Coordinated variable speed drive

Abstract

The present invention relates to a coordinated speed-changing drive device, wherein a driving pulley is connected to a driven pulley on an output shaft through a V-belt, the driving pulley comprises a left fixed disc and a right movable disc, the outer tenon of the left fixed disc is fixed on a primary input shaft, the right movable disc is sleeved on the outer tenon of the left fixed disc, a driving wheel compression spring is respectively arranged in the countersunk hole of the right movable disc, the right end of each driving wheel compression spring is commonly against the left end face of the fork flange, the fork flange is connected to the outer spline sleeve through an inner spline, the outer spline sleeve is fixed on the primary input shaft, the end face helical gear movable disc is installed on the central boss of the right end of the fork flange through its movable disc bearing, the right side of the end face helical gear movable disc forms a tooth-embedded meshing with the end face helical gear fixed disc, a clutch arm is arranged on the circumference of the end face helical gear movable disc, the end face helical gear fixed disc is supported on the primary input shaft through its fixed disc bearing, and the right end face of the end face helical gear fixed disc is provided with a circumferential limiting boss embedded in a box body. The mechanism can be adjusted online and has stable transmission.

Description

Technical Field

[0001] The invention relates to a coordinated speed-changing driving device, belonging to the technical field of transmissions. Background Art

[0002] Vehicle transmissions often use pulley drives and planetary speed change mechanisms. Pulley drives are a commonly used transmission method. Depending on different working objects and complex and changeable working environments, pulley transmission devices often need to be speed-regulated. The most common way to regulate the pulley speed is to change the diameter ratio of the master and slave pulleys.

[0003] Traditional planetary gears include an inner ring gear, a sun gear and a planetary gear. The planetary gear meshes between the sun gear and the inner ring gear, and the planetary gear shaft is fixed on the planetary bracket. There are many ways to input power, such as the planetary bracket is locked, the power is input from the sun gear and output from the inner ring gear; the planetary bracket is locked, the power is input from the inner ring gear and output from the sun gear; the inner ring gear is locked, the power is input from the sun gear and output from the planetary bracket; the inner ring gear is locked, the power is input from the sun gear and output from the planetary bracket; the inner ring gear is locked, the power is input from the planetary bracket and output from the sun gear; the sun gear is locked, the power is input from the planetary bracket and output from the inner ring gear; the sun gear is locked, the power is input from the inner ring gear and output from the planetary bracket, etc. When ordinary planetary gear mechanisms are used in special vehicles such as tractors, they often encounter many difficulties and are difficult to meet special application scenarios. For example, the vehicle speed can only be adjusted in a few gears, the output power is insufficient when the engine speed is reduced, or the inner ring gear is too large to be arranged, or the planetary gear, sun gear and inner ring gear cannot be arranged in the same plane, etc., which affects the use of planetary speed change mechanisms on special vehicles.

[0004] When a vehicle turns, the wheels rotate at different speeds. Each wheel travels a different distance, with the inner wheel traveling a shorter distance than the outer wheel. The gearbox of a traditional vehicle drives both wheels at the same time through the differential. When turning, the differential outputs two different speeds, causing the left and right wheels to roll at different speeds, ensuring that the drive wheels on both sides perform pure rolling motion.

[0005] With traditional differential steering, although the speed of the inner wheel is lower than that of the outer wheel and the driving distance is shorter, a larger turning radius is still required. The tractor's operating environment needs to be able to make sharp turns in areas close to the ridges, especially in the corners of the field. Otherwise, there will be large uncultivated areas in the corners of the field and in areas close to the ridges, which require manual remediation, greatly reducing the efficiency of farming, increasing the workload of manual labor, and being unfavorable to the promotion of modern automatic farming. In addition, there are often obstacles such as derricks and electric poles in the fields, which need to be bypassed closely during farming or harvesting, and these are the blind spots of traditional tractors.

[0006] In addition, when the tractor is operating, it is often necessary to switch between forward and reverse, so the traditional transmission drive axle cannot meet the above multiple working conditions. Summary of the invention

[0007] The purpose of the present invention is to overcome the problems existing in the prior art and provide a coordinated speed-changing drive device, which can adjust the speed of the belt transmission mechanism online without a tensioning wheel, and has a wide speed regulation range, the belt will not be loose, and the transmitted power is stable.

[0008] In order to solve the above technical problems, a coordinated speed change drive device of the present invention includes a belt transmission mechanism and a planetary speed change mechanism, wherein the belt transmission mechanism includes a driving pulley installed at the left end of a primary input shaft, the driving pulley is connected to the driven pulley through a V-belt, and the driven pulley is installed at the left end of a primary output shaft, the driving pulley includes a left fixed disc and a right moving disc, the outer tenon of the left fixed disc extends to the right and is fixed to the left end of the primary input shaft, the center boss of the right moving disc is sleeved on the outer tenon of the left fixed disc, and a plurality of right moving disc countersunk holes with openings at the right ends are evenly distributed on the center boss of the right moving disc, and each right moving disc has a right side. A driving wheel compression spring is respectively arranged in the countersunk hole, and the right end of each driving wheel compression spring abuts against the left end face of the shift fork flange together. The shift fork flange is connected to the outer spline sleeve through an inner spline, and the outer spline sleeve is fixed on the primary input shaft. The central boss of the shift fork flange extends to the right, and the end face helical gear movable plate is installed on the central boss of the shift fork flange through its movable plate bearing. The right side of the end face helical gear movable plate forms a tooth-engaged engagement with the end face helical gear fixed plate. A clutch arm extending outward is arranged on the circumference of the end face helical gear movable plate. The end face helical gear fixed plate is supported on the primary input shaft through its fixed plate bearing, and the right end face of the end face helical gear fixed plate is provided with a fixed plate circumferential limiting boss embedded in the groove of the box body.

[0009] Compared with the prior art, the present invention has achieved the following beneficial effects: the primary input shaft drives the left fixed disc and the right moving disc to rotate, the two side walls of the V-belt are clamped between the left fixed disc and the right moving disc and rotate accordingly, the fork flange rotates synchronously with the driving pulley, and the V-belt drives the driven pulley to rotate. The right moving disc can only translate on the outer tenon of the left fixed disc, ensuring that the right moving disc and the left fixed disc will not rotate relative to each other. The right end of the end face helical tooth fixed disc is fixed to the box body through the fixed disc circumferential limiting boss. When the clutch arm rotates the end face helical toothed fixed disc in the positive direction, the meshing surface of the end face helical toothed fixed disc is pushed out to the left, the end face helical toothed fixed disc pushes the fork flange to the left, and the fork flange slides to the left on the outer spline sleeve to push the right moving disc to the left, so that the distance between the right moving disc and the left fixed disc is reduced, the V-belt is pushed out to the outer periphery, and the driving pulley presents a large diameter working state. When the clutch arm rotates the end face helical gear moving plate in the opposite direction, the end face helical gear moving plate moves to the right, and the right moving plate and the fork flange move to the right, so that the distance between the right moving plate and the left fixed plate increases, and the tension of the V-belt itself moves it to the inner periphery of the driving pulley, and the driving pulley presents a small diameter working state. The tension of the driving pulley compression spring keeps the fork flange and the end face helical gear moving plate in good axial close contact at all times. After the end face helical gear moving plate moves to the right, the right moving plate and the left fixed plate keep pressure contact on both sides of the V-belt, and the V-belt will not slip when starting again.

[0010] As an improvement of the present invention, the helical teeth of the end face helical gear movable plate and the end face helical gear fixed plate cooperate with each other through steel balls, and the two sides of the steel balls are respectively embedded in the arc-shaped ball paths of the corresponding tooth grooves. The helical teeth of the end face helical gear movable plate and the end face helical gear fixed plate are contacted through steel balls instead of directly contacting each other, which reduces the friction force when the end face helical gear movable plate and the end face helical gear fixed plate are engaged or disengaged, prolongs the service life, and makes the rotation of the end face helical gear movable plate smoother.

[0011] As a further improvement of the present invention, the outer tenon of the left fixed disc is correspondingly embedded in the inner groove of the central boss of the right movable disc, and the outer groove of the left fixed disc is formed between the adjacent outer tenons of the left fixed disc, and the inner tenon of the central boss of the right movable disc is correspondingly embedded in the corresponding outer groove of the left fixed disc. The outer tenon of the left fixed disc is embedded in the inner groove of the right movable disc, and the inner tenon of the right movable disc is embedded in the outer groove of the left fixed disc, so that the right movable disc and the left fixed disc are radially positioned but can slide axially, which can not only adjust the distance between the right movable disc and the left fixed disc, but also prevent the right movable disc from slipping relative to the left fixed disc.

[0012] As a further improvement of the present invention, a retaining spring is embedded on the outer periphery of the right end of the outer spline sleeve, and the retaining spring is located on the right side of the central boss of the fork flange. The retaining spring limits the right stroke of the fork flange, indirectly limiting the maximum distance between the right movable disc and the left fixed disc.

[0013] As a further improvement of the present invention, the right end of the inner ring of the fixed plate bearing abuts against the shoulder of the primary input shaft, the right end of the outer spline sleeve abuts against the left side of the inner ring of the fixed plate bearing, the left end of the outer spline sleeve is embedded in the inner step hole of the left fixed plate, and the left fixed plate fixing screw is screwed on the left end center of the primary input shaft and pressed against the outer end center of the left fixed plate through a gasket. The left fixed plate fixing screw presses the left fixed plate, the outer spline sleeve and the inner ring of the movable plate bearing through the gasket, so that the three are axially positioned on the primary input shaft; the left fixed plate and the outer spline sleeve are radially positioned with the primary input shaft through a flat key; the left end of the outer spline sleeve is embedded in the inner step hole of the left fixed plate, so that the two are both axially positioned and circumferentially positioned.

[0014] As a further improvement of the present invention, the driven pulley comprises a right fixed disc and a left movable disc, the center column of the right fixed disc extending to the left and fixed to the left end of the output shaft, the outer periphery of the center column of the right fixed disc is provided with a right fixed disc outer spline, the left movable disc is sleeved on the right fixed disc outer spline through an inner spline, and the left port of the left movable disc is symmetrically provided with a left movable disc support ear extending toward the axial direction; the right fixed disc center column is evenly provided with a through right fixed disc center column through hole and a right fixed disc countersunk hole open at the right end, each right fixed disc countersunk hole is respectively provided with a driven wheel compression spring, the right end of each driven wheel compression spring is provided with a pressure plate, and each spacer sleeve is respectively supported between the pressure plate and the corresponding left movable disc support ear, and a plurality of long-rod screws are evenly inserted on the pressure plate from right to left, and each long-rod screw passes through the corresponding spacer sleeve and is screwed into the screw hole of the left movable disc support ear. The fixing screw of the right fixed disc fixes the right fixed disc on the left end shoulder of the output shaft through the gasket. The spacer realizes the axial positioning between the pressure plate and the left movable disc support ear, and provides the passage space for the long rod screw, so that the left movable disc and the pressure plate located on both sides of the right fixed disc form a rigid whole. The left movable disc is in a floating state, and the inner spline of the left movable disc is sleeved on the outer spline of the right fixed disc and can slide axially. The tension of the compression springs of each driven wheel pushes the pressure plate to the right, and the pressure plate pushes the left movable disc to the right through the long rod screw and the left movable disc support ear to clamp the V-belt. Since the center distance between the driving pulley and the driven pulley remains unchanged, when the driving pulley switches to the large-diameter working state, the driven pulley automatically switches to the small-diameter working state under the pressure of the V-belt; conversely, when the driving pulley switches to the small-diameter working state, the pressure of the V-belt on the driven pulley disc decreases, and under the tension of the driven pulley compression spring, the left driven disc moves right, and the driven pulley automatically switches to the large-diameter working state. In this way, the online adjustment of the diameter ratio of the driving pulley and the driven pulley can be achieved by rotating the end face helical gear driven disc through the clutch pull arm, thereby achieving the online change of the transmission ratio between the primary input shaft and the output shaft, and in the process of speed regulation, the transmission of the V-belt is reliable, and the belt will not slip when restarting.

[0015] As a further improvement of the present invention, the planetary speed change mechanism includes an external gear planet carrier plate, a primary gear is installed in the middle section of the primary input shaft, the primary gear is meshed with the external gear planet carrier plate, the center of the external gear planet carrier plate is supported on the middle section of the secondary input shaft through a bearing, a planet carrier is fixedly installed on the right end surface of the external gear planet carrier plate, planetary shafts are symmetrically installed on the planet carrier, each planetary shaft is supported on the external gear planet carrier plate through a bearing, a double planetary gear is installed in the middle section of each planetary shaft, and each double planetary gear includes a double large planetary gear and a double small planetary gear arranged from left to right. ; A primary output gear is installed at the right end of the primary output shaft, and the primary output gear is meshed with the secondary input large gear through a bridge gear. The secondary input large gear is fixed to the left end of the secondary input shaft, and a secondary input small sun gear is provided at the right end of the secondary input shaft, and the secondary input small sun gear is meshed with each of the double large planetary gears; a secondary output shaft is coaxially provided on the right side of the secondary input shaft, and the left end of the secondary output shaft is supported in the inner hole of the planetary carrier through a bearing and a secondary output large sun gear is fixed to the left end, and the secondary output large sun gear is meshed with each of the double small planetary gears. The primary gear on the primary input shaft drives the outer gear planet carrier disk to rotate and realize the primary reduction. The outer gear planet carrier disk drives the planet carrier and three planetary shafts to revolve synchronously. The revolution speed ratio of the outer gear planet carrier disk and the rotation speed of the primary input shaft remains unchanged and is in the opposite direction. The bearing allows the secondary input shaft and the outer gear planet carrier disk to rotate relative to each other. The primary output gear at the right end of the primary output shaft drives the secondary input large gear to rotate through the bridge gear. The secondary input large gear drives the secondary input shaft to rotate. The secondary input shaft drives the double large planetary gears to rotate through the secondary input small sun gear. The revolution direction of the planetary shaft is opposite to that of the secondary input small sun gear. The two jointly determine the rotation speed of the double large planetary gears. The bearing allows the secondary output shaft and the planet carrier to rotate relative to each other. The double small planetary gears synchronously drive the secondary output large sun gear to rotate and realize further reduction of the secondary output shaft. When the speed of the secondary input small sun gear is equal to the revolution speed of the outer gear planet carrier, the speed of each double planetary gear is zero, so that the secondary output shaft can be changed from zero speed to the maximum speed by changing the speed of the secondary input small sun gear while the speed of the primary input shaft remains unchanged, thus realizing stepless speed change. Moreover, the primary input shaft and the secondary input shaft jointly drive the secondary output shaft to rotate, thus improving the output power and making speed regulation more convenient while maintaining high power output.

[0016] As a further improvement of the present invention, a two-way clutch is installed in the middle section of the secondary output shaft through a spline, an idler gear 1 is installed on the left side of the two-way clutch, the idler gear 1 is meshed with gear 2, the gear 2 is fixed to the left end of the intermediate shaft 1, the other side of the gear 2 is meshed with gear 3, and the gear 3 is fixed to the middle section of the main drive shaft; a left idler gear and a left clutch for controlling the left idler gear are installed on the left side of the gear 3, and a right idler gear and a right clutch for controlling the right idler gear are installed on the right side of the gear 3; the left idler gear is meshed with the left half-shaft gear, and the right idler gear is meshed with the right half-shaft gear; the left half-shaft gear is installed at the right end of the left half-shaft, and the left wheel connecting flange is installed at the left end of the left half-shaft; the right half-shaft gear is installed at the left end of the right half-shaft, and the right wheel connecting flange is installed at the right end of the right half-shaft. When in forward gear, the left side of the two-way clutch is engaged, so that the idler gear 1 is fixed on the secondary output shaft, and the secondary output shaft drives the gear 2 to rotate through the idler gear 1, and the gear 2 drives the gear 3 and the main drive shaft to rotate in the positive direction. When both the left clutch and the right clutch are engaged, the left idler gear and the right idler gear are fixedly connected to the main drive shaft, and the left idler gear drives the left half shaft to rotate through the left half shaft gear, and the left half shaft drives the left wheel to rotate through the left wheel connecting flange; the right idler gear drives the right half shaft to rotate through the right half shaft gear, and the right half shaft drives the right wheel to rotate through the right wheel connecting flange, so that the vehicle moves in a straight line. When the left clutch is engaged alone, the left idler gear is fixedly connected to the main drive shaft, and the left idler gear drives the left half shaft and the left wheel to rotate alone through the left half shaft gear; the right idler gear is suspended on the main drive shaft, and the right wheel remains stationary, and the vehicle turns right with a very small turning radius. When the right clutch is engaged alone, the right idler gear is fixedly connected to the main drive shaft, and the right idler gear drives the right half shaft and the right wheel to rotate independently through the right half shaft gear; the left idler gear is suspended on the main drive shaft, the left wheel remains stationary, and the vehicle turns left with a very small turning radius. In this way, you can switch to turn left, walk, turn right, etc. at any time, and greatly reduce the turning radius of engineering vehicles such as tractors, meeting the operating needs of various working conditions.

[0017] As a further improvement of the present invention, an idler gear 4 is installed on the right side of the two-way clutch, and the idler gear 4 meshes with the idler gear 5. The idler gear 5 is mounted on the right end of the intermediate shaft 1, and the other side of the idler gear 5 meshes with the gear 6. The gear 6 is fixed to the right end of the intermediate shaft 2, and the left end of the intermediate shaft 2 is fixedly installed with the gear 7, and the gear 7 meshes with the gear 3. In the reverse gear, the right side of the two-way clutch is combined, so that the idler gear 4 is fixed on the secondary output shaft, and the secondary output shaft drives the idler gear 5 to rotate on the intermediate shaft 1 through the idler gear 4, and the idler gear 5 drives the intermediate shaft 2 to rotate through the gear 6, and the intermediate shaft 2 drives the gear 3 to rotate in the opposite direction through the gear 7, and the gear 3 drives the main drive shaft to rotate in the opposite direction. At the same time, the gear 3 drives the gear 2 and the intermediate shaft 1 to rotate in suspension, and the gear 2 drives the idler gear 1 to rotate in suspension. In the forward gear, the gear 3 drives the intermediate shaft 2 and the gear 6 to rotate in suspension through the gear 7, and the gear 6 drives the idler gear 5 to rotate in suspension on the intermediate shaft 1, and the idler gear 5 drives the idler gear 4 to rotate in suspension.

[0018] As a further improvement of the present invention, the two-way clutch is controlled by the forward and reverse gear shift fork, the driving shaft of the forward and reverse gear shift fork is fixed at the center of the forward and reverse gear winch, and the outer peripheral rope groove of the forward and reverse gear winch is wrapped with a shift rope; the left clutch is controlled by the left clutch arm, and the driving end of the left clutch arm is controlled by the left steering rope; the right clutch is controlled by the right clutch arm, and the driving end of the right clutch arm is controlled by the right steering rope. The forward and reverse gear winch is driven to rotate by the shift rope, and the forward and reverse gear winch drives the forward and reverse gear shift fork to swing to the left, then the two-way clutch switches to the forward gear; the forward and reverse gear shift fork swings to the right, then the two-way clutch switches to the reverse gear. The left clutch and the right clutch are normally in a combined state. When the left steering rope is pulled, the left clutch arm rotates to switch the left clutch to a disengaged state, cutting off the power of the left wheel. When the right steering rope is pulled, the right clutch arm rotates to switch the right clutch to a disengaged state, cutting off the power of the right wheel. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is a front view of the coordinated variable speed drive device of the present invention.

[0020] Figure 2 This is a schematic diagram of the structure of the present invention without the box body.

[0021] Figure 3 It is a three-dimensional diagram of the coordinated variable speed drive device of the present invention.

[0022] Figure 4 This is a three-dimensional diagram of the present invention without the box body and the cover shell.

[0023] Figure 5 It is a front view of the belt transmission mechanism in the present invention.

[0024] Figure 6 for Figure 5 Stereoscopic diagram.

[0025] Figure 7 for Figure 6 Exploded diagram.

[0026] Figure 8 It is the front view of the planetary speed change mechanism in the present invention.

[0027] Fig. 9 for Figure 8 Stereoscopic diagram.

[0028] Fig.10 for Fig. 9 Exploded diagram.

[0029] Fig.11 It is a three-dimensional diagram of the forward and reverse driving mechanism in the present invention.

[0030] Fig.12 It is the gear transmission diagram when the present invention moves forward.

[0031] Fig.13 It is the gear transmission diagram of the present invention when moving backward.

[0032] In the figure: 1. Primary input shaft; 1a. Primary gear; 2a. Left fixed plate; 2a1. External tenon of left fixed plate; 2a2. External slide groove of left fixed plate; 2a3. Fixing screw of left fixed plate; 2b. Right movable plate; 2b1. Countersunk hole of right movable plate; 2b2. Compression spring of driving wheel; 3. Internal splined fork flange; 3a. Center boss of fork flange; 4. External splined sleeve; 4a. Circlip; 5. End face helical gear movable plate; 5a. Clutch arm; 5b. Moving plate bearing; 6. Steel ball; 7. End face helical gear fixed plate; 7a. Circumferential limit boss of fixed plate; 7b. Fixed plate bearing; 8a. Right fixed plate; 8a1. External spline of right fixed plate; 8a2. Countersunk hole of right fixed plate; 8a3. Compression spring of driven wheel; 8a4. Spacer; 8a5. Fixing screw of right fixed plate; 8b. Left moving plate; 8b1. Internal spline of left moving plate; 8b2. Support ear of left moving plate; 9. Pressure plate; 9a. Long rod screw; 10. V-belt; 11. Primary output shaft; 11a. Primary output gear; 11b. Bridge gear; 12. External gear planet carrier plate; 12a. Planet carrier; 12b. Planet shaft; 12c. Double planetary gear; 12c1. Double large planetary gear; 12c2. Double small planetary gear; 13. Secondary input shaft; 13a. Secondary input large gear; 13b. Secondary input small sun gear; 14. Secondary output shaft; 14a. Secondary output large sun gear; 14b. Idle gear one; 14c. Two-way clutch; 14c1. Forward and reverse gear winch; 14c2. Forward and reverse gear shift fork; 14c3. Shift rope; 14d. Idle gear four; 15. Intermediate shaft one; 15a. Gear two; 15b. Idle gear five; 16. Intermediate shaft two; 16a. Gear six; 16b. Gear seven; 17. Main drive shaft; 17a. Left clutch; 17a1. Left clutch arm; 17a2. Left steering rope; 17b. Left idler gear; 17c. Gear three; 17d. Right idler gear; 17e. Right clutch; 17e1. Right clutch arm; 17e2. Right steering rope; 18. Left half shaft; 18a. Left wheel connecting flange; 18b. Left half shaft gear; 19. Right half shaft; 19a. Right wheel connecting flange; 19b. Right half shaft gear. DETAILED DESCRIPTION

[0033] In the following description of the present invention, the terms "left", "right", "inside", "outside", etc. indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not mean that the device must have a specific direction.

[0034] like Figures 1 to 7As shown, the coordinated speed change drive device of the present invention includes a belt transmission mechanism, a planetary speed change mechanism and a gearbox drive axle. The primary input shaft 1 is supported on the housing by a bearing, and the belt transmission mechanism includes a driving pulley installed at the left end of the primary input shaft 1, and the driving pulley is connected to the driven pulley through a V-belt 10, and the driven pulley is installed at the left end of the output shaft 11. The driving pulley includes a left fixed disc 2a and a right moving disc 2b, and the outer tenon of the left fixed disc 2a extends to the right and is fixed to the left end of the primary input shaft 1, and the center boss of the right moving disc 2b is sleeved on the outer tenon 2a1 of the left fixed disc, and a plurality of right moving disc countersunk holes 2b1 with right end openings are evenly distributed on the center boss of the right moving disc, and each right moving disc countersunk hole 2b1 is respectively provided with a driving wheel compression spring 2b2, and each main The right end of the moving wheel compression spring 2b2 is jointly against the left end face of the shift fork flange 3. The shift fork flange 3 is mounted on the outer spline sleeve 4 through an inner spline. The outer spline sleeve 4 is fixed on the primary input shaft 1. The central boss of the shift fork flange 3 extends to the right. The end face helical gear moving plate 5 is installed on the central boss 3a of the shift fork flange through its moving plate bearing 5b. The right side of the end face helical gear moving plate 5 forms a tooth-engaged engagement with the end face helical gear fixed plate 7. A clutch arm 5a extending outward is provided on the circumference of the end face helical gear moving plate 5. The end face helical gear fixed plate 7 is supported on the primary input shaft 1 through its fixed plate bearing 7b. The right end face of the end face helical gear fixed plate 7 is provided with a fixed plate circumferential limiting boss 7a embedded in the groove of the box body.

[0035] The primary input shaft 1 drives the left fixed disc 2a and the right moving disc 2b to rotate, and the two side walls of the V-belt 10 are clamped between the left fixed disc 2a and the right moving disc 2b and rotate accordingly. The fork flange 3 rotates synchronously with the driving pulley, and the V-belt 10 drives the driven pulley to rotate. The right moving disc 2b can only translate on the outer tenon 2a1 of the left fixed disc to ensure that the right moving disc 2b and the left fixed disc 2a will not rotate relative to each other. The right end of the end face helical tooth fixed disc 7 is fixed to the box body through the fixed disc circumferential limit boss 7a.

[0036] When the clutch arm 5a rotates the end face bevel gear movable plate 5 in the positive direction, it is pushed leftward by the meshing surface of the end face bevel gear fixed plate 7, and the end face bevel gear movable plate 5 pushes the fork flange 3 to the left. The fork flange 3 slides to the left on the outer spline sleeve 4 to push the right movable plate 2b to the left, so that the distance between the right movable plate 2b and the left fixed plate 2a is reduced, and the V-belt 10 is pushed outward, and the driving pulley presents a large diameter working state.

[0037] When the clutch arm 5a rotates the end face helical geared movable disc 5 in the opposite direction, the end face helical geared movable disc 5 moves to the right, and the right movable disc 2b and the fork flange 3 move to the right, so that the distance between the right movable disc 2b and the left fixed disc 2a becomes larger, and the tension of the V-belt 10 itself makes it move toward the inner periphery of the driving pulley, and the driving pulley presents a small-diameter working state. The tension of the driving wheel compression spring 2b2 keeps the fork flange 3 and the end face helical geared movable disc 5 in good axial close contact at all times. After the end face helical geared movable disc 5 moves to the right, the right movable disc 2b and the left fixed disc 2a maintain pressure contact on both sides of the V-belt 10, and the V-belt 10 will not slip when starting again.

[0038] The helical teeth of the end face helical gear moving plate 5 and the end face helical gear fixed plate 7 cooperate with each other through the steel ball 6, and the two sides of the steel ball 6 are respectively embedded in the arc-shaped ball track of the corresponding tooth groove. The helical teeth of the end face helical gear moving plate 5 and the end face helical gear fixed plate 7 are contacted through the steel ball 6 instead of directly contacting each other, which reduces the friction force when the end face helical gear moving plate 5 and the end face helical gear fixed plate 7 are engaged and disengaged, prolongs the service life, and makes the rotation of the end face helical gear moving plate 5 smoother.

[0039] The outer tenon 2a1 of the left fixed disc is correspondingly embedded in the inner groove of the central boss of the right movable disc, and the outer groove 2a2 of the left fixed disc is formed between the adjacent outer tenons 2a1 of the left fixed disc, and the inner tenon of the central boss of the right movable disc is correspondingly embedded in the corresponding outer groove 2a2 of the left fixed disc. The outer tenon 2a1 of the left fixed disc is embedded in the inner groove of the right movable disc, and the inner tenon of the right movable disc is embedded in the outer groove 2a2 of the left fixed disc, so that the right movable disc 2b and the left fixed disc 2a are radially positioned but can slide axially, which can adjust the distance between the right movable disc 2b and the left fixed disc 2a and prevent the right movable disc 2b from slipping relative to the left fixed disc 2a.

[0040] A retaining spring 4a is embedded on the outer periphery of the right end of the outer spline sleeve 4, and the retaining spring 4a is located on the right side of the central boss 3a of the fork flange. The retaining spring 4a limits the right stroke of the fork flange 3, and indirectly limits the maximum distance between the right movable disc 2b and the left fixed disc 2a.

[0041] The right end of the inner ring of the fixed plate bearing 7b abuts against the shoulder of the primary input shaft 1, the right end of the outer spline sleeve 4 abuts against the left side of the inner ring of the fixed plate bearing 7b, the left end of the outer spline sleeve 4 is embedded in the inner step hole of the left fixed plate 2a, and the left fixed plate fixing screw 2a3 is screwed on the left end center of the primary input shaft 1 and pressed against the outer end center of the left fixed plate 2a through a gasket. The left fixed plate fixing screw 2a3 presses the left fixed plate 2a, the outer spline sleeve 4 and the inner ring of the fixed plate bearing 7b through a gasket, so that the three are axially positioned on the primary input shaft 1; the left fixed plate 2a and the outer spline sleeve 4 are radially positioned with the primary input shaft 1 through a flat key; the left end of the outer spline sleeve 4 is embedded in the inner step hole of the left fixed plate 2a, so that the two are both axially positioned and circumferentially positioned.

[0042] The driven pulley comprises a right fixed disc 8a and a left movable disc 8b. The center column of the right fixed disc 8a extends to the left and is fixed to the left end of the output shaft 11. The outer periphery of the center column of the right fixed disc is provided with a right fixed disc outer spline 8a1. The left movable disc 8b is sleeved on the right fixed disc outer spline 8a1 through the left movable disc inner spline 8b1. The left end of the left movable disc 8b is symmetrically provided with a left movable disc support ear 8b2 extending in the axial direction. The center column of the right fixed disc is evenly provided with a through hole of the center column of the right fixed disc and a right end opening. The right fixed disc countersunk hole 8a2 of the mouth, each right fixed disc countersunk hole 8a2 is respectively provided with a driven wheel compression spring 8a3, the right end of each driven wheel compression spring 8a3 is provided with a pressure plate 9, each right fixed disc central column through hole is respectively provided with a spacer sleeve 8a4, each spacer sleeve 8a4 is respectively supported between the pressure plate 9 and the corresponding left movable disc support ear 8b2, a plurality of long rod screws 9a are evenly inserted on the pressure plate 9 from right to left, each long rod screw 9a respectively passes through the corresponding spacer sleeve 8a4 and is screwed into the screw hole of the left movable disc support ear 8b2.

[0043] The right fixed disc fixing screw 8a5 fixes the right fixed disc 8a to the left end shoulder of the output shaft 11 through a gasket, and the spacer 8a4 realizes the axial positioning between the pressure plate 9 and the left movable disc support ear 8b2, providing a passage space for the long rod screw 9a, so that the left movable disc 8b and the pressure plate 9 located on both sides of the right fixed disc 8a form a rigid whole. The left movable disc 8b is in a floating state, and the inner spline 8b1 of the left movable disc is sleeved on the outer spline 8a1 of the right fixed disc and can slide axially. The tension of the compression spring 8a3 of each driven wheel pushes the pressure plate 9 to the right, and the pressure plate 9 pushes the left movable disc 8b to the right through the long rod screw 9a and the left movable disc support ear 8b2 to clamp the V-belt 10.

[0044] Since the center distance between the driving pulley and the driven pulley remains unchanged, when the driving pulley switches to the large-diameter working state, the driven pulley automatically switches to the small-diameter working state under the pressure of the V-belt 10; conversely, when the driving pulley switches to the small-diameter working state, the pressure of the V-belt 10 on the driven pulley disc decreases, and under the tension of the driven pulley compression spring 8a3, the left driven disc 8b moves right, and the driven pulley automatically switches to the large-diameter working state. In this way, the diameter ratio of the driving pulley and the driven pulley can be adjusted online by rotating the end face helical gear driven disc 5 through the clutch arm 5a, thereby realizing the online change of the transmission ratio between the primary input shaft 1 and the output shaft 11, and in the speed regulation process, the transmission of the V-belt 10 is reliable, and the belt will not slip when restarting.

[0045] Figures 8 to 10It is a planetary speed change mechanism. The middle section of the first-stage input shaft 1 is equipped with a primary gear 1a, which meshes with the outer gear planet carrier plate 12. The center of the outer gear planet carrier plate 12 is supported on the middle section of the second-stage input shaft 13 through a bearing. The left end of the second-stage input shaft 13 is equipped with a second-stage input large gear 13a. The left and right sides of the second-stage input large gear 13a are respectively equipped with bearings and supported in the wall of the box through the bearings. The right end surface of the outer gear planet carrier plate 12 is fixedly equipped with a planet carrier 12a. Planet shafts 12b are symmetrically installed on the planet carrier 12a. Each planet shaft 12b is supported on the outer gear planet carrier plate 12 through a bearing. The middle section of each planet shaft 12b is equipped with a double planetary gear 12c. Each double planetary gear 12c includes a double large planetary gear 12c1 and a double small planetary gear 12c2 arranged from left to right.

[0046] A primary output gear 11a is installed at the right end of the primary output shaft 11, and the primary output gear 11a is meshed with the secondary input large gear 13a through the bridge gear 11b. The secondary input large gear 13a is fixed to the left end of the secondary input shaft 13, and a secondary input small sun gear 13b is provided at the right end of the secondary input shaft 13, and the secondary input small sun gear 13b is meshed with each double-linked large planetary gear 12c1; a secondary output shaft 14 is coaxially provided on the right side of the secondary input shaft 13, and the middle section of the secondary output shaft 14 is supported in the wall of the box through a bearing, and the left end of the secondary output shaft 14 is supported in the inner hole of the planet carrier 12a through a bearing and a secondary output large sun gear 14a is fixed to the left end, and the secondary output large sun gear 14a is meshed with each double-linked small planetary gear 12c2.

[0047] The primary gear 1a on the primary input shaft 1 drives the outer gear planet carrier plate 12 to rotate and realize the first-stage reduction. The outer gear planet carrier plate 12 drives the planet carrier 12a and the three planet shafts 12b to revolve synchronously. The revolving speed ratio of the outer gear planet carrier plate 12 and the primary input shaft 1 is constant and the direction is opposite. The bearing enables the secondary input shaft 13 and the outer gear planet carrier plate 12 to rotate relative to each other. The primary output gear 11a at the right end of the primary output shaft 11 drives the secondary input large gear 13a to rotate through the bridge gear 11b. The secondary input large gear 13a drives the secondary input shaft 13 to rotate. The secondary input shaft 13 drives the double-linked large planetary gear 12c1 to rotate through the secondary input small sun gear 13b. The revolution direction of the planetary shaft 12b is opposite to the rotation direction of the secondary input small sun gear 13b. The revolution speed of the planetary shaft 12b and the rotation speed of the secondary input small sun gear 13b jointly determine the rotation speed of the double-linked large planetary gear 12c1. The bearing enables the secondary output shaft 14 and the planet carrier 12a to rotate relative to each other. The double-linked small planetary gear 12c2 synchronously drives the secondary output large sun gear 14a to rotate and realizes further deceleration of the secondary output shaft 14. When the rotation speed of the secondary input small sun gear 13b is equal to the revolution speed of the external gear planet carrier plate 12, the rotation speed of each double-linked planetary gear 12c is zero, thereby realizing that when the speed of the primary input shaft 1 remains unchanged, the rotation speed of the secondary input small sun gear 13b can change the secondary output shaft 14 from zero speed to the maximum speed, thereby realizing stepless speed change. Moreover, the primary input shaft 1 and the secondary input shaft 13 jointly drive the secondary output shaft 14 to rotate, thereby increasing the output power and making speed regulation more convenient while maintaining high power output.

[0048] like Figures 1 to 4 , Fig.11 As shown, in the transmission drive axle, the left wheel connecting flange 18a is installed at the left end of the left half shaft 18, and the left half shaft gear 18b is installed at the right end of the left half shaft 18; the right wheel connecting flange 19a is installed at the right end of the right half shaft 19, and the right half shaft gear 19b is installed at the left end of the right half shaft 19; the middle section of the secondary output shaft 14 is installed with a two-way clutch 14c through a spline, and an idler gear 14b is installed on the left side of the two-way clutch 14c, and the idler gear 14b is meshed with the gear 2 15a, and the gear 2 15a is fixed to At the left end of the intermediate shaft 15, the other side of the gear 2 15a is meshed with the gear 3 17c, and the gear 3 17c is fixed to the middle section of the main drive shaft 17; the left side of the gear 3 17c is equipped with a left idler gear 17b and a left clutch 17a for controlling the left idler gear 17b, and the right side of the gear 3 17c is equipped with a right idler gear 17d and a right clutch 17e for controlling the right idler gear 17d; the left idler gear 17b is meshed with the left half-shaft gear 18b, and the right idler gear 17d is meshed with the right half-shaft gear 19b.

[0049] An idler gear four 14d is installed on the right side of the two-way clutch 14c, and the idler gear four 14d is meshed with the idler gear five 15b. The idler gear five 15b is mounted on the right end of the intermediate shaft one 15, and the other side of the idler gear five 15b is meshed with the gear six 16a. The gear six 16a is fixed to the right end of the intermediate shaft two 16, and the gear seven 16b is fixed on the left end of the intermediate shaft two 16, and the gear seven 16b is meshed with the gear three 17c.

[0050] like Fig.12 As shown, in the forward gear, the left side of the two-way clutch 14c is engaged, so that the idler gear 1 14b is fixed on the secondary output shaft 14, and the secondary output shaft 14 drives the gear 2 15a to rotate through the idler gear 1 14b, and the gear 2 15a drives the gear 3 17c and the main drive shaft 17 to rotate in the positive direction. The gear 3 17c drives the intermediate shaft 2 16 and the gear 6 16a to rotate in suspension through the gear 7 16b, and the gear 6 16a drives the idler gear 5 15b to rotate in suspension on the intermediate shaft 15, and the idler gear 5 15b drives the idler gear 4 14d to rotate in suspension.

[0051] like Fig.13 As shown, when the reverse gear is in reverse gear, the right side of the two-way clutch 14c is engaged, so that the idler gear 4 14d is fixed on the secondary output shaft 14, and the secondary output shaft 14 drives the idler gear 5 15b to rotate on the intermediate shaft 15 through the idler gear 4 14d, and the idler gear 5 15b drives the intermediate shaft 2 16 to rotate through the gear 6 16a, and the intermediate shaft 2 16 drives the gear 3 17c to rotate in the opposite direction through the gear 7 16b, and the gear 3 17c drives the main drive shaft 17 to rotate in the opposite direction. At the same time, the gear 3 17c drives the gear 2 15a and the intermediate shaft 15 to rotate in suspension, and the gear 2 15a drives the idler gear 1 14b to rotate in suspension.

[0052] When moving forward, the left clutch 17a and the right clutch 17e are both engaged, the left idler gear 17b and the right idler gear 17d are both fixedly connected to the main drive shaft 17, the left idler gear 17b drives the left half-shaft 18 to rotate through the left half-shaft gear 18b, and the left half-shaft 18 drives the left wheel to rotate through the left wheel connecting flange 18a; the right idler gear 17d drives the right half-shaft 19 to rotate through the right half-shaft gear 19b, and the right half-shaft 19 drives the right wheel to rotate through the right wheel connecting flange 19a, so that the vehicle moves in a straight line.

[0053] When turning right, the left clutch 17a is engaged alone, the left idler gear 17b is fixedly connected to the main drive shaft 17, and the left idler gear 17b drives the left half-shaft 18 and the left wheel to rotate independently through the left half-shaft gear 18b; the right idler gear 17d is suspended on the main drive shaft 17, the right wheel remains stationary, and the vehicle turns right with an extremely small turning radius.

[0054] When turning left, the right clutch 17e is engaged alone, the right idler gear 17d is fixedly connected to the main drive shaft 17, and the right idler gear 17d drives the right half shaft 19 and the right wheel to rotate independently through the right half shaft gear 19b; the left idler gear 17b is suspended on the main drive shaft 17, the left wheel remains stationary, and the vehicle turns left with a very small turning radius. In this way, the vehicle can switch between turning left, walking, turning right, etc. at any time, and the turning radius of engineering vehicles such as tractors is greatly reduced, meeting the operation requirements of various working conditions.

[0055] The two-way clutch 14c is controlled by the forward and reverse gear shift fork 14c2, the driving shaft of the forward and reverse gear shift fork 14c2 is fixed at the center of the forward and reverse gear winch 14c1, and the shift rope 14c3 is wrapped in the outer rope groove of the forward and reverse gear winch 14c1. The forward and reverse gear winch 14c1 is driven by the shift rope 14c3 to rotate, and the forward and reverse gear winch 14c1 drives the forward and reverse gear shift fork 14c2 to swing to the left, and the two-way clutch 14c is switched to the forward gear; the forward and reverse gear shift fork 14c2 swings to the right, and the two-way clutch 14c is switched to the reverse gear.

[0056] The left clutch 17a is controlled by the left clutch arm 17a1, and the driving end of the left clutch arm 17a1 is controlled by the left steering rope 17a2; the left clutch 17a and the right clutch 17e are normally in a coupled state. When the left steering rope 17a2 is pulled, the left clutch arm 17a1 rotates to switch the left clutch 17a to a disengaged state, cutting off the power to the left wheel.

[0057] The right clutch 17e is controlled by the right clutch arm 17e1, and the driving end of the right clutch arm 17e1 is controlled by the right steering rope 17e2. When the right steering rope 17e2 is pulled, the right clutch arm 17e1 rotates to switch the right clutch 17e to the disengaged state, cutting off the power of the right wheel.

[0058] The above description is only a preferred embodiment of the present invention, and does not limit the scope of patent protection of the present invention. In addition to the above embodiments, the present invention may also have other implementations. Any technical solution formed by equivalent replacement or equivalent transformation falls within the protection scope required by the present invention. The technical features not described in the present invention can be realized by or using existing technologies, and will not be repeated here.

Claims

1. A coordinated speed change drive device, comprising a belt transmission mechanism and a planetary speed change mechanism, wherein the belt transmission mechanism comprises a driving pulley mounted on the left end of a primary input shaft, the driving pulley is connected to a driven pulley through a V-belt, and the driven pulley is mounted on the left end of a primary output shaft, characterized in that: The driving pulley comprises a left fixed disc and a right movable disc, the outer tenon of the left fixed disc extends to the right and is fixed to the left end of the primary input shaft, the central boss of the right movable disc is sleeved on the outer tenon of the left fixed disc, a plurality of right movable disc countersunk holes with right end openings are evenly distributed on the central boss of the right movable disc, a driving wheel compression spring is respectively arranged in each right movable disc countersunk hole, the right end of each driving wheel compression spring is commonly pressed against the left end face of the fork flange, and the fork flange is connected to the outer spline sleeve through an inner spline The external spline sleeve is fixed on the primary input shaft, the central boss of the shift fork flange extends to the right, the end face helical gear movable plate is installed on the central boss of the shift fork flange through its movable plate bearing, the right side of the end face helical gear movable plate forms a tooth-engaged engagement with the end face helical gear fixed plate, a clutch arm extending outward is provided on the circumference of the end face helical gear movable plate, the end face helical gear fixed plate is supported on the primary input shaft through its fixed plate bearing, and the right end face of the end face helical gear fixed plate is provided with a fixed plate circumferential limiting boss embedded in the groove of the box body; The outer tenon of the left fixed plate is correspondingly embedded in the inner slide groove of the central boss of the right movable plate, and the outer slide groove of the left fixed plate is formed between the adjacent outer tenons of the left fixed plate, and the inner tenon of the central boss of the right movable plate is correspondingly embedded in the corresponding outer slide groove of the left fixed plate; The planetary speed change mechanism comprises an outer gear planet carrier plate, a primary gear is installed in the middle section of the first-stage input shaft, the primary gear is meshed with the outer gear planet carrier plate, the center of the outer gear planet carrier plate is supported on the middle section of the second-stage input shaft through a bearing, a planet carrier is fixedly installed on the right end surface of the outer gear planet carrier plate, planetary shafts are symmetrically installed on the planet carrier, each planetary shaft is supported on the outer gear planet carrier plate through a bearing, a double-linked planetary gear is installed in the middle section of each planetary shaft, and each double-linked planetary gear comprises a double-linked large planetary gear and a double-linked small planetary gear arranged from left to right; the first-stage input shaft A primary output gear is installed at the right end of the output shaft, and the primary output gear is meshed with the secondary input large gear through a bridge gear. The secondary input large gear is fixed to the left end of the secondary input shaft, and a secondary input small sun gear is provided at the right end of the secondary input shaft, and the secondary input small sun gear is meshed with each of the double large planetary gears; a secondary output shaft is coaxially provided on the right side of the secondary input shaft, and the left end of the secondary output shaft is supported in the inner hole of the planetary carrier through a bearing and a secondary output large sun gear is fixed to the left end, and the secondary output large sun gear is meshed with each of the double small planetary gears.

2. The coordinated variable speed drive device according to claim 1, characterized in that: The helical teeth of the end face helical gear moving plate and the end face helical gear fixed plate cooperate with each other through steel balls, and the two sides of the steel balls are respectively embedded in the arc-shaped ball tracks of the corresponding tooth grooves.

3. The coordinated variable speed drive device according to claim 1, characterized in that: A retaining spring is embedded on the outer periphery of the right end of the external spline sleeve, and the retaining spring is located on the right side of the central boss of the fork flange.

4. The coordinated variable speed drive device according to claim 1, characterized in that: The right end of the inner ring of the fixed plate bearing abuts against the shoulder of the first-stage input shaft, the right end of the external spline sleeve abuts against the left side of the inner ring of the fixed plate bearing, the left end of the external spline sleeve is embedded in the inner step hole of the left fixed plate, and the left fixed plate fixing screw is screwed on the left end center of the first-stage input shaft and is pressed against the outer end center of the left fixed plate through a gasket.

5. The coordinated variable speed drive device according to claim 1, characterized in that: The driven pulley comprises a right fixed disc and a left movable disc, the center column of the right fixed disc extending to the left and being fixed to the left end of the output shaft, the outer periphery of the center column of the right fixed disc is provided with an outer spline of the right fixed disc, the left movable disc is sleeved on the outer spline of the right fixed disc through an inner spline, and the left port of the left movable disc is symmetrically provided with a left movable disc support ear extending toward the axial direction; a through right fixed disc center column through hole and a right fixed disc countersunk hole open at the right end are evenly provided in the center column of the right fixed disc, a driven wheel compression spring is respectively provided in each right fixed disc countersunk hole, a pressure plate is provided at the right end of each driven wheel compression spring, a spacer is respectively provided in the through hole of the center column of each right fixed disc, and each spacer is respectively supported between the pressure plate and the corresponding left movable disc support ear, and a plurality of long-rod screws are evenly inserted on the pressure plate from right to left, and each long-rod screw passes through the corresponding spacer and is screwed into the screw hole of the left movable disc support ear.

6. The coordinated variable speed drive device according to claim 1, characterized in that: A two-way clutch is installed in the middle section of the secondary output shaft through a spline, an idler gear 1 is installed on the left side of the two-way clutch, the idler gear 1 is meshed with gear 2, the gear 2 is fixed to the left end of the intermediate shaft 1, and the other side of the gear 2 is meshed with gear 3, and the gear 3 is fixed to the middle section of the main drive shaft; a left idler gear and a left clutch for controlling the left idler gear are installed on the left side of the gear 3, and a right idler gear and a right clutch for controlling the right idler gear are installed on the right side of the gear 3; the left idler gear is meshed with the left half-shaft gear, and the right idler gear is meshed with the right half-shaft gear; the left half-shaft gear is installed at the right end of the left half-shaft, and a left wheel connecting flange is installed at the left end of the left half-shaft; the right half-shaft gear is installed at the left end of the right half-shaft, and a right wheel connecting flange is installed at the right end of the right half-shaft.

7. The coordinated variable speed drive device according to claim 6, characterized in that: An idler gear four is installed on the right side of the two-way clutch, and the idler gear four is meshed with the idler gear five. The idler gear five is mounted on the right end of the intermediate shaft one, and the other side of the idler gear five is meshed with gear six. The gear six is ​​fixed to the right end of the intermediate shaft two, and a gear seven is fixed on the left end of the intermediate shaft two, and the gear seven is meshed with gear three.

8. The coordinated variable speed drive device according to claim 7, characterized in that: The two-way clutch is controlled by the forward and reverse gear fork, the driving shaft of the forward and reverse gear fork is fixed at the center of the forward and reverse gear winch, and the outer rope groove of the forward and reverse gear winch is wrapped with a shift rope; the left clutch is controlled by the left clutch arm, and the driving end of the left clutch arm is controlled by the left steering rope; the right clutch is controlled by the right clutch arm, and the driving end of the right clutch arm is controlled by the right steering rope.

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