CN116292786A - Universal mechanical stepless speed changer and speed changing method - Google Patents
Universal mechanical stepless speed changer and speed changing method Download PDFInfo
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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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
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
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Abstract
The invention discloses a general mechanical stepless speed changer and a speed changing method, comprising the following steps: the transmission comprises a transmission input shaft, a shaft end seal, a bearing gland, an input end bearing, a wheel carrier bearing, a bevel gear sun gear I, a bevel gear planet wheel I, a planet wheel carrier I, a bevel gear planet wheel II, a differential wheel shaft, a bevel gear sun gear II, a bevel gear disc gear ring, a speed regulation large gear, a straight gear ring, a straight gear sun gear, an intermediate shaft, an output connecting flange, a speed regulation motor, a speed regulation pinion, a bevel gear planet wheel III, a needle bearing, an input connecting flange, a bevel gear planet wheel IV, an intermediate shaft supporting bearing, a straight gear planet wheel and a planet wheel carrier II. The invention realizes the speed regulation function by combining the planetary differential and the planetary reducer, realizes torque balance by reversing output of two groups of gears of the planetary differential, and realizes the change of the transmission ratio by regulating the rotation speed of the balance gear ring through the speed regulation motor.
Description
Technical Field
The invention belongs to the technical field of speed variators, and particularly relates to a universal mechanical stepless speed changer and a speed change method.
Background
Continuously variable transmission (Continuously Variable Transmission, CVT for short) refers to a transmission that allows the rotational speed of the output shaft of a machine to be continuously varied over a range of speeds under some control. A continuously variable transmission is a device that has two shafts, a driving shaft and a driven shaft, and connects the two shafts directly or indirectly through an intermediate medium (solid, fluid, electromagnetic flow) capable of transmitting torque to transmit power. When the relation between the input shaft and the output shaft is controlled, the transmission ratio between the two shafts can be continuously changed in the range of two polar values. Compared with the fixed transmission ratio and the stepped transmission, the stepless speed change transmission has the advantages of being capable of continuously changing the speed in a certain range according to the working requirement so as to adapt to the requirement of output rotating speed and external load change, and the like, so that the stepless speed change transmission plays an important role in the technical field of modern transmission. Continuously variable transmissions are generally classified into three types according to the transmission medium: electrical, fluidic, and mechanical.
The electric stepless speed change transmission is realized by controlling the electric parameters of an alternating current or direct current motor, such as changing magnetic flux, voltage, current or frequency, adjusting the phase angle of the motor, and controlling the motor through a microprocessor. The stepless speed regulation of electric power mainly comprises three kinds of electromagnetic slip speed regulation, direct current speed regulation and alternating current speed regulation, and the current alternating current frequency conversion speed regulation performance is good, and the efficiency is high, so that the application is the most.
Fluid continuously variable transmissions fall into two categories: firstly, the hydraulic type hydraulic transmission is used for speed change by changing the discharge amount of a hydraulic pump or the capacity of a hydraulic motor, and is suitable for medium and small power transmission; the other type is hydraulic, adopts a hydraulic coupler or a hydraulic torque converter to carry out variable-speed transmission, and is suitable for high power. The common characteristics of the two are that the speed regulation range is large, the impact can be absorbed and overload can be prevented, but the manufacturing precision requirement is high, the price is high, the output characteristic is constant torque, the slip rate is large, and oil leakage is easy to occur during operation.
Mechanical continuously variable transmissions mostly rely on friction or oil film traction to transfer power, mainly by changing the ratio of the length (working diameter) between the drive members. Compared with other stepless speed change devices, the stepless speed change device has the advantages of simple structure, convenient operation, low price, stable transmission, reliable work, convenient maintenance, strong adaptability and the like. By integrating the above applications, the adoption of the stepless speed change transmission is beneficial to simplifying a speed change transmission scheme, improving the productivity and the product quality, reasonably utilizing power and saving energy, facilitating the realization of remote control and automatic control, and simultaneously is beneficial to reducing the labor intensity and improving the maneuvering performance. Continuously variable transmission is a basic general transmission type at present, and is widely applied to the industries of textile, light industry, food, packaging, machine tools, automobiles and the like. With the development of power electronics technology, various alternating current electric speed regulation modes are developed, and a novel switch reluctance speed regulation motor with better performance is developed in recent years, so that a certain impact is generated on a mechanical stepless speed changer. However, they have disadvantages such as a constant torque characteristic at a lower speed than the rated rotational speed of the motor, low and unstable low-speed operation efficiency, poor starting overload performance, and the like. In contrast, the mechanical stepless speed changer has the advantages of good constant power, stable rotating speed, reliable work, high efficiency, convenient maintenance, wide application range and the like, has wide prospect in industrial application and has irreplaceable function in many occasions.
Defects and deficiencies of the prior art: the structure of the mechanical stepless speed changer can be optimized through the chain belt and the conical wheel; the speed-regulating motor has the defects of only having constant torque characteristic, low-speed operation efficiency, instability, poor starting overload performance and unbalanced torque when being lower than the rated rotating speed of the motor.
Disclosure of Invention
The invention aims to provide a universal mechanical stepless speed changer and a speed changing method, which are used for solving the problems that the existing speed-regulating motor only has constant torque characteristic, low-speed operation efficiency, instability, poor starting overload performance and unbalanced torque when the speed-regulating motor is lower than the rated rotating speed of a motor.
The invention adopts the following technical scheme: a universal mechanical continuously variable transmission comprising: the transmission comprises a transmission input shaft, a shaft end seal, a bearing gland, an input end bearing, a wheel carrier bearing, a bevel sun gear I, a bevel planet gear I, a planet wheel carrier I, a bevel planet gear II, a differential wheel shaft, a bevel sun gear II, a bevel disc gear ring, a speed regulation large gear, a straight tooth gear ring, a straight tooth sun gear, an intermediate shaft, an output connecting flange, a speed regulation motor, a speed regulation pinion, a bevel planet gear III, a needle bearing, an input connecting flange, a bevel planet gear IV, an intermediate shaft support bearing, a straight tooth planet gear and a planet wheel carrier II.
The input connecting flange is sleeved on the transmission input shaft, an input end bearing is arranged at the joint of the input connecting flange and the transmission input shaft, the bearing cover is sleeved on the transmission input shaft and fixed on the input connecting flange, and a shaft end seal is arranged at the joint of the bearing cover and the transmission input shaft; the carrier bearing is sleeved and limited on the transmission input shaft, the planet carrier I is sleeved and rotatably arranged on the transmission input shaft, and the carrier bearing is arranged at the joint of the planet carrier I and the transmission input shaft; an intermediate shaft support bearing is arranged on the transmission input shaft; the bevel gear sun gear I is sleeved on the transmission input shaft and is fixedly connected with the transmission input shaft through a key; the bevel gear planetary gear I and the bevel gear planetary gear IV are in meshed connection with the bevel gear sun gear I and are symmetrically distributed on two sides of the transmission input shaft; the differential wheel shafts are symmetrically supported on two sides of the planetary wheel carrier I through needle bearings; the bevel gear planetary wheel I and the bevel gear planetary wheel II are sleeved and fixed on a differential wheel shaft positioned at one side of the planetary wheel carrier I; the bevel gear planetary gear IV and the bevel gear planetary gear III are sleeved and fixed on a differential wheel shaft positioned at the other side of the planetary wheel carrier I; the bevel disk gear ring is fixedly connected with the speed regulating large gear; the speed regulating large gear and the bevel disk gear ring form a planetary carrier, and a straight-tooth planetary gear is arranged on the planetary carrier; the straight-tooth planetary gear is in meshed connection with the straight-tooth sun gear and the straight-tooth gear ring; the straight-tooth sun gear is fixedly connected with the intermediate shaft; the straight tooth gear is sleeved on the intermediate shaft, one end of the intermediate shaft is supported in the output shaft through a bearing, the other end of the intermediate shaft is supported on the transmission input shaft through an intermediate shaft supporting bearing, and the bevel tooth sun gear II and the straight tooth sun gear are respectively sleeved at two ends of the intermediate shaft and fixedly connected to the intermediate shaft through keys, so that the intermediate shaft, the output shaft and the transmission input shaft can relatively rotate to form a revolute pair; the tail end of the intermediate shaft is sleeved in the output connecting shaft; the bevel gear sun gear II and the bevel gear planet gear III are sleeved and fixed on the differential wheel shaft; the bevel gear planetary gear III is connected with the straight gear planetary gear through a planetary gear carrier II, and the speed regulating pinion is sleeved on an output shaft of the speed regulating control motor and is fixedly connected through a key; the output shaft and the straight tooth gear ring are processed into a whole.
The carrier bearing, the bevel gear sun gear I, the bevel gear planet wheel I, the planet carrier I, the bevel gear planet wheel II, the differential wheel shaft and the bevel gear sun gear II form a planetary differential mechanism; the straight tooth gear ring, the straight tooth sun gear and the straight tooth planet gear jointly form a planetary reducer; the speed regulating function is realized by combining the planetary differential and the planetary reducer.
Preferably, the bevel disk gear ring, the speed regulating large gear and the planet carrier II are fixedly connected, and can be processed into a whole or respectively processed and then connected into a whole by bolts.
The invention adopts another technical scheme that: the speed changing method of the universal mechanical stepless speed changer comprises two speed regulating modes, wherein the two speed regulating modes are respectively as follows:
(1) When the speed regulation control motor is not in an energized state, the continuously variable transmission outputs at a constant speed ratio:
when the speed regulation control motor is not electrified, the brake of the dead brake at the tail end of the speed regulation control motor is locked, the speed regulation pinion and the speed regulation gear wheel do not rotate, the bevel disk gear ring fixedly connected with the speed regulation gear wheel of the transmission input shaft does not rotate, the bevel planet gears I-IV do planetary motion and drive the bevel sun gear II and the straight-tooth sun gear fixedly connected with the bevel sun gear II to rotate, at the moment, the continuously variable transmission outputs at a constant speed ratio, and the output speed ratio is the ratio of the number of teeth of the straight-tooth sun gear to the number of teeth of the straight-tooth gear ring.
(2) When the speed regulating control motor is electrified, the stepless speed changer regulates the output rotating speed through the two-stage combined action:
when the speed regulating motor has the rotation speed and torque output, the transmission is divided into two stages when the relation of the input/output rotation speed is calculated.
The first stage input is: the transmission input shaft is used for inputting the rotating speed, the rotating speed is sequentially transmitted to the bevel sun gear I and the bevel planet gear I, the transmission input shaft bevel planet gear I drives the differential wheel shaft to rotate, the transmission input shaft differential wheel shaft is transmitted to the bevel disc gear ring, and the transmission input shaft bevel planet gear I is further transmitted to the bevel sun gear II.
The second stage input is: an output shaft of a speed-regulating motor of an input shaft of the speed changer drives a speed-regulating pinion to drive and transmits to a speed-regulating gearwheel; the speed regulation large gear of the transmission input shaft is driven to the bevel disk gear ring; the transmission input shaft is provided with a transmission input shaft and a speed regulating motor, the two rotational speeds are synthesized and then output to a straight-tooth sun gear through a bevel-tooth sun gear II, and finally output through a straight-tooth gear ring and an output shaft fixedly connected with the straight-tooth gear ring.
The input/output rotation speed relation calculation of the first stage input is as follows:
the number of teeth of the bevel gear sun gear I is Y O The tooth number of the bevel planet wheel I is Y n The tooth number of the planetary wheel carrier I and the bevel planetary wheel II is Y m The tooth number of the bevel gear sun gear II is Y O The tooth number of the bevel disk gear ring is Y h The tooth number of the bevel planet wheel III is Y m The tooth number of the bevel planet wheel IV is Y n 。
The planetary carrier I is fixed after rotating by adopting a rotary arm fixing method, and the following steps are:
ω o1 -ω 8 ＝-(ω o2 -ω 8 )
wherein omega o1 : the speed of the bevel sun gear I; omega o2 : the speed of the bevel sun gear II; omega h : the speed of the bevel disk gear ring.
The input/output rotation speed relation calculation of the second stage input is as follows:
the number of teeth of the speed regulating pinion (20) is z 1 Gear of speed regulating large gear (13)The number is z x The number of teeth z of the straight-tooth sun gear (15) a The number of teeth z of the straight tooth gear ring (14) b The following steps are:
ω a : the speed of the spur sun gear (15); omega x : the speed of the speed regulating large gear (13); omega b : the speed of the straight tooth gear ring (14).
The total rotational speed input/output relationship is
ω a ＝ω o2 : the speed of the straight-tooth sun gear (15) is equal to that of the bevel-tooth sun gear II (11).
ω x ＝ω h : the speed of the speed regulating large gear (13) is equal to the speed of the bevel disk gear ring (12).
The output speed is:
the invention has the beneficial effects that: the invention adopts all-gear transmission stepless speed regulation, the transmission ratio in the whole transmission process is controllable and computable, and the transmission process has no difference and slip. The invention adopts all-gear transmission, and is superior to friction transmission in transmission stability and reliability; because the gear transmission process has no slippage, transmission errors are eliminated, the transmission ratio is accurate and can be calculated, and the transmission ratio has incomparable advantages on a precise transmission and servo control system.
Drawings
FIG. 1 is a cross-sectional view of a universal mechanical continuously variable transmission of the present invention;
FIG. 2 is a cross-sectional view of a planetary carrier in the universal mechanical continuously variable transmission of the present invention;
FIG. 3 is a cross-sectional view of a spur gear ring and an output shaft in the universal mechanical continuously variable transmission of the present invention;
FIG. 4 is a cross-sectional view of a bevel disk ring gear, a step-up gear, and a carrier II in a universal mechanical continuously variable transmission according to the present invention;
FIG. 5 is a cross-sectional view of the transmission input shaft in the universal mechanical continuously variable transmission of the present invention;
FIG. 6 is a cross-sectional view of the intermediate shaft of the universal mechanical continuously variable transmission of the present invention;
fig. 7 is a cross-sectional view of a differential axle of a universal mechanical continuously variable transmission of the present invention.
Wherein, 1, a transmission input shaft, 2, a shaft end seal, 3, a bearing gland, 4, an input end bearing, 5, a wheel carrier bearing, 6, a bevel gear sun wheel I,7, a bevel gear wheel I,8, a planet wheel carrier I,9, a bevel gear wheel II,10, a differential wheel shaft, 11, a bevel gear sun wheel II,12, a bevel disk gear ring, 13, a speed regulation large gear, 14, a straight gear ring, 15, a straight-tooth sun gear, 16, an intermediate shaft, 17, an output shaft, 18, an output connecting flange, 19, a speed regulating motor, 20, a speed regulating pinion, 21, a conical tooth planet gear III,22, a needle bearing, 23, an input connecting flange, 24, a conical tooth planet gear IV,25, an intermediate shaft supporting bearing, 26, a straight tooth planet gear and 27, a planet carrier II.
Detailed Description
The following description of the technical solutions in the embodiments of the present invention will be clear and complete, and it is obvious that the described embodiments are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Example 1
As shown in fig. 1 to 7, a universal mechanical continuously variable transmission includes: the transmission comprises a transmission input shaft 1, a shaft end seal 2, a bearing gland 3, an input end bearing 4, a carrier bearing 5, a bevel sun gear I6, a bevel planet gear I7, a planet carrier I8, a bevel planet gear II9, a differential wheel shaft 10, a bevel sun gear II11, a bevel disc gear ring 12, a speed regulating large gear 13, a straight tooth gear ring 14, a straight tooth sun gear 15, an intermediate shaft 16, an output shaft 17, an output connecting flange 18, a speed regulating motor 19, a speed regulating pinion 20, a bevel planet gear III 21, a needle bearing 22, an input connecting flange 23, a bevel planet gear IV 24, an intermediate shaft supporting bearing 25, a straight tooth planet gear 26 and a planet carrier II 27.
The input connecting flange 23 is sleeved on the transmission input shaft 1, an input end bearing 4 is arranged at the joint of the input connecting flange 23 and the transmission input shaft 1, the bearing gland 3 is sleeved on the transmission input shaft 1 and fixed on the input connecting flange 23, and a shaft end seal 2 is arranged at the joint of the bearing gland 3 and the transmission input shaft 1; the carrier bearing 5 is sleeved and limited on the transmission input shaft 1, the planet carrier I8 is sleeved and rotatably arranged on the transmission input shaft 1, and the carrier bearing 5 is arranged at the joint of the planet carrier I8 and the transmission input shaft 1; a middle shaft support bearing 25 is arranged on the transmission input shaft 1; the bevel gear sun gear I6 is sleeved on the transmission input shaft 1 and is fixedly connected with the transmission input shaft 1 through a key; the bevel gear planetary gear I7 and the bevel gear planetary gear IV 24 are in meshed connection with the bevel gear sun gear I6 and are symmetrically distributed on two sides of the transmission input shaft 1; the differential axle 10 is symmetrically supported on two sides of the planet wheel carrier I8 through needle bearings 22; the bevel gear planetary wheel I7 and the bevel gear planetary wheel II9 are sleeved and fixed on a differential wheel shaft 10 positioned at one side of the planetary wheel carrier I8; the bevel planet wheel IV 24 and the bevel planet wheel III 21 are sleeved and fixed on the differential wheel shaft 10 at the other side of the planet wheel carrier I8; the bevel disk gear ring 12 is fixedly connected with a speed regulating large gear 13; the speed regulating large gear 13 and the bevel disk gear ring 12 form a planetary carrier 27, and a straight-tooth planetary gear 26 is arranged on the planetary carrier; the straight-tooth planetary gear 26 is in meshed connection with the straight-tooth sun gear 15 and the straight-tooth gear ring 14; the straight-tooth sun gear 15 is fixedly connected with the intermediate shaft 16; the straight tooth gear ring 14 is sleeved on the intermediate shaft 16, one end of the intermediate shaft 16 is supported in the output shaft 17 through a bearing, the other end of the intermediate shaft 16 is supported on the transmission input shaft 1 through an intermediate shaft supporting bearing 25, and the bevel tooth sun gear II11 and the straight tooth sun gear 15 are respectively sleeved on two ends of the intermediate shaft 16 and fixedly connected to the intermediate shaft 16 through keys, so that the intermediate shaft 16, the output shaft 17 and the transmission input shaft 1 can relatively rotate to form a revolute pair; the tail end of the intermediate shaft 16 is sleeved in the output connecting shaft 17; the bevel gear sun gear II11 and the bevel gear planet gear III 21 are sleeved and fixed on the differential wheel shaft 10; the bevel gear planetary wheel III 21 is connected with the straight gear planetary wheel 26 through a planetary wheel carrier II 27, and the speed regulating pinion 20 is sleeved on the output shaft of the speed regulating control motor 19 and fixedly connected through a key; the output shaft 17 and the straight tooth gear ring 14 are processed into a whole;
the carrier bearing 5, the bevel gear sun gear I6, the bevel gear planet wheel I7, the planet carrier I8, the bevel gear planet wheel II9, the differential wheel shaft 10 and the bevel gear sun gear II11 form a planetary differential mechanism; the straight tooth gear ring 14, the straight tooth sun gear 15 and the straight tooth planet gears 26 together form a planetary reducer; the speed regulating function is realized by combining the planetary differential and the planetary reducer.
A speed change method for a universal mechanical continuously variable transmission comprises the steps of:
when the speed regulation control motor is not electrified, the brake lock of the dead brake at the tail end of the motor is locked, the speed regulation pinion 20 and the speed regulation gear wheel 13 do not rotate, the bevel disk gear ring 12 fixedly connected with the speed regulation gear wheel 13 does not rotate, the bevel planetary gears I-IV do planetary motion and drive the bevel sun gear II11 and the straight-tooth sun gear 15 fixedly connected with the bevel sun gear II to rotate, at the moment, the transmission outputs at a constant speed ratio, and the output speed ratio is the ratio of the number of teeth of the straight-tooth sun gear to the number of teeth of the straight-tooth gear ring.
When the speed regulating motor 19 has the rotation speed and torque output, the transmission can be divided into two stages when the relation of the input/output rotation speed is calculated; the first stage is a part from the transmission input shaft 1 to the bevel planet gear II9 and the bevel sun gear II 11; the second stage is the part from the bevel gear sun gear II11 to the output shaft 17; the transmission input shaft 1 and the speed regulating motor 19 are provided with rotational speed input, and the two rotational speeds are synthesized and then output to the straight-tooth sun gear 15 through the bevel-tooth sun gear II 11; finally, the output is carried out through the straight tooth gear ring 14 and an output shaft 17 fixedly connected with the straight tooth gear ring;
calculating the input/output rotation speed relation:
first stage:
the number of teeth of the bevel gear sun gear I6 is Y O The tooth number of the conical planetary gear I7 is Y n The tooth number of the planetary wheel carrier I8 and the bevel planetary wheel II9 is Y m The tooth number of the bevel gear sun gear II11 is Y O The number of teeth of the bevel disk gear ring 12 is Y h The number of teeth of the bevel planet wheel III 21 is Y m The tooth number of the bevel planet wheel IV 24 is Y n ；
The planet carrier I8 is fixed after rotating by adopting a rotating arm fixing method, and the following steps are:
ω o1 -ω 8 ＝-(ω o2 -ω 8 )
wherein omega o1 : the speed of the bevel sun gear I; omega o2 : the speed of the bevel sun gear II; omega h : the speed of the bevel disk gear ring;
second stage:
the number of teeth of the timing pinion 20 is z 1 The number of teeth of the speed regulating large gear 13 is z x Tooth number z of straight sun gear 15 a The number z of teeth of the straight-tooth ring gear 14 b Then there is
ω a : the speed of the spur sun gear 15;
ω x : the speed of the speed regulating large gear 13;
ω b : the speed of the straight-tooth ring gear 14;
total rotational speed input/output relationship:
ω a ＝ω o2 : the speed of the straight-tooth sun gear 15 is equal to the speed of the bevel-tooth sun gear II;
ω x ＝ω h : the speed of the speed regulating large gear 13 is equal to the speed of the bevel disk gear ring;
the output speed is:
the bevel gear sun gear I6, the bevel gear sun gear II11, the bevel gear planetary gear I7, the bevel gear planetary gear II9, the bevel gear planetary gear III 21, the bevel gear planetary gear IV 24, the planetary gear carrier I8 and the differential gear shaft 10 form a differential gear train, and the bevel gear sun gear II of the differential gear train 11 is connected with the straight-tooth sun gear 15 through an intermediate shaft; the bevel planet gears II9 and III 21 are meshed with the bevel disc gear ring 12; the bevel gear disc gear ring 12 is fixedly connected with the planet carrier II 27; the output shaft 17 is fixedly connected with the straight tooth gear ring, and the speed regulating motor is provided with a power-off brake.
The stepless speed change transmission is used as an ideal transmission type generally promoted in the mechanical industry, can maximally realize the optimal distribution of output torque and improve the energy utilization rate, and has long been studied. Currently, stepless speed regulators are mainly classified into "belt drive type" and "traction drive type". Wherein the belt transmission type transmits power through friction force between a flexible piece such as a belt or a chain and a belt wheel; the traction transmission type is to transmit power through friction force between the rigid revolution bodies; the traction transmission type is also divided into a double-cone disc type, a double-cone ring type, a planetary cone disc type, a roller half ring type, a roller full ring type, a spherical friction type and the like. The belt transmission type and the traction transmission type have the defects of poor sliding, transmission stability and reliability because the power is transmitted through friction force.
While the present invention has been described in detail through the foregoing description of the preferred embodiment, it should be understood that the foregoing description is not to be considered as limiting the invention. Many modifications and substitutions of the present invention will become apparent to those of ordinary skill in the art upon reading the foregoing. Accordingly, the scope of the invention should be limited only by the attached claims.
Claims (3)
1. A universal mechanical continuously variable transmission comprising: the transmission comprises a transmission input shaft (1), a shaft end seal (2), a bearing gland (3), an input end bearing (4), a carrier bearing (5), a bevel sun gear I (6), a bevel planet gear I (7), a planet carrier I (8), a bevel planet gear II (9), a differential wheel shaft (10), a bevel sun gear II (11), a bevel disc gear ring (12), a speed regulating large gear (13), a straight tooth gear ring (14), a straight tooth sun gear (15), an intermediate shaft (16), an output shaft (17), an output connecting flange (18), a speed regulating motor (19), a speed regulating pinion (20), a bevel planet gear III (21), a needle bearing (22), an input connecting flange (23), a bevel planet gear IV (24), an intermediate shaft supporting bearing (25), a straight tooth planet gear (26) and a planet carrier II (27);
the input connecting flange (23) is sleeved on the transmission input shaft (1), an input end bearing (4) is arranged at the joint of the input connecting flange (23) and the transmission input shaft (1), the bearing gland (3) is sleeved on the transmission input shaft (1) and fixed on the input connecting flange (23), and a shaft end seal (2) is arranged at the joint of the bearing gland (3) and the transmission input shaft (1); the carrier bearing (5) is sleeved and limited on the transmission input shaft (1), the planet carrier I (8) is sleeved and rotatably arranged on the transmission input shaft (1), and the carrier bearing (5) is arranged at the joint of the planet carrier I (8) and the transmission input shaft (1); the intermediate shaft support bearing (25) is arranged on the transmission input shaft (1); the bevel gear sun gear I (6) is sleeved on the transmission input shaft (1) and is fixedly connected with the transmission input shaft (1) through a key; the bevel gear planetary gears I (7) and the bevel gear planetary gears IV (24) are in meshed connection with the bevel gear sun gear I (6) and are symmetrically distributed on two sides of the transmission input shaft (1); the differential wheel shafts (10) are symmetrically supported on two sides of the planet wheel carrier I (8) through needle bearings (22); the bevel gear planetary wheel I (7) and the bevel gear planetary wheel II (9) are sleeved and fixed on a differential wheel shaft (10) positioned at one side of the planetary wheel carrier I (8); the bevel gear planetary gear IV (24) and the bevel gear planetary gear III (21) are sleeved and fixed on a differential wheel shaft (10) positioned at the other side of the planetary wheel carrier I (8); the bevel disk gear ring (12) is fixedly connected with the speed regulating large gear (13); the speed regulating large gear (13) and the bevel disk gear ring (12) form a planetary carrier (27), and a straight-tooth planetary gear (26) is arranged on the planetary carrier; the straight-tooth planetary gear (26) is in meshed connection with the straight-tooth sun gear (15) and the straight-tooth gear ring (14); the straight-tooth sun gear (15) is fixedly connected with the intermediate shaft (16); the straight-tooth gear ring (14) is sleeved on the intermediate shaft (16), one end of the intermediate shaft (16) is supported in the output shaft (17) through a bearing, the other end of the intermediate shaft is supported on the transmission input shaft (1) through an intermediate shaft supporting bearing (25), and the bevel gear sun gear II (11) and the straight-tooth sun gear (15) are respectively sleeved at two ends of the intermediate shaft (16) and fixedly connected to the intermediate shaft (16) through keys, so that the intermediate shaft (16), the output shaft (17) and the transmission input shaft (1) can relatively rotate to form a revolute pair; the tail end of the intermediate shaft (16) is sleeved in the output connecting shaft (17); the bevel gear sun gear II (11) and the bevel gear planet gear III (21) are sleeved and fixed on the differential wheel shaft (10); the bevel gear planetary wheel III (21) is connected with the straight gear planetary wheel (26) through the planetary wheel carrier II (27), and the speed regulating pinion (20) is sleeved on the output shaft of the speed regulating control motor (19) and fixedly connected through a key; the output shaft (17) and the straight tooth gear ring (14) are processed into a whole;
the carrier bearing (5), the bevel gear sun gear I (6), the bevel gear planet wheel I (7), the planet carrier I (8), the bevel gear planet wheel II (9), the differential wheel shaft (10) and the bevel gear sun gear II (11) form a planetary differential mechanism; the straight tooth gear ring (14), the straight tooth sun gear (15) and the straight tooth planet gear (26) form a planet speed reducer together; the speed regulating function is realized by combining the planetary differential and the planetary reducer.
2. A universal mechanical continuously variable transmission according to claim 1, wherein the bevel disk ring gear (12), the speed regulating gearwheel (13) and the planet carrier II (27) are fixedly connected and can be machined as one piece or separately machined and then bolted together.
3. A speed change method based on the universal mechanical continuously variable transmission as claimed in claim 1 or 2, characterized in that the speed change method comprises two speed change modes, respectively:
(1) When the speed regulation control motor is not in an energized state, the continuously variable transmission outputs at a constant speed ratio:
when the speed regulation control motor is not electrified, the brake of the dead brake at the tail end of the speed regulation control motor is locked, the speed regulation pinion (20) and the speed regulation large gear (13) do not rotate, the bevel disk gear ring (12) fixedly connected with the speed regulation large gear (13) also does not rotate, the bevel planetary gears I-IV do planetary motion, meanwhile, the bevel sun gear II (11) and the straight-tooth sun gear (15) fixedly connected with the bevel sun gear II are driven to rotate, the continuously variable transmission is output in a constant speed ratio, and the output speed ratio is the ratio of the number of teeth of the straight-tooth sun gear (15) to the number of teeth of the straight-tooth gear ring (14);
(2) When the speed regulating control motor is electrified, the stepless speed changer regulates the output rotating speed through the two-stage combined action:
when the speed regulating motor (19) has the rotation speed and torque output, the transmission is divided into two stages when the relation of the input/output rotation speed is calculated;
the first stage input is: the transmission input shaft (1) inputs rotating speed, the rotating speed is sequentially transmitted to a bevel sun gear I (6) and a bevel planet gear I (7), the bevel planet gear I (7) drives a differential wheel shaft (10) to rotate, the differential wheel shaft (10) is transmitted to a bevel disc gear ring (12), and the bevel planet gear I (7) is further transmitted to a bevel sun gear II (11);
the second stage input is: an output shaft of the speed regulating motor (19) drives a speed regulating pinion (20) to drive and transmits to a speed regulating large gear (13); the speed regulating large gear (13) is driven to the bevel disk gear ring (12); the transmission input shaft (1) and the speed regulating motor (19) are respectively provided with a rotating speed input, the two rotating speeds are synthesized and then output to the straight-tooth sun gear (15) through the bevel-tooth sun gear II (11), and finally output through the straight-tooth gear ring (14) and an output shaft (17) fixedly connected with the straight-tooth gear ring;
the input/output rotation speed relation calculation of the first stage input is as follows:
the number of teeth of the bevel gear sun gear I (6) is Y O The tooth number of the conical tooth planet wheel I (7) is Y n The tooth number of the bevel gear planet wheel II (9) of the planet wheel carrier I (8) is Y m The tooth number of the bevel gear sun gear II (11) is Y O The tooth number of the bevel disk gear ring (12) is Y h The tooth number of the conical tooth planet wheel III (21) is Y m The tooth number of the conical tooth planet wheel IV (24) is Y n ；
The planetary carrier I (8) is fixed after rotating by adopting a rotary arm fixing method, and then:
ω o1 -ω 8 ＝-(ω o2 -ω 8 )
wherein omega o1 : the speed of the bevel sun gear I; omega o2 : the speed of the bevel sun gear II; omega h : the speed of the bevel disk gear ring;
the input/output rotation speed relation calculation of the second stage input is as follows:
the number of teeth of the speed regulating pinion (20) is z 1 The number of teeth of the speed regulating large gear (13) is z x The number of teeth z of the straight-tooth sun gear (15) a The number of teeth z of the straight tooth gear ring (14) b The following steps are:
ω a : the speed of the spur sun gear (15); omega x : the speed of the speed regulating large gear (13); omega b : the speed of the straight tooth gear ring (14);
the total rotational speed input/output relationship is omega a ＝ω o2 : the speed of the straight-tooth sun gear (15) is equal to that of the bevel-tooth sun gear II (11); omega x ＝ω h : the speed of the speed regulating large gear (13) is equal to the speed of the bevel disk gear ring (12); the output speed is:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211618315.3A CN116292786A (en) | 2022-12-15 | 2022-12-15 | Universal mechanical stepless speed changer and speed changing method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211618315.3A CN116292786A (en) | 2022-12-15 | 2022-12-15 | Universal mechanical stepless speed changer and speed changing method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116292786A true CN116292786A (en) | 2023-06-23 |
Family
ID=86787563
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211618315.3A Withdrawn CN116292786A (en) | 2022-12-15 | 2022-12-15 | Universal mechanical stepless speed changer and speed changing method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116292786A (en) |
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2022
- 2022-12-15 CN CN202211618315.3A patent/CN116292786A/en not_active Withdrawn
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Application publication date: 20230623 |
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