＝i×r2(2-2)
thus:
wherein:
a is the center distance between the driving non-circular gear and the driven non-circular gear,
r1-the radius of the driving wheel,
r2-the radius of the driven wheel,
i-instantaneous transmission ratio.
S30: obtaining the radius r2 of the driven non-circular gear according to the center distance a between the driving non-circular gear and the driven non-circular gear and the radius r1 of the driving non-circular gear, and forming a pitch curve of the driven non-circular gear under polar coordinates; specifically, for the first driven non-circular gear 31 and the second driven non-circular gear 21, the pitch curves thereof can be generated by MATLAB programming calculation according to the following formula
The derivation process specifically is as follows: for driven non-circular gears, according to the radius relationship of two transmission shafts, namely:
according to the speed equality of the driven non-circular gear and the non-circular gear at the meshing point, namely: v. of1＝v2
In the formula:the rotation angle relation of the driving wheel and the driven wheel can be expressed as follows:
and substituting the formula (2-1) into the formula (2-5) for segmentation integration to obtain the corresponding driven wheel angle under any angle of the driving wheel. After mathematical modeling in the form of the non-circular gear structure is performed, the calculation results are imported into the CAD to generate two pairs of non-circular gear structure diagrams after numerical calculation in MATLAB.
Under the structure of double-layer non-circular gear, the upper punch and the lower punchThe speed of the stroke is changed, but the stroke is still a fixed value, and the corresponding relation is that the meshing angle of the driven wheels of the first pair of non-circular gears in a single cycle is equal to the meshing angle of the driven wheels of the second pair of non-circular gears, namely the meshing angle of the driven wheels of the first pair of non-circular gears is equal to the meshing angle of the driven wheels of the second pair of non-circular gearsAccording to the basic relation, the following mathematical model establishment is carried out:
according to the formula (2-1), according to the working requirement of the pumping unit, the maximum transmission ratio A is kept equal to the first pair of gears, the rotation angles of the two speed change regions are 120 degrees, so that the uniform speed region C is determined to be 75 degrees, namely β is 45 degrees, only one variable in the formula (2-1), namely the minimum transmission ratio B, is taken into the formula (2-5), and the formula (3-1) is obtained:
the solving process involves integration operation of negative high power, and general numerical calculation cannot solve the determined B value reversely. Therefore, the first pair of non-circular gears is also designed. Firstly, a range of minimum transmission ratio B is given, and the corresponding maximum rotation angle of the driven wheel is calculated according to the formula (3-1) in a circulation mode according to fixed increment from the minimum valueMake it approach to infinity
Thereby determining the structural parameters of the second pair of non-circular gears.
After mathematical modeling of the structural form of the non-circular gear is carried out, after numerical calculation in MATLAB, calculation results are imported into CAD to generate a structure diagram of two pairs of non-circular gears
Preferably, as shown in fig. 6, transition regions, i.e. transition parabolas, are further disposed between the deceleration region B and the uniform velocity region C and between the uniform velocity region C and the acceleration region D, and preferably, in order to make the non-circular gear pair more stable in the meshing process, the transition may be performed by using circular arcs, and the specific function is as shown in equation (2-1).
Specifically, the formula of the transmission ratio i of the driving noncircular gear and the driven noncircular gear meshed with the driving noncircular gear is sequentially substituted into the formula of the radius r1 of the driving noncircular gear to obtain the angle corresponding to the radius r1 of the driving noncircular gear relative to the pitch curve of the driving noncircular gearThen, the MATLAB can be used for drawing a pitch curve of the driving non-circular gear on a polar coordinate; since the center distance a between the driven non-circular gear and the driving non-circular gear is not changed, the radius r2 of the driven non-circular gear can be obtained according to the angle of the pitch curve of the driven non-circular gearThereby obtaining the angle of the radius r2 of the driven non-circular gear relative to the pitch curve of the driven non-circular gearMay then be used to plot the pitch curve of the driven non-circular gear on polar coordinates using MATLAB.
According to the design method of the non-circular gear pair, the method is simple and reliable, flexible and adjustable design parameters are provided, and the flexibility of the design of the non-circular gear pair is improved.
The above description is intended to be illustrative of the present invention and not to limit the scope of the invention, which is defined by the claims appended hereto.
Those skilled in the art will appreciate that various features of the various embodiments of the invention described hereinabove may be omitted, added to, or combined in any manner, respectively. Moreover, simple modifications and structural modifications that are adaptive and functional to those skilled in the art are within the scope of the present invention.
While the invention has been shown and described with reference to various embodiments, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the scope of the invention as defined by the appended claims.
Claims (9)
1. A gear reverser mechanism comprising:
an input shaft (1) for receiving power;
a first transmission shaft (2), a second transmission shaft (3) and an output shaft (4) which are arranged in parallel with the input shaft (1);
a first driving non-circular gear (11) and a second driving non-circular gear (12) provided on the input shaft (1);
a first driven non-circular gear (31) and a second driven non-circular gear (21) respectively provided on the second transmission shaft (3) and the first transmission shaft (2) and configured to be respectively adapted to mesh with the first driving non-circular gear (11) and the second driving non-circular gear (12); and
a first cylindrical gear (22), a second cylindrical gear (32) and a third cylindrical gear (41) which are respectively arranged on the first transmission shaft (2), the second transmission shaft (3) and the output shaft (4), and the second cylindrical gear (32) and the third cylindrical gear (41) are respectively meshed with the first cylindrical gear (22),
wherein, in the process of one circle of rotation of the input shaft (1), an upper stroke stage and a lower stroke stage are sequentially carried out, and when the input shaft is in the upper stroke stage, the second driving non-circular gear (12) is meshed with the second driven non-circular gear (21); when in the down stroke stage, the first driving non-circular gear (11) is meshed with the first driven non-circular gear (31), and in the process, the rotated angles of the second driven non-circular gear (21) and the first driven non-circular gear (31) are equal.
2. A gear reversing mechanism according to claim 1, characterized in that the pitch curves of the first driving non-circular gear (11) and the second driving non-circular gear (12) each comprise a toothless zone (a), a constant velocity zone (C) and two symmetrically arranged speed change zones.
3. Gear reverser mechanism according to claim 2, characterized in that the angle of the toothless zone (a) of the first driving noncircular gear (11) is greater than the angle of the toothless zone (a) of the second driving noncircular gear (12).
4. A gear reversing mechanism according to claim 3, characterized in that the toothless zone (a) of the first driving non-circular gear wheel (11) is 195 °, the speed change zone is 60 ° and the uniform velocity zone (C) is 45 °.
5. A gear reversing mechanism according to claim 3 or 4, characterized in that the toothless zone (A) of the second driving non-circular gear (12) is 165 °, the speed change zone is 60 ° and the uniform velocity zone (C) is 75 °.
6. The gear reversing mechanism according to claim 1, characterized in that when the first driving non-circular gear (11) is initially engaged with the first driven non-circular gear (31) engaged therewith, the angle between the central connecting line of the first driving non-circular gear (11) and the first driven non-circular gear (31) and the symmetry axis (O) of the first driving non-circular gear (11) is 87.5 °; when the second driving noncircular gear (12) is initially meshed with a second driven noncircular gear (21) meshed with the second driving noncircular gear, the included angle between the central connecting line of the second driving noncircular gear (12) and the second driven noncircular gear (21) and the symmetrical axis (O) of the second driving noncircular gear (12) is 87.5 degrees.
7. A design method of a non-circular gear pair is characterized by comprising the following steps:
s10: designing a transmission ratio i according to a pitch curve change rule of the non-circular gear and a motion process that the driving non-circular gear is required to meet the requirements of deceleration, uniform speed and acceleration in a meshing process by combining the driving non-circular gear and a driven non-circular gear meshed with the driving non-circular gear;
s20: calculating the radius r of the driving noncircular gear according to the transmission ratio i and the center distance a between the driving noncircular gear and the driven noncircular gear1And forming a pitch curve of the driving non-circular gear in polar coordinates, wherein,
the radius of the driving non-circular gear satisfies the following formula:
wherein a is the center distance between the driving non-circular gear and the driven non-circular gear;
s30: according to the center distance a between the driving non-circular gear and the driven non-circular gear and the radius r of the driving non-circular gear1Obtaining the radius r of the driven non-circular gear2And forming a pitch curve of the driven non-circular gear under polar coordinates.
8. A method of designing a non-circular gear pair according to claim 7, characterized in that transition zones are further provided between the deceleration zone (B) and the uniform velocity zone (C) and between the uniform velocity zone (C) and the acceleration zone (D).
9. A method of designing a non-circular gear pair according to claim 8, wherein the transmission ratio i of the driving non-circular gear to the driven non-circular gear engaged therewith satisfies the following equation:
wherein,is the angle corresponding to the pitch curve of the driving non-circular gear, i is the transmission ratio, β is the angle of the uniform speed area (C), the second driving non-circular gear (12) takes 45 degrees, the first driving non-circular gear (11) takes 75 degrees, A is the maximum transmission ratio, B is the minimum transmission ratio, m is the transmission ratio transition factor, takes 0.5, and
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