CN212297483U - Coordinated variable speed drive - Google Patents

Abstract

The utility model relates to a coordinated variable speed driving device, a driving belt pulley is connected with a driven belt pulley on an output shaft through a V-shaped belt, the driving belt pulley comprises a left fixed disc and a right movable disc, the outer tenon of the left fixed disc is fixed on a first-level input shaft, the right movable disc is sleeved on the outer tenon of the left fixed disc, a driving wheel pressure spring is respectively arranged in a counter bore of the right movable disc, the right end of each driving wheel pressure spring is commonly propped against the left end surface of a shifting fork flange which is connected on an outer spline sleeve through an inner spline, the outer spline sleeve is fixed on the first-level input shaft, an end face skewed tooth movable disc is arranged on a central boss at the right end of the shifting fork flange through a movable disc bearing, the right side of the end face skewed tooth movable disc and the end face skewed tooth fixed disc form tooth type meshing, a clutch pull arm is arranged on the circumference of the end face skewed tooth movable disc, the right end face of the end face helical tooth fixed disc is provided with a circumferential limit boss embedded in the box body. The mechanism can carry out online speed regulation and has stable transmission.

Description

Coordinated variable speed drive

Technical Field

The utility model relates to a coordinate variable speed drive arrangement belongs to derailleur technical field.

Background

The belt pulley transmission and the planetary speed change mechanism are frequently used in the vehicle transmission, the belt pulley transmission is a common transmission mode, the belt pulley transmission device is often required to regulate speed according to different operation objects and complex and changeable operation environments, and the most common mode of belt pulley speed regulation is to change the diameter ratio of a main wheel disc and a driven wheel disc.

The traditional planetary gear comprises an inner gear ring, a sun gear and a planetary gear, wherein the planetary gear is engaged between the sun gear and the inner gear ring, and a planetary gear shaft is fixed on a planetary support. The power is input in various modes, such as locking of the planet carrier, and the power is input from the sun gear and output from the inner gear ring; the planet carrier is locked, and power is input from the inner gear ring and output from the sun gear; the inner gear ring is locked, and power is input from the sun gear and output from the planet carrier; the inner gear ring is locked, and power is input from the planet support and output from the sun gear; the sun gear is locked, and power is input from the planet support and output from the inner gear ring; the sun gear is locked, power is input from the inner gear ring, and power is output from the planet carrier. When the common planetary gear mechanism is applied to special vehicles such as tractors and the like, a lot of difficulties are often encountered, and special application scenes are difficult to meet. For example, the speed of the vehicle can only be adjusted by engaging several gears, the output power is insufficient when the speed of the engine is reduced, the inner gear ring is too large and difficult to arrange, or the planet wheel, the sun wheel and the inner gear ring cannot be arranged in the same plane, and the like, which affects the use of the planetary speed change mechanism on special vehicles.

As the vehicle turns, the wheels rotate at different speeds. The distance covered by each wheel is different, and the distance covered by the inner wheel is shorter than that covered by the outer wheel. The gearbox of the traditional vehicle simultaneously drives two wheels through a differential mechanism, and the differential mechanism outputs two different rotating speeds when the vehicle turns, so that the left wheel and the right wheel roll at different rotating speeds, and the wheels are driven by two sides to do pure rolling motion.

With conventional differential steering, a large turning radius is required although the inner wheels rotate at a lower speed than the outer wheels and travel a shorter distance. The operation environment of tractor need can sharp turn in the region that is close to the ridge, especially in the bight in field especially so, otherwise the bight in field and the region that is close to the ridge can leave great not farming region, need the manual work to remedy, greatly reduced farming efficiency, improve artificial work load, be unfavorable for the popularization of modernized automatic farming. In addition, barriers such as a derrick and a telegraph pole are often found in the field, and the barriers need to be tightly attached to and detour during cultivation or harvesting, so that the barriers are dead zones of operation of a traditional tractor.

In addition, when the tractor works, the forward or reverse often needs to be switched, so that the traditional gearbox drive axle cannot meet the multi-operating condition requirement.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to overcome the problem that exists among the prior art, provide a coordinate variable speed drive, can carry out online speed governing to belt drive mechanism without the take-up pulley, and the speed governing scope is wide, and the belt can not relax, and transmission power is stable.

In order to solve the technical problems, the utility model discloses a coordinated variable speed driving device, which comprises a belt transmission mechanism and a planetary variable speed mechanism, wherein the belt transmission mechanism comprises a driving belt pulley arranged at the left end of a primary input shaft, the driving belt pulley is in transmission connection with a driven belt pulley through a V-shaped belt, the driven belt pulley is arranged at the left end of a primary output shaft, the driving belt pulley comprises a left fixed disc and a right movable disc, an outer tenon of the left fixed disc extends rightwards and is fixed at the left end of the primary input shaft, a central boss of the right movable disc is sleeved on the outer tenon of the left fixed disc, a plurality of right movable disc counter bores with right end openings are uniformly distributed on the central boss of the right movable disc, a driving wheel pressure spring is respectively arranged in each right movable disc counter bore, the right end of each driving wheel pressure spring is commonly supported on the left end surface of a shifting fork, the external spline housing is fixed on the one-level input shaft, the center boss of shift fork flange stretches out to the right, the terminal surface skewed tooth driving disk is installed on shift fork flange center boss through its driving disk bearing, the right side of terminal surface skewed tooth driving disk forms the jaw formula meshing with terminal surface skewed tooth fixed disk, be equipped with the separation and reunion arm-drag that outwards stretches out on the circumference of terminal surface skewed tooth driving disk, the terminal surface skewed tooth fixed disk supports on the one-level input shaft through its fixed disk bearing, the right-hand member face of terminal surface skewed tooth fixed disk is equipped with the spacing boss of fixed disk circumference that inlays in the box recess.

Compared with the prior art, the utility model discloses following beneficial effect has been obtained: the first-level input shaft drives the left fixed disc and the right movable disc to rotate, two side walls of the V-shaped belt are clamped between the left fixed disc and the right movable disc to rotate along with the left fixed disc, the shifting fork flange and the driving belt pulley rotate synchronously, and the V-shaped belt drives the driven belt pulley to rotate. The right movable disc can only move horizontally on the tenon outside the left fixed disc, so that the right movable disc and the left fixed disc can not rotate relatively. The right end of the end face helical tooth fixed disc is fixed on the box body through the fixed disc circumference limiting boss, when the clutch pull arm rotates the end face helical tooth movable disc in the forward direction, the end face helical tooth fixed disc is pushed out leftwards by the meshing face of the end face helical tooth fixed disc, the end face helical tooth movable disc pushes out the shifting fork flange leftwards, the shifting fork flange slides leftwards on the external spline sleeve to push out the right movable disc plate leftwards, the distance between the right movable disc plate and the left fixed disc plate is reduced, the V-shaped belt is pushed out towards the periphery, and the driving belt pulley is in a large-diameter working state. When the clutch pull arm rotates the end face helical tooth moving disc reversely, the end face helical tooth moving disc moves rightwards, the right moving disc and the shifting fork flange move rightwards, the distance between the right moving disc and the left fixed disc is increased, the V-shaped belt moves towards the inner periphery of the driving belt pulley due to the tension of the V-shaped belt, and the driving belt pulley is in a small-diameter working state. The tension of the pressure spring of the driving wheel enables the shifting fork flange and the end face helical tooth moving disc to be always kept in good axial close contact, after the end face helical tooth moving disc moves rightwards, the right moving disc and the left fixed disc keep pressure contact on two sides of the V-shaped belt, and the V-shaped belt cannot slip when the V-shaped belt is restarted.

As a further improvement, the evagination tenon correspondence of the left side fixed disk piece is inlayed in the inner chute of the central boss of the right side movable disk piece, forms the outer chute of the left side fixed disk piece between the outer tenon of the adjacent left side fixed disk piece, and the inner tenon correspondence of the central boss of the right side movable disk piece is inlayed in the outer chute of the corresponding left side fixed disk piece. The outer tenon of the left fixed disc is embedded in the inner chute of the right movable disc, and the inner tenon of the right movable disc is embedded in the outer chute of the left fixed disc, so that the right movable disc and the left fixed disc form radial positioning but can axially slide, the distance between the right movable disc and the left fixed disc can be adjusted, and the right movable disc can be prevented from slipping relative to the left fixed disc.

As a further improvement, the snap spring is embedded in the outer spline housing's right-hand member periphery, the snap spring is located the right side of shift fork flange center boss. The clamp spring limits the right stroke of the shifting fork flange, and indirectly limits the maximum distance between the right movable disc and the left fixed disc.

As the utility model discloses a further improvement, the inner circle right-hand member of fixed disk bearing supports and leans on the shaft shoulder of one-level input shaft, the right-hand member of outer spline housing supports and leans on the inner circle left side of fixed disk bearing, the left end of outer spline housing inlays in the inner step hole of left side fixed disk, and left side fixed disk set screw connects at the left end center of one-level input shaft and compresses tightly the outer end center at left side fixed disk through the gasket soon. The left fixed disk piece fixing screw compresses the left fixed disk piece, the outer spline sleeve and the inner ring of the movable disk bearing through the gasket, so that the left fixed disk piece, the outer spline sleeve and the inner ring of the movable disk bearing are axially positioned on the primary input shaft; the left fixed disk and the outer spline sleeve are respectively positioned in the radial direction through a flat key and the primary input shaft; the left end of the outer spline sleeve is embedded in the inner step hole of the left fixed disk, so that the outer spline sleeve and the inner step hole can realize axial positioning and circumferential positioning.

As a further improvement of the utility model, the driven belt pulley comprises a right fixed disc and a left movable disc, a central column of the right fixed disc extends leftwards and is fixed at the left end of the output shaft, a right fixed disc external spline is arranged on the periphery of the central column of the right fixed disc, a left movable disc is sleeved on the right fixed disc external spline through an internal spline, and a left port of the left movable disc is symmetrically provided with a left movable disc support lug extending towards the axial direction; the right fixed disc central column is evenly provided with a through right fixed disc central column through hole and a right fixed disc counter bore with an open right end, each right fixed disc counter bore is respectively provided with a driven wheel pressure spring, each right end of the driven wheel pressure spring is provided with a pressure plate, each right fixed disc central column through hole is respectively provided with a spacer bush, each spacer bush is respectively supported between the pressure plate and a corresponding left movable disc support lug, a plurality of long rod screws are evenly inserted into the pressure plate from right to left, and each long rod screw respectively passes through the corresponding spacer bush and is screwed into a screw hole of the left movable disc support lug. The right fixed disc piece fixing screw fixes the right fixed disc piece on the left end shaft shoulder of the output shaft through the gasket, the spacer bush realizes the axial positioning between the pressing plate and the left movable disc piece support lug, and a passing space is provided for the long rod screw, so that the left movable disc pieces positioned on the two sides of the right fixed disc piece and the pressing plate form a rigid whole. The left movable disc is in a floating state, the inner spline of the left movable disc is sleeved on the outer spline of the right fixed disc in an axially sliding mode, the pressing plate is pushed out rightwards by tension of each driven wheel pressure spring, and the pressing plate pushes the left movable disc rightwards through the long rod screw and the left movable disc support lug so as to clamp the V-shaped belt. Because the center distance between the driving belt pulley and the driven belt pulley is unchanged, when the driving belt pulley is switched to a large-diameter working state, the driven belt pulley is automatically switched to a small-diameter working state under the extrusion of the V-shaped belt; on the contrary, when the driving belt pulley is switched to the small-diameter working state, the pressure of the V-shaped belt on the disk of the driven belt pulley is reduced, the left moving disk moves to the right under the tension of the pressure spring of the driven wheel, and the driven belt pulley is automatically switched to the large-diameter working state. Therefore, the ratio of the diameters of the driving belt wheel and the driven belt wheel can be adjusted on line by rotating the end face helical gear driving disc through the clutch pull arm, so that the online change of the transmission ratio between the first-stage input shaft and the output shaft is realized, the transmission of the V-shaped belt is reliable in the speed regulation process, and the phenomenon of slipping of the belt can not occur when the belt is restarted.

As a further improvement of the present invention, the planetary transmission mechanism includes an external-tooth planet carrier disc, a primary gear is installed in the middle section of the first-stage input shaft, the primary gear is engaged with the external-tooth planet carrier disc, the center of the external-tooth planet carrier disc is supported in the middle section of the second-stage input shaft through a bearing, a planet carrier is fixedly installed on the right end face of the external-tooth planet carrier disc, planet shafts are symmetrically installed on the planet carrier, the planet shafts are supported on the external-tooth planet carrier disc through bearings respectively, duplicate planet gears are installed in the middle sections of the planet shafts respectively, and each duplicate planet gear includes a duplicate large planet gear and a duplicate small planet gear which are arranged from left to right respectively; a primary output gear is mounted at the right end of the primary output shaft and meshed with a secondary input large gear through a carrier gear, the secondary input large gear is fixed at the left end of the secondary input shaft, a secondary input small sun gear is arranged at the right end of the secondary input shaft and meshed with the duplex large planetary gears; the right side of the secondary input shaft is coaxially provided with a secondary output shaft, the left end of the secondary output shaft is supported in an inner hole of the planet carrier through a bearing, a secondary output large sun gear is fixed at the left end, and the secondary output large sun gear is meshed with each duplex small planetary gear. The primary gear on the primary input shaft drives the external gear planet carrier disc to rotate and realize primary speed reduction, the external gear planet carrier disc drives the planet carrier and the three planet shafts to synchronously revolve, and the revolution ratio of the external gear planet carrier disc to the rotation speed of the primary input shaft is unchanged and the direction is opposite; the bearing enables the second-stage input shaft and the external gear planet carrier disc to rotate relatively, the first-stage output gear at the right end of the first-stage output shaft drives the second-stage input large gear to rotate through the intermediate gear, the second-stage input large gear drives the second-stage input shaft to rotate, the second-stage input shaft drives the duplex large planet gear to rotate through the second-stage input small sun gear, the revolution direction of the planet shaft is opposite to the rotation direction of the second-stage input small sun gear, the revolution direction of the duplex large planet gear and the rotation direction of the second-stage input small sun gear jointly determine the rotation speed of the duplex large planet gear, the bearing enables the second-stage output shaft and the planet carrier to rotate relatively, and the duplex. When the rotating speed of the secondary input small sun gear is equal to the revolution speed of the external tooth planet carrier disc, the rotating speed of each duplex planet gear is zero, so that the change of the secondary output shaft from zero rotating speed to the highest rotating speed can be realized by changing the rotating speed of the secondary input small sun gear under the condition that the speed of the primary input shaft is not changed, and the stepless speed change is realized. And the primary input shaft and the secondary input shaft drive the secondary output shaft to rotate together, so that the output power is improved, and the speed regulation is more convenient under the condition of keeping high-power output.

As a further improvement of the present invention, a two-way clutch is mounted on the middle section of the secondary output shaft through a spline, a first idler gear is mounted on the left side of the two-way clutch, the first idler gear is meshed with a second gear, the second gear is fixed on the left end of the first intermediate shaft, the other side of the second gear is meshed with a third gear, and the third gear is fixed on the middle section of the main drive shaft; a left idler gear and a left clutch for controlling the left idler gear are arranged on the left side of the gear III, and a right idler gear and a right clutch for controlling the right idler gear are arranged on the right side of the gear III; the left idler gear is meshed with the left half axle gear, and the right idler gear is meshed with the right half axle gear; the left half axle gear is arranged at the right end of the left half axle, and the left end of the left half axle is provided with a left wheel connecting flange; 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 the gear is shifted forward, the left sides of the two-way clutches are combined, the first idler gear is fixed on the second-stage output shaft, the second-stage output shaft rotates through the first idler gear driving gear II, and the second gear driving gear III and the main driving shaft rotate in the positive direction. When the left clutch and the right clutch are combined, the left idler gear and the right idler gear are both fixedly connected with the main driving shaft, 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, the right half shaft drives the right wheel to rotate through the right wheel connecting flange, and the vehicle travels linearly. When the left clutch is combined independently, the left idler gear is fixedly connected with the main driving shaft, and the left idler gear drives the left half shaft and the left wheel to rotate independently through the left half shaft gear; the right idler gear is suspended on the main driving shaft, the right wheel is kept still, the vehicle turns right, and the turning radius is extremely small. When the right clutch is combined independently, the right idler gear is fixedly connected with the main driving 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 driving shaft, the left wheel is kept still, the vehicle turns left, and the turning radius is extremely small. So can switch left turn, walking, right turn etc. at any time, and reduced engineering vehicle's such as tractor turning radius greatly, satisfy the operation demand of various operating modes.

As a further improvement, free gear four is installed on two-way clutch's right side, and free gear four meshes with free gear five mutually, free gear five suit in the right-hand member of jackshaft one, free gear five's opposite side meshes with the gear six mutually, the gear six is fixed in the right-hand member of jackshaft two, the left end fixed mounting of jackshaft two has gear seven, gear seven meshes with the gear three-phase. When the two-way clutch is in reverse gear, the right side of the two-way clutch is combined, the second-stage output shaft is fixed on the second-stage output shaft, the second-stage output shaft drives the second idle gear to rotate in a suspended mode on the first intermediate shaft through the fourth idle gear, the fifth idle gear drives the second intermediate shaft to rotate through the sixth gear, the second intermediate shaft drives the third gear to rotate in the reverse direction through the seventh gear, and the third gear drives the main driving shaft to rotate in the reverse direction. Meanwhile, the gear three drives the gear two and the intermediate shaft one to rotate in a suspension mode, and the gear two drives the idler gear one to rotate in a suspension mode. When the gear is shifted forward, the third gear drives the second intermediate shaft and the sixth gear to rotate in a suspended mode through the seventh gear, the sixth gear drives the fifth idler gear to rotate in a suspended mode on the first intermediate shaft, and the fifth idler gear drives the fourth idler gear to rotate in a suspended mode.

As a further improvement of the present invention, the bidirectional clutch is controlled by a forward and reverse shift fork, a driving shaft of the forward and reverse shift fork is fixed at the center of the forward and reverse capstan, and a shift rope is wound around an outer peripheral rope groove of the forward and reverse capstan; the left clutch is controlled by a left clutch pull arm, and the driving end of the left clutch pull arm is controlled by a left steering pull rope; the right clutch is controlled by a right clutch pull arm, and the driving end of the right clutch pull arm is controlled by a right steering pull rope. The gear shifting pull rope drives the forward and reverse gear winch to rotate, the forward and reverse gear winch drives the forward and reverse gear shifting fork to swing leftwards, and the bidirectional clutch is switched to a forward gear; when the forward and reverse shift fork swings to the right, the bidirectional clutch is switched to the reverse gear. The left clutch and the right clutch are normally in a combined state, and when the left steering pull rope is pulled, the left clutch pull arm rotates to enable the left clutch to be switched to a separated state, so that the power of a left wheel is cut off. When the right steering pull rope is pulled, the right clutch pull arm rotates to enable the right clutch to be switched to a separated state, and power of the right wheel is cut off.

Drawings

Fig. 1 is a front view of the coordinated variable speed drive device of the present invention.

Fig. 2 is the schematic structural diagram of the utility model with the box body removed.

Fig. 3 is a perspective view of the coordinated variable speed drive device of the present invention.

Fig. 4 is a perspective view of the present invention with the box and the housing removed.

Fig. 5 is a front view of the middle belt transmission mechanism of the present invention.

Fig. 6 is a perspective view of fig. 5.

Fig. 7 is an exploded view of fig. 6.

Fig. 8 is a front view of the planetary transmission mechanism of the present invention.

Fig. 9 is a perspective view of fig. 8.

Fig. 10 is an exploded view of fig. 9.

Fig. 11 is a perspective view of the forward and reverse rotation driving mechanism of the present invention.

Fig. 12 is a gear transmission diagram of the present invention when it goes forward.

Fig. 13 is a gear transmission diagram of the present invention when it is reversed.

In the figure: 1. a primary input shaft; 1a, a primary gear; 2a, a left fixed disc; 2a1. left fixed disk outer tenon; 2a2. a left fixed disc outer chute; 2a3. left fixed disk slice fixing screw; 2b, a right movable disc; 2b1, forming a right dynamic disc counter bore; 2b2. driving wheel compression spring; 3. an internal spline fork flange; 3a, shifting fork flange center boss; 4. an outer spline housing; 4a, a clamp spring; 5. an end face helical gear moving disc; 5a, a clutch pull arm; 5b, moving disc bearings; 6. a steel ball; 7. fixing the end face helical teeth; 7a, a fixed disc circumference limiting boss; 7b, a fixed disc bearing; 8a, right fixed disk; 8a1. right fixed disk outer spline; 8a2. right fixed disc counter bore; 8a3. driven wheel compression spring; 8a4. spacer sleeve; 8a5. right fixed disk fixing screw; 8b, moving the disc leftwards; 8b1, forming a spline in the left movable disc; 8b2. left movable disc support lug; 9. pressing a plate; a long rod screw; a V-shaped belt; 11. a primary output shaft; 11a, a primary output gear; 11b. a carrier gear; 12. an outer toothed planet carrier disc; 12a. a planet carrier; 12b. a planet axle; 12c. a duplex planetary gear; 12c1. a duplex big planetary gear; 12c2. double-linked pinion; 13. a secondary input shaft; 13a, a secondary input gearwheel; 13b, a secondary input small sun gear; 14. a secondary output shaft; 14a, a secondary output large sun gear; 14b, an idler gear I; 14c. a bi-directional clutch; 14c1. forward reverse capstan; 14c2. forward reverse shift forks; 14c3. shift cable; 14d, an idler gear four; 15. a first intermediate shaft; 15a, a second gear; 15b, an idler gear five; 16. a second intermediate shaft; gear six; 16b. gear seven; 17. a main drive shaft; a left clutch; 17a1. left clutch pull arm; 17a2. left steering pull cord; 17b, a left idler gear; gear three; 17d, right idler gear; 17e, a right clutch; 17e1. right clutch pull arm; 17e2. right steering pull cord; 18. a left half shaft; a left wheel attachment flange; 18b. a left side gear; 19. a right half shaft; a right wheel attachment flange; right half shaft gear 19b.

Detailed Description

In the following description of the present invention, the terms "left", "right", "inside", "outside", and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, only for convenience of description and simplification of description, and do not mean that the device must have a specific orientation.

As shown in fig. 1 to 7, the coordinated variable speed drive device of the present invention includes a belt transmission mechanism, a planetary transmission mechanism and a transmission drive axle. The primary input shaft 1 is supported on the box body through a bearing, the belt transmission mechanism comprises a driving belt pulley arranged at the left end of the primary input shaft 1, the driving belt pulley is in transmission connection with a driven belt pulley through a V-shaped belt 10, the driven belt pulley is arranged at the left end of an output shaft 11, the driving belt pulley comprises a left fixed disc 2a and a right movable disc 2b, an outer convex tenon of the left fixed disc 2a extends rightwards and is fixed at the left end head of the primary input shaft 1, a central boss of the right movable disc 2b is sleeved on the outer convex tenon 2a1 of the left fixed disc, a plurality of right movable disc counter bores 2b1 with openings at right ends are uniformly distributed on the central boss of the right movable disc, a driving wheel pressure spring 2b2 is respectively arranged in each right movable disc counter bore 2b1, the right end of each driving wheel pressure spring 2b2 jointly abuts against the left end face of a shifting fork flange 3, the shifting fork flange 3 is sleeved on an outer spline sleeve, the central boss of shift fork flange 3 stretches out right, the terminal surface skewed tooth driving disk 5 is installed on shift fork flange center boss 3a through its driving disk bearing 5b, the right side of terminal surface skewed tooth driving disk 5 forms the tooth embedded meshing with terminal surface skewed tooth fixed disk 7, be equipped with the separation and reunion arm-drag 5a of outwards stretching out on the circumference of terminal surface skewed tooth driving disk 5, terminal surface skewed tooth fixed disk 7 supports on one-level input shaft 1 through its fixed disk bearing 7b, the right-hand member face of terminal surface skewed tooth fixed disk 7 is equipped with the spacing boss 7a of fixed disk circumference of inlaying in the box recess.

First-level input shaft 1 drive left fixed plate piece 2a and right movable plate piece 2b rotate, and the both sides wall of V-arrangement area 10 is followed the rotation by the centre gripping between left fixed plate piece 2a and right movable plate piece 2b, and shift fork flange 3 and drive pulley synchronous revolution, V-arrangement area 10 drive driven pulley rotate. The right movable disc 2b can only translate on the left fixed disc outer tenon 2a1, so that the right movable disc 2b and the left fixed disc 2a can not rotate relatively. The right end of the end face helical tooth fixed disc 7 is fixed on the box body through a fixed disc circumference limiting boss 7a.

When the clutch pull arm 5a rotates the end face helical tooth movable disk 5 in the forward direction, the end face helical tooth fixed disk 7 pushes the meshing face of the end face helical tooth fixed disk leftward, the end face helical tooth movable disk 5 pushes the shifting fork flange 3 leftward, the shifting fork flange 3 slides leftward on the external spline housing 4 to push the right movable disk plate 2b leftward, so that the distance between the right movable disk plate 2b and the left fixed disk plate 2a is reduced, the V-shaped belt 10 is pushed out to the outer periphery, and the driving belt pulley is in a large-diameter working state.

When the clutch pull arm 5a rotates the end face helical gear moving disk 5 reversely, the end face helical gear moving disk 5 moves rightwards, the right moving disk 2b and the shifting fork flange 3 move rightwards, so that the distance between the right moving disk 2b and the left fixed disk 2a is increased, the V-shaped belt 10 moves towards the inner periphery of the driving belt pulley by the tension of the V-shaped belt 10, and the driving belt pulley is in a small-diameter working state. The tension of the driving wheel pressure spring 2b2 keeps the shifting fork flange 3 and the end face helical gear disc 5 in good axial close contact all the time, after the end face helical gear disc 5 moves rightwards, the right moving disc 2b and the left fixed disc 2a keep pressure contact on two sides of the V-shaped belt 10, and the V-shaped belt 10 cannot slip when being restarted.

The oblique teeth of the end face oblique tooth moving disc 5 and the end face oblique tooth fixed disc 7 are matched with each other through steel balls 6, and two sides of each steel ball 6 are embedded in the arc ball paths of the corresponding tooth grooves respectively. The oblique tooth direct contact of terminal surface skewed tooth driving disk 5 and terminal surface skewed tooth fixed disk 7 changes into through the contact of steel ball 6, has reduced the frictional force when terminal surface skewed tooth driving disk 5 and terminal surface skewed tooth fixed disk 7 separation, has prolonged life, and makes the rotation of terminal surface skewed tooth driving disk 5 more smooth and easy.

The left fixed disc outer tenon 2a1 is correspondingly embedded in the inner sliding groove of the right movable disc center boss, a left fixed disc outer sliding groove 2a2 is formed between the adjacent left fixed disc outer tenons 2a1, and the inner tenon of the right movable disc center boss is correspondingly embedded in the corresponding left fixed disc outer sliding groove 2a2. The left fixed disk outer tenon 2a1 is embedded in the right fixed disk inner sliding groove, and the right movable disk inner tenon is embedded in the left fixed disk outer sliding groove 2a2, so that the right movable disk 2b and the left fixed disk 2a form radial positioning but can axially slide, the distance between the right movable disk 2b and the left fixed disk 2a can be adjusted, and the right movable disk 2b can be prevented from slipping relative to the left fixed disk 2a.

And a clamp spring 4a is embedded in the periphery of the right end of the outer spline sleeve 4, and the clamp spring 4a is positioned on the right side of the central boss 3a of the shifting fork flange. The clamp spring 4a limits the right stroke of the shifting fork flange 3, and indirectly limits the maximum distance between the right movable disk piece 2b and the left fixed disk piece 2a.

The right end of the inner ring of the fixed disc bearing 7b abuts against the shaft shoulder of the first-level input shaft 1, the right end of the outer spline sleeve 4 abuts against the left side of the inner ring of the fixed disc bearing 7b, the left end of the outer spline sleeve 4 is embedded in the inner step hole of the left fixed disc 2a, and the left fixed disc fixing screw 2a3 is screwed in the center of the left end of the first-level input shaft 1 and is tightly pressed at the center of the outer end of the left fixed disc 2a through a gasket. The left fixed disk piece fixing screw 2a3 compresses the left fixed disk piece 2a, the outer spline sleeve 4 and the inner ring of the fixed disk bearing 7b through a gasket, so that the three are axially positioned on the primary input shaft 1; the left fixed disc piece 2a and the outer spline sleeve 4 are respectively positioned in the radial direction with the first-stage input shaft 1 through a flat key; the left end of the outer spline housing 4 is embedded in the inner step hole of the left fixed disk 2a, so that the two realize axial positioning and circumferential positioning.

The driven belt pulley comprises a right fixed disc 8a and a left movable disc 8b, a center column of the right fixed disc 8a extends leftwards and is fixed at the left end of the output shaft 11, a right fixed disc external spline 8a1 is arranged on the periphery of the center column of the right fixed disc, the left movable disc 8b is sleeved on a right fixed disc external spline 8a1 through a left movable disc internal spline 8b1, and a left port of the left movable disc 8b is symmetrically provided with a left movable disc support lug 8b2 extending towards the axial direction; a through right fixed disc central column through hole and a right fixed disc counter bore 8a2 with an opening at the right end are uniformly arranged in the right fixed disc central column, a driven wheel pressure spring 8a3 is respectively arranged in each right fixed disc counter bore 8a2, a pressure plate 9 is arranged at the right end of each driven wheel pressure spring 8a3, a spacer 8a4 is respectively arranged in each right fixed disc central column through hole, each spacer 8a4 is respectively supported between the pressure plate 9 and a corresponding left movable disc lug 8b2, a plurality of long rod screws 9a are uniformly inserted into the pressure plate 9 from right to left, and each long rod screw 9a respectively penetrates through a corresponding spacer 8a4 and is screwed into a screw hole of the left movable disc lug 8b2.

The right fixed disk piece fixing screw 8a5 fixes the right fixed disk piece 8a on the left end shaft shoulder of the output shaft 11 through a gasket, the spacer 8a4 realizes the axial positioning between the pressing plate 9 and the left movable disk piece support lug 8b2, and provides a passing space for the long rod screw 9a, so that the left movable disk pieces 8b positioned at the two sides of the right fixed disk piece 8a and the pressing plate 9 form a rigid whole. The left movable disk 8b is in a floating state, the left movable disk internal spline 8b1 is sleeved on the right fixed disk external spline 8a1 and can axially slide, the pressure plate 9 is pushed out rightwards by the tension of each driven wheel pressure spring 8a3, and the pressure plate 9 pushes the left movable disk 8b rightwards through the long rod screw 9a and the left movable disk support lug 8b2 so as to clamp the V-shaped belt 10.

Because the center distance between the driving belt pulley and the driven belt pulley is unchanged, when the driving belt pulley is switched to a large-diameter working state, the driven belt pulley is automatically switched to a small-diameter working state under the extrusion of the V-shaped belt 10; on the contrary, when the driving pulley is switched to the small-diameter working state, the pressure of the V-shaped belt 10 on the disk of the driven pulley is reduced, the left moving disk 8b moves to the right under the tension of the driven wheel pressure spring 8a3, and the driven pulley is automatically switched to the large-diameter working state. Therefore, the ratio of the diameters of the driving belt wheel and the driven belt wheel can be adjusted on line by rotating the end face helical gear moving disc 5 through the clutch pull arm 5a, so that the online change of the transmission ratio between the first-stage input shaft 1 and the output shaft 11 is realized, the transmission of the V-shaped belt 10 is reliable in the speed regulation process, and the phenomenon of slipping can not occur when the belt is restarted.

Fig. 8 to 10 show a planetary transmission mechanism, wherein a primary gear 1a is mounted on a middle section of a primary input shaft 1, the primary gear 1a is engaged with an external-tooth planet carrier disc 12, the center of the external-tooth planet carrier disc 12 is supported on a middle section of a secondary input shaft 13 through a bearing, a secondary input gearwheel 13a is mounted on a left end of the secondary input shaft 13, and bearings are respectively mounted on left and right sides of the secondary input gearwheel 13a and supported in a wall of a box body through the bearings. A planet carrier 12a is fixedly mounted on the right end face of the external gear planet carrier disc 12, planet shafts 12b are symmetrically mounted on the planet carrier 12a, the planet shafts 12b are supported on the external gear planet carrier disc 12 through bearings respectively, duplex planet gears 12c are mounted at the middle section of each planet shaft 12b respectively, and each duplex planet gear 12c comprises a duplex big planet gear 12c1 and a duplex small planet gear 12c2 which are arranged from left to right respectively.

A primary output gear 11a is mounted at the right end of the primary output shaft 11, the primary output gear 11a is meshed with a secondary input large gear 13a through a carrier gear 11b, the secondary input large gear 13a is fixed at the left end of a secondary input shaft 13, a secondary input small sun gear 13b is arranged at the right end of the secondary input shaft 13, and the secondary input small sun gear 13b is meshed with the duplex large planetary gears 12c 1; a secondary output shaft 14 is coaxially arranged on the right side of the secondary input shaft 13, the middle section of the secondary output shaft 14 is supported in the wall of the box body through a bearing, the left end of the secondary output shaft 14 is supported in an inner hole of the planet carrier 12a through a bearing, a secondary output large sun gear 14a is fixed at the left end, and the secondary output large sun gear 14a is meshed with the duplex small planet gears 12c2.

A primary gear 1a on the primary input shaft 1 drives an external gear planet carrier disc 12 to rotate and realize primary speed reduction, the external gear planet carrier disc 12 drives a planet carrier 12a and three planet shafts 12b to synchronously revolve, and the ratio of the revolution of the external gear planet carrier disc 12 to the rotation speed of the primary input shaft 1 is unchanged and the direction is opposite; the bearing enables the secondary input shaft 13 and the externally toothed planet carrier disc 12 to rotate relatively, 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 intermediate gear 11b, the secondary input large gear 13a drives the secondary input shaft 13 to rotate, the secondary input shaft 13 drives the duplex large planet gear 12c1 to rotate through the secondary input small sun gear 13b, the revolution direction of the planet shaft 12b is opposite to the rotation direction of the secondary input small sun gear 13b, the revolution speed of the planet shaft 12b and the rotation speed of the secondary input small sun gear 13b jointly determine the rotation speed of the duplex large planet gear 12c1, the bearing enables the secondary output shaft 14 and the planet carrier 12a to rotate relatively, and the duplex small planet gear 12c2 synchronously drives the secondary output large sun gear 14a to rotate and further speed reduction of the secondary output shaft 14 is achieved. When the rotation speed of the secondary input small sun gear 13b is equal to the revolution speed of the externally toothed planet carrier disc 12, the rotation speed of each duplex planet gear 12c is zero, so that the change of the secondary output shaft 14 from zero rotation speed to the highest rotation speed can be realized by changing the rotation speed of the secondary input small sun gear 13b under the condition that the speed of the primary input shaft 1 is not changed, and the stepless speed change is realized. And the primary input shaft 1 and the secondary input shaft 13 drive the secondary output shaft 14 to rotate together, so that the output power is improved, and the speed regulation is more convenient under the condition of keeping high-power output.

As shown in fig. 1 to 4 and 11, a left wheel connecting flange 18a in a transmission drive axle is mounted at the left end of a left half shaft 18, and a left side gear 18b is mounted at the right end of the left half shaft 18; a right wheel connecting flange 19a is arranged at the right end of the right half shaft 19, and a right half shaft gear 19b is arranged at the left end of the right half shaft 19; a bidirectional clutch 14c is mounted in the middle section of the secondary output shaft 14 through a spline, a first idler gear 14b is mounted on the left side of the bidirectional clutch 14c, the first idler gear 14b is meshed with a second gear 15a, the second gear 15a is fixed to the left end of the first intermediate shaft 15, the other side of the second gear 15a is meshed with a third gear 17c, and the third gear 17c is fixed to the middle section of the main driving shaft 17; a left idler gear 17b and a left clutch 17a for controlling the left idler gear 17b are arranged on the left side of the gear III 17c, and a right idler gear 17d and a right clutch 17e for controlling the right idler gear 17d are arranged on the right side of the gear III 17 c; the left idler gear 17b is meshed with the left side gear 18b, and the right idler gear 17d is meshed with the right side gear 19b.

The right side of the bidirectional clutch 14c is provided with a fourth idle gear 14d, the fourth idle gear 14d is meshed with a fifth idle gear 15b, the fifth idle gear 15b is sleeved at the right end of the first intermediate shaft 15, the other side of the fifth idle gear 15b is meshed with a sixth gear 16a, the sixth gear 16a is fixed at the right end of the second intermediate shaft 16, the left end of the second intermediate shaft 16 is fixedly provided with a seventh gear 16b, and the seventh gear 16b is meshed with a third gear 17c.

As shown in fig. 12, in the forward gear, the left side of the bidirectional clutch 14c is engaged, so that the first idler gear 14b is fixed to the second-stage output shaft 14, the second-stage output shaft 14 rotates via the first idler gear 14b to drive the second gear 15a, and the second gear 15a drives the third gear 17c and the main drive shaft 17 to rotate in the forward direction. The third gear 17c drives the second intermediate shaft 16 and the sixth gear 16a to rotate in a suspended manner through the seventh gear 16b, the sixth gear 16a drives the fifth idler gear 15b to rotate in a suspended manner on the first intermediate shaft 15, and the fifth idler gear 15b drives the fourth idler gear 14d to rotate in a suspended manner.

As shown in fig. 13, in the reverse gear, the right side of the bidirectional clutch 14c is engaged, so that the fourth idler gear 14d is fixed on the second-stage output shaft 14, the second-stage output shaft 14 drives the fifth idler gear 15b to rotate in a suspended manner on the first intermediate shaft 15 through the fourth idler gear 14d, the fifth idler gear 15b drives the second intermediate shaft 16 to rotate through the sixth gear 16a, the second intermediate shaft 16 drives the third gear 17c to rotate in the reverse direction through the seventh gear 16b, and the third gear 17c drives the main drive shaft 17 to rotate in the reverse direction. Meanwhile, the gear three 17c drives the gear two 15a and the intermediate shaft one 15 to rotate in a suspension mode, and the gear two 15a drives the idler gear one 14b to rotate in a suspension mode.

When the bicycle moves forwards, the left clutch 17a and the right clutch 17e are combined, the left idler gear 17b and the right idler gear 17d are fixedly connected with the main driving 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 18 a; the right idler gear 17d drives the right half shaft 19 to rotate through the right half shaft gear 19b, the right half shaft 19 drives the right wheel to rotate through the right wheel connecting flange 19a, and therefore the vehicle travels in a straight line.

When the vehicle turns to the right, the left clutch 17a is combined independently, the left idler gear 17b is fixedly connected with the main driving 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 18 b; the right idler gear 17d is suspended on the main drive shaft 17, the right wheel remains stationary, and the vehicle turns to the right with a very small turning radius.

When the vehicle turns to the left, the right clutch 17e is independently combined, the right idler gear 17d is fixedly connected with the main driving shaft 17, and the right idler gear 17d drives the right half shaft 19 and the right wheel to independently rotate through the right half shaft gear 19 b; the left idler gear 17b is suspended on the main drive shaft 17, the left wheel remains stationary, the vehicle turns to the left with a very small turning radius. So can switch left turn, walking, right turn etc. at any time, and reduced engineering vehicle's such as tractor turning radius greatly, satisfy the operation demand of various operating modes.

The bidirectional clutch 14c is controlled by a forward and reverse shift fork 14c2, a driving shaft of the forward and reverse shift fork 14c2 is fixed at the center of a forward and reverse capstan 14c1, and a shift rope 14c3 is wound in an outer peripheral rope groove of the forward and reverse capstan 14c1. The gear shifting pull rope 14c3 drives the forward and reverse gear winch 14c1 to rotate, the forward and reverse gear winch 14c1 drives the forward and reverse gear shift fork 14c2 to swing leftwards, and then the bidirectional clutch 14c is switched to a forward gear; the forward reverse shift fork 14c2 swings to the right, and the bidirectional clutch 14c shifts to reverse.

The left clutch 17a is controlled by a left clutch pull arm 17a1, and the driving end of the left clutch pull arm 17a1 is controlled by a left steering pull rope 17a 2; when the left steering cord 17a2 is pulled, the left clutch pull arm 17a1 rotates to switch the left clutch 17a to the disengaged state, and the power of the left wheel is cut off.

The right clutch 17e is controlled by a right clutch pull arm 17e1, and the driving end of the right clutch pull arm 17e1 is controlled by a right steering pull rope 17e2. When the right steering cord 17e2 is pulled, the right clutch pull arm 17e1 rotates to switch the right clutch 17e to the disengaged state, and the power of the right wheel is cut off.

The above description is only a preferred embodiment of the present invention, and not intended to limit the scope of the present invention. In addition to the above embodiments, the present invention may have other embodiments. All the technical solutions formed by adopting equivalent substitutions or equivalent transformations fall within the protection scope claimed by the present invention. The undescribed technical features of the present invention can be realized by or using the prior art, and are not described herein again.

Claims (9)

1. The utility model provides a coordinate variable speed drive, includes belt drive and planet speed change mechanism, belt drive is including installing the drive pulley at one-level input shaft left end, and drive pulley passes through the V-arrangement area and is connected with the driven pulley transmission, and the left end at one-level output shaft is installed to the driven pulley, its characterized in that: the driving belt pulley comprises a left fixed disc and a right movable disc, an outer convex tenon of the left fixed disc extends rightwards and is fixed at the left end of the primary input shaft, a central boss of the right movable disc is sleeved on the outer convex tenon of the left fixed disc, a plurality of right movable disc counter bores with right end openings are uniformly distributed on the central boss of the right movable disc, a driving wheel pressure spring is respectively arranged in each right movable disc counter bore, the right ends of the driving wheel pressure springs jointly abut against the left end surface of a shifting fork flange, the shifting fork flange is connected on an outer spline sleeve through an inner spline, the outer spline sleeve is fixed on the primary input shaft, the central boss of the shifting fork flange extends rightwards, an end face helical tooth movable disc is arranged on the central boss of the shifting fork flange through a movable disc bearing, the right side of the end face helical tooth movable disc and the end face helical tooth fixed disc form tooth type meshing, an outwardly extending clutch pull arm is arranged on the circumference of the end face helical tooth movable, the right end face of the end face helical tooth fixed disc is provided with a fixed disc circumference limiting boss embedded in a groove of the box body.

2. The coordinated variable speed drive of claim 1, wherein: the outer convex tenon of the left fixed disc is correspondingly embedded in the inner sliding groove of the central boss of the right movable disc, a left fixed disc outer sliding groove is formed between the outer convex tenons of the adjacent left fixed discs, and the inner convex tenon of the central boss of the right movable disc is correspondingly embedded in the corresponding left fixed disc outer sliding groove.

3. The coordinated variable speed drive of claim 1, wherein: and a clamp spring is embedded in the periphery of the right end of the outer spline sleeve and is positioned on the right side of the central boss of the shifting fork flange.

4. The coordinated variable speed drive of claim 1, wherein: the right end of the inner ring of the fixed disc bearing abuts against a shaft shoulder of the first-stage input shaft, the right end of the outer spline sleeve abuts against the left side of the inner ring of the fixed disc bearing, the left end of the outer spline sleeve is embedded in an inner step hole of the left fixed disc, and the left fixed disc fixing screw is screwed in the center of the left end of the first-stage input shaft and is tightly pressed at the center of the outer end of the left fixed disc through a gasket.

5. The coordinated variable speed drive of claim 1, wherein: the driven belt pulley comprises a right fixed disc and a left movable disc, a central column of the right fixed disc extends leftwards and is fixed at the left end of the output shaft, a right fixed disc external spline is arranged on the periphery of the right fixed disc central column, the left movable disc is sleeved on the right fixed disc external spline through an internal spline, and a left movable disc support lug extending towards the axial direction is symmetrically arranged at the left end port of the left movable disc; the right fixed disc central column is evenly provided with a through right fixed disc central column through hole and a right fixed disc counter bore with an open right end, each right fixed disc counter bore is respectively provided with a driven wheel pressure spring, each right end of the driven wheel pressure spring is provided with a pressure plate, each right fixed disc central column through hole is respectively provided with a spacer bush, each spacer bush is respectively supported between the pressure plate and a corresponding left movable disc support lug, a plurality of long rod screws are evenly inserted into the pressure plate from right to left, and each long rod screw respectively passes through the corresponding spacer bush and is screwed into a screw hole of the left movable disc support lug.

6. The coordinated variable speed drive of claim 1, wherein: the planetary speed change mechanism comprises an external gear planet carrier disc, a primary gear is mounted in the middle section of the primary input shaft and is meshed with the external gear planet carrier disc, the center of the external gear planet carrier disc is supported in the middle section of the secondary input shaft through a bearing, a planet carrier is fixedly mounted on the right end face of the external gear planet carrier disc, planet shafts are symmetrically mounted on the planet carrier and are supported on the external gear planet carrier disc through bearings respectively, duplex planet gears are mounted in the middle sections of the planet shafts respectively, and each duplex planet gear comprises a duplex big planet gear and a duplex small planet gear which are arranged from left to right; a primary output gear is mounted at the right end of the primary output shaft and meshed with a secondary input large gear through a carrier gear, the secondary input large gear is fixed at the left end of the secondary input shaft, a secondary input small sun gear is arranged at the right end of the secondary input shaft and meshed with the duplex large planetary gears; the right side of the secondary input shaft is coaxially provided with a secondary output shaft, the left end of the secondary output shaft is supported in an inner hole of the planet carrier through a bearing, a secondary output large sun gear is fixed at the left end, and the secondary output large sun gear is meshed with each duplex small planetary gear.

7. The coordinated variable speed drive of claim 6, wherein: the middle section of the secondary output shaft is provided with a two-way clutch through a spline, the left side of the two-way clutch is provided with a first idler gear, the first idler gear is meshed with a second gear, the second gear is fixed at the left end of the first intermediate shaft, the other side of the second gear is meshed with a third gear, and the third gear is fixed at the middle section of the main driving shaft; a left idler gear and a left clutch for controlling the left idler gear are arranged on the left side of the gear III, and a right idler gear and a right clutch for controlling the right idler gear are arranged on the right side of the gear III; the left idler gear is meshed with the left half axle gear, and the right idler gear is meshed with the right half axle gear; the left half axle gear is arranged at the right end of the left half axle, and the left end of the left half axle is provided with a left wheel connecting flange; 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.

8. The coordinated variable speed drive of claim 7, wherein: the right side of the bidirectional clutch is provided with a fourth idle gear, the fourth idle gear is meshed with a fifth idle gear, the fifth idle gear is sleeved at the right end of the first intermediate shaft, the other side of the fifth idle gear is meshed with a sixth gear, the sixth gear is fixed at the right end of the second intermediate shaft, a seventh gear is fixedly mounted at the left end of the second intermediate shaft, and the seventh gear is meshed with a three-phase gear.

9. The coordinated variable speed drive of claim 8, wherein: the bidirectional clutch is controlled by a forward and reverse gear shifting fork, a driving shaft of the forward and reverse gear shifting fork is fixed at the center of a forward and reverse gear winch, and a gear shifting pull rope is wound in an outer peripheral rope groove of the forward and reverse gear winch; the left clutch is controlled by a left clutch pull arm, and the driving end of the left clutch pull arm is controlled by a left steering pull rope; the right clutch is controlled by a right clutch pull arm, and the driving end of the right clutch pull arm is controlled by a right steering pull rope.

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