CN108916346B - Variable-speed transmission method for crawler - Google Patents
Variable-speed transmission method for crawler Download PDFInfo
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- CN108916346B CN108916346B CN201811038953.1A CN201811038953A CN108916346B CN 108916346 B CN108916346 B CN 108916346B CN 201811038953 A CN201811038953 A CN 201811038953A CN 108916346 B CN108916346 B CN 108916346B
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- steering
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
Abstract
A variable speed transmission method for a crawler carrier is characterized in that variable speed transmission is implemented by a variable speed transmission device for the crawler carrier, power is transmitted to an input gear of the variable speed transmission device for the crawler carrier through variable speed transmission, then the power is divided into two paths, one path of power is transmitted to a left gear ring, the other path of power is transmitted to a right gear ring, steering power is input from a left sun gear and a right sun gear, the power is converged through double flows to enable the rotating speeds of the left planetary gear carrier and the right planetary gear carrier to be increased and decreased, finally, the rotating speeds transmitted to a left driving shaft and a right driving shaft are increased and decreased, so that the rotating speed difference is generated between the left crawler and the right crawler, steering power is input from the sun gear of a planetary gear mechanism, the reduction ratio of the steering input power is large, the transmission mechanism is simpler, and the light weight of the device; and the electromagnet in the reversible hydrostatic stepless speed change loop is connected with the first shifting fork shaft, so that the operation difficulty is reduced, and the safety accidents are reduced.
Description
Technical Field
The invention relates to the technical field of variable-speed transmission, in particular to a variable-speed transmission method for a crawler.
Background
In a crawler vehicle transmission using double-flow (double power flow) input power, two sets of planetary gear mechanisms are generally adopted to combine power input by a speed change mechanism and power input by a steering mechanism in parallel, the power input by the speed change mechanism is input by a gear ring or a sun gear of the planetary gear mechanism, the power input by the steering mechanism is input by the sun gear or the gear ring of the planetary gear mechanism, and the combined power is output by a planet carrier. In the double-flow transmission scheme, if the steering input power is input in a stepless speed change mode, the steering is flexible, the steering radius can be continuously changed, the steering angular speed and the rotating speed input by the steering mechanism form a certain proportional relation, the steering is accurate, and the performance is excellent; in the double-flow transmission scheme adopting the planetary gear mechanism, the steering operation direction of a steering operation mechanism (a steering wheel or a steering pull rod) is unchanged (for example, for the steering operation mechanism of the steering wheel type, the steering wheel is deviated to the left side or the right side when the steering wheel moves forwards and backwards), taking the left operation steering mechanism as an example, when the steering mechanism is operated leftwards, after power confluence, the left side crawler belt is decelerated, the right side crawler belt is accelerated, the crawler vehicle turns leftwards, when the steering mechanism is operated backwards, the speed change input power is reversed, the direction of the steering input power is unchanged, although the crawler vehicle runs backwards, the change rule of the left side crawler belt and the right side crawler belt is unchanged because the deflection direction of the steering mechanism is unchanged, namely: the left crawler belt decelerates relative to the advancing direction, the right crawler belt accelerates relative to the advancing direction (namely, the left crawler belt accelerates for reversing, the right crawler belt decelerates for reversing), the tracked vehicle reverses to the right, and when the steering mechanism deflects to the left, the tracked vehicle turns to the left when advancing and turns to the right when reversing, so that the operation is difficult, and even safety accidents occur; particularly, the transport type tracked vehicle has high running speed, and road conditions are poor when the vehicle is used for field or non-road transport, and the vehicle adopting the confluence scheme is easy to have reversing running safety accidents.
Disclosure of Invention
The technical problem to be solved by the present invention is to provide a variable transmission method for a tracked vehicle, so as to solve the above-mentioned drawbacks in the background art.
The technical problem solved by the invention is realized by adopting the following technical scheme:
a variable-speed transmission method for a crawler carrier is characterized in that variable-speed transmission is implemented by a variable-speed transmission device for the crawler carrier, power is transmitted to an input gear of the variable-speed transmission device for the crawler carrier through variable-speed transmission, then the power is divided into two paths, one path of power is transmitted to a left gear ring, the other path of power is transmitted to a right gear ring, when the crawler carrier is in straight line driving, a swash plate of a bidirectional variable pump is placed at a middle zero position, a fixed-quantity motor does not rotate because no hydraulic oil flows in a hydrostatic stepless variable-speed transmission loop, all gears arranged on a steering shaft do not rotate because the fixed-quantity motor does not rotate, and the power of the left gear ring is driven to a left driving shaft by a left planet wheel, a left planet wheel carrier; the power of the right gear ring drives the right crawler belt through a right planet wheel, a right planet wheel carrier, a right driving gear, a right driving driven gear and a right driving shaft; because the rotating speeds of the left sun wheel and the right sun wheel are the same and the directions are opposite, the forces acting on the steering shaft by the left sun wheel and the right sun wheel are the same and the directions are opposite, the steering shaft is self-locked, the driving power cannot be output to the quantitative motor from the steering shaft, and the agricultural tracked carrier can run linearly;
forward steering driving
The variable speed transmission is arranged in a forward gear, a swash plate of the bidirectional variable pump is arranged in a non-intermediate zero position, and when the electromagnet is not electrified:
the variable speed power is transmitted to the input gear through variable speed, then the power is divided into two paths, one path is transmitted to the left gear ring, the other path is transmitted to the right gear ring, the swash plate of the bidirectional variable pump is arranged at a non-middle zero position, the quantitative motor rotates under the hydraulic action, and then all gears arranged on the steering shaft are driven to rotate; the direction of the steering is in a certain relation with the deflection direction of a swash plate of the bidirectional variable pump, and the angular speed of the steering is in a certain proportional relation with the deflection angle of the swash plate of the bidirectional variable pump;
backward steering driving
When the variable speed transmission is arranged in a reverse gear, the swash plate of the bidirectional variable pump is arranged in a non-middle zero position, when the electromagnet is electrified, the power for running in reverse is transmitted to the input gear through variable speed, then the power is divided into two paths, one path of power is transmitted to the left gear ring, the other path of power is transmitted to the right gear ring, because the swash plate of the bidirectional variable pump is arranged in the non-middle zero position, the electromagnet is electrified, and the two-position four-way electromagnetic reversing valve reverses the hydraulic oil path between the bidirectional variable pump and the quantitative motor, so that after the power is converged in the planetary gear mechanism, the reverse turning rule of the agricultural crawler is the same as the forward turning rule, thereby realizing;
a variable speed drive for crawler includes variable speed drive subassembly, power double current transmission subassembly, power take off subassembly, box subassembly and hydraulic system, wherein, variable speed drive subassembly, power double current transmission subassembly are connected with hydraulic system, and power double current transmission subassembly is connected with power take off subassembly, and variable speed drive subassembly, power double current transmission subassembly and power take off subassembly are installed in the box subassembly, and concrete structure is as follows:
in the variable-speed transmission assembly, a gear lever for controlling gear shifting is arranged on a box body, the bottom end of the gear lever is in switching connection with a first shifting fork shaft and a second shifting fork shaft and is used for controlling the first shifting fork shaft and the second shifting fork shaft to realize gear shifting movement, a second shifting fork and a third shifting fork are arranged on the second shifting fork shaft, and a first shifting fork is arranged on the first shifting fork shaft;
a first shaft is arranged on a box body, a third-gear driving gear, a second-gear driving gear, a first-gear driving gear and a reverse-gear driving gear are sequentially sleeved on the first shaft in an empty mode, a second spline hub and a first spline hub are arranged on the first shaft, a second combination sleeve used for being combined with a second shifting fork is arranged on the second spline hub, a first combination sleeve used for being combined with the first shifting fork is arranged on the first spline hub, a shifting groove used for inserting the second shifting fork is circumferentially arranged outside the second combination sleeve, a shifting groove used for inserting the first shifting fork is circumferentially arranged outside the first combination sleeve, under the control of a gear shifting lever, the second shifting fork shaft drives the second combination sleeve to axially slide through the second shifting fork, and the first shifting fork shaft drives the first spline hub to axially slide through the first shifting fork;
the external spline hub is arranged on one side, adjacent to the second spline hub, of the third-gear driving gear, the external spline hub is arranged on one side, adjacent to the second spline hub, of the second-gear driving gear, the external spline hub is arranged on one side, adjacent to the first spline hub, of the first-gear driving gear, the external spline hub is arranged on one side, adjacent to the first spline hub, of the reverse-gear driving gear, and matched transmission of the gear and the combination sleeve and;
the second shaft is arranged on the box body, and is provided with a three-gear driven gear normally meshed with the three-gear driving gear, a two-gear driven gear normally meshed with the two-gear driving gear, a first-gear driven gear normally meshed with the first-gear driving gear and a reverse-gear driven gear;
one end of the reverse gear shaft is arranged on the box body, and the other end of the reverse gear shaft is provided with a reverse gear intermediate gear which is used for being meshed with the reverse gear driven gear and the reverse gear driving gear simultaneously;
in the power double-flow transmission assembly, a gear ring frame is installed on a steering shaft, an input gear is arranged on the outer side of the gear ring frame, a left gear ring and a right gear ring are arranged on the inner side of the gear ring frame, a left sun gear and a right sun gear are respectively installed on the steering shaft, a plurality of left planetary gears are uniformly distributed around the left sun gear through a left planetary gear carrier, one end of the left planetary gear carrier is installed on a box body, the other end of the left planetary gear carrier is sleeved on a connecting shaft in a hollow mode, a left driving gear is installed on the left planetary gear carrier, a plurality of right planetary gears are uniformly distributed around the right sun gear through a right planetary gear carrier, the right planetary gear carrier is; the steering shaft is arranged on the box body, one end of the connecting shaft is arranged on the box body, the other end of the connecting shaft is sleeved on the steering shaft in a hollow mode, a steering driven gear meshed with the steering driving gear is arranged on the steering shaft, a driven bevel gear is arranged on the connecting shaft, the planetary gear is sleeved on a planetary gear shaft, the planetary gear shaft is fixed on the differential steering end cover, one side of the planetary gear is in meshed transmission with the driven bevel gear, and the other side of the planetary gear is in meshed transmission with the driving bevel gear; the driving bevel gear and the driven bevel gear form a constant-speed reverse transmission mechanism through a planetary gear shaft and a planetary gear, and a steering driving gear is arranged on the quantitative motor;
in the power output assembly, a left driving driven gear is connected to a left driving shaft, the left driving driven gear is normally meshed with a left driving gear, one end of the left driving shaft is installed on a box body, and the other end of the left driving shaft is installed on a left driving end cover; the right driving driven gear is connected to the right driving shaft, the right driving driven gear is normally meshed with the right driving gear, one end of the right driving shaft is installed on the box body, and the other end of the right driving shaft is installed on the right driving end cover;
the box body assembly comprises a box body, a differential steering end cover for mounting a planetary gear shaft, a left driving end cover and a right driving end cover, wherein the left driving end cover and the right driving end cover are mounted on the box body;
the hydraulic system is provided with a reversible hydrostatic stepless speed change loop, an oil supplement loop and a hydrostatic stepless speed change transmission loop, wherein the oil supplement loop supplements oil when the hydrostatic stepless speed change transmission loop works and unloads hydraulic oil when the hydrostatic stepless speed change transmission loop does not work, and an electromagnet in the reversible hydrostatic stepless speed change loop is interactively connected with a first shifting fork shaft so as to reduce the operation difficulty.
In the invention, the middle part of the gear shifting lever is arranged on the box body through the supporting seat.
In the invention, the second spline hub is positioned on a shaft between the third gear driving gear and the second gear driving gear.
In the present invention, the first spline hub is located on a shaft between the first gear drive gear and the reverse gear drive gear.
In the present invention, the number of the left planetary gears is any one of 2, 3, and 4.
In the present invention, the number of right planetary gears is any one of 2, 3, and 4.
The reversible hydrostatic stepless speed change loop consists of an electromagnet, a bidirectional variable pump, a one-way valve, an overflow valve, a two-position four-way electromagnetic directional valve and a quantitative motor.
In the invention, the electromagnet is arranged on the two-position four-way electromagnetic reversing valve.
In the invention, the oil supplementing loop consists of an oil tank, a filter, an oil supplementing pump, an oil pipe and an overflow valve.
In the invention, the hydrostatic stepless speed change transmission loop consists of a bidirectional variable pump and a quantitative motor, and the oil supplementing loop supplements oil when the hydrostatic stepless speed change transmission loop works and unloads hydraulic oil to an oil tank by an overflow valve when the hydrostatic stepless speed change transmission loop does not work.
In the present invention, the power transmission route:
first gear: the first shifting fork shaft moves leftwards, the first shifting fork drives the first combination sleeve to move leftwards, and power is transmitted to the first combination sleeve through the first spline hub and then transmitted to the first-gear driven gear through the first-gear driving gear and output from the first-gear driven gear;
and (2) second: the second shifting fork shaft moves rightwards, the second and third shifting forks drive the second and third gear combination sleeve to move rightwards, power is transmitted to the second and third gear combination sleeve from the first shaft through the second and third gear spline hub, then transmitted to the second driven gear through the second driving gear, transmitted to the second shaft through the second driven gear and output from the first driven gear;
and (3) third gear: the second shifting fork shaft moves leftwards, the second and third shifting forks drive the second and third gear combination sleeve to move leftwards, and power is transmitted to the second and third gear combination sleeve from the first shaft through the second and third gear spline hub, then transmitted to the third gear driven gear through the third gear driving gear, transmitted to the second shaft through the third gear driven gear and output from the first gear driven gear;
reversing gear: the first shifting fork shaft moves rightwards, the first shifting fork drives the first combination sleeve to move rightwards, power is transmitted to the first combination sleeve from the first shaft through the first spline hub, then transmitted to the reverse gear intermediate gear through the reverse gear driving gear, transmitted to the reverse gear driven gear from the reverse gear intermediate gear, transmitted to the second shaft and output from the first gear driven gear;
power double flow afflux
The first-gear driven gear is normally meshed with the input gear, and the driving power transmitted by variable speed is transmitted to the left gear ring and the right gear ring through the input gear;
the steering power input by the hydraulic system is input by a quantitative motor, the quantitative motor drives a steering driving gear to be meshed with a steering driven gear so as to drive a steering shaft, and the steering shaft drives a left sun gear and a right sun gear;
the running power is input by the left gear ring and the right gear ring, the steering power is input by the left sun gear and the right sun gear, and the double-flow power is converged and then output by the left planetary gear carrier and the right planetary gear carrier of the planetary gear mechanism.
Has the advantages that:
1) the variable speed transmission device for the crawler carrier adopts the fixed-displacement motor and the bidirectional variable pump to form a hydrostatic stepless variable speed transmission loop so as to realize the continuous change of the steering radius of the crawler carrier and improve the steering accuracy;
2) the driving power and the steering power in the variable speed transmission device for the crawler transport vehicle are converged under the coaxial condition, the structure is compact, and the manufacturing process is simplified;
3) the speed change transmission device for the crawler carrier is provided with the reversing valve between the quantitative motor and the bidirectional variable pump, and after the reverse gear is changed, the hydraulic system automatically switches the hydraulic loop to realize the same steering characteristic of forward and backward movement;
4) the variable speed transmission device for the crawler carrier disclosed by the invention has the advantages that the electromagnet in the reversible hydrostatic stepless speed change loop is connected with the first shifting fork shaft, so that the operation difficulty is reduced, and the occurrence of safety accidents is reduced;
5) the steering power in the variable speed transmission device for the crawler carrier is input by the sun gear of the planetary gear mechanism, the reduction ratio of the steering input power is large, the transmission mechanism is simpler, and the light weight of the device is effectively realized.
Drawings
FIG. 1 is a schematic structural connection diagram of a preferred embodiment of the present invention.
FIG. 2 is a schematic view of the structural connection of the variable speed drive assembly in the preferred embodiment of the present invention.
FIG. 3 is a schematic view of the structural connection of the power dual flow transmission assembly in the preferred embodiment of the present invention.
Fig. 4 is a schematic structural connection diagram of a power output assembly in a preferred embodiment of the invention.
Fig. 5 is a schematic structural connection diagram of a hydraulic system according to a preferred embodiment of the present invention.
Detailed Description
In order to make the technical means, the creation characteristics, the achievement purposes and the effects of the invention easy to understand, the invention is further explained below by combining the specific drawings.
Referring to fig. 1 to 5, a variable speed transmission method for a crawler carrier, which implements variable speed transmission by using a variable speed transmission device for the crawler carrier, the variable speed transmission device for the crawler carrier includes a variable speed transmission assembly a, a power dual-flow transmission assembly B, a power output assembly C, a box assembly D and a hydraulic system E, the variable speed transmission assembly a, the power dual-flow transmission assembly B are connected with the hydraulic system E, the power dual-flow transmission assembly B is connected with the power output assembly C, and the variable speed transmission assembly a, the power dual-flow transmission assembly B and the power output assembly C are installed in the box assembly D, and the specific structure is as follows:
the speed change transmission assembly A comprises a shift lever A11, a support seat A12, a first shift fork shaft A13, a second shift fork shaft A14, a second and third shift fork A15, a first shift fork A16, a shaft A21, a third gear driving gear A22, a second and third gear combination sleeve A23, a second gear driving gear A24, a second spline hub A25, a first gear driving gear A26, a first combination sleeve A27, a reverse gear driving gear A28, a first spline hub A29, a second shaft A31, a third gear driven gear A32, a second gear driven gear A33, a first gear driven gear A34, a reverse gear driven gear A35, a reverse gear shaft A41 and a reverse gear intermediate gear A42; one end of a gear shift lever A11 is used for controlling gear shifting, the middle part of the gear shift lever A11 is installed on a box body D1 through a support seat A12, the other end of the gear shift lever A11 is connected with a first shifting fork shaft A13 and a second shifting fork shaft A14 and is used for controlling the first shifting fork shaft A13 and the second shifting fork shaft A14 to realize gear shifting movement, a second-third-gear shifting fork A15 is arranged on the second shifting fork shaft A14, and a first shifting fork A16 is arranged on the first shifting fork shaft A13;
two ends of a first shaft A21 are mounted on a box body D1 through a bearing D2, a third-gear driving gear A22, a second-gear driving gear A24, a first-gear driving gear A26 and a reverse-gear driving gear A28 are sequentially sleeved on a first shaft A21 in an empty manner, the four gears are axially limited relative to the first shaft A21, a second-spline hub A22 is mounted on the first shaft A22 between the third-gear driving gear A22 and the second-gear driving gear A22, the first shaft A22 is fixedly connected with the second-spline hub A22 for transmission, a second-spline coupling sleeve A22 for coupling with the second-gear shifting fork A22 is arranged on the second-gear spline hub A22, the second-spline hub A22 is matched with the second-gear shifting sleeve A22 through an inner and outer spline coupling groove, and the second-gear shifting sleeve A22 is inserted into the second-gear shifting sleeve 22 for limiting the axial direction of the second-gear shifting fork A22. Under the operation of a gear shift lever A11, a second shift fork shaft A14 drives a second combination sleeve A23 to slide axially through a second shift fork A15, a first combination sleeve A27 used for being combined with a first shift fork A16 is arranged on a first spline hub A29, the first spline hub A29 and the first combination sleeve A27 are in fit transmission through internal and external splines, a shifting groove is formed in the outer circumferential direction of a first combination sleeve A27, the first shift fork A16 is inserted into the shifting groove of the first combination sleeve A27 to limit the axial position of the first combination sleeve A27, and under the operation of a gear shift lever A11, the first shift fork shaft A13 drives the first spline hub A27 to slide axially through the first shift fork A16;
when the second shifting fork A15 shifts the second combination sleeve A23 to move axially towards the third gear driving gear A22, the external spline hub arranged on one side of the third gear driving gear A22 is in matched transmission with the internal spline of the second combination sleeve A23, meanwhile, the internal spline of the second combination sleeve A23 is in matched transmission with the second spline hub A25, and the power of the first shaft A21 is transmitted to the third gear driving gear A22 from the second spline hub A25 through the second combination sleeve A23;
when the second shift fork A15 shifts the second combination sleeve A23 to move axially towards the second driving gear A24, the external spline hub arranged on one side of the second driving gear A24 is in matched transmission with the internal spline of the second combination sleeve A23, meanwhile, the internal spline of the second combination sleeve A23 is in matched transmission with the second spline hub A25, and the power of the shaft A21 is transmitted to the second driving gear A24 from the second spline hub A25 through the second combination sleeve A23;
when the first shift fork A16 shifts the first combination sleeve A27 to move axially towards the first gear driving gear A26, the external spline hub arranged on one side of the first gear driving gear A26 is in matched transmission with the internal spline of the first combination sleeve A27, meanwhile, the internal spline of the first combination sleeve A27 is in matched transmission with the first spline hub A29, and the power of a shaft A21 is transmitted to the first gear driving gear A26 from the first spline hub A29 through the first combination sleeve A27;
when the first shifting fork A16 shifts the first combination sleeve A27 to move axially towards the reverse driving gear A28, the external spline hub arranged on one side of the reverse driving gear A28 is in matched transmission with the internal spline of the first combination sleeve A27, meanwhile, the internal spline of the first combination sleeve A27 is in matched transmission with the first spline hub A29, and the power of a shaft A21 is transmitted to the reverse driving gear A28 from the first spline hub A29 through the first combination sleeve A27;
two ends of a secondary shaft A31 are mounted on a box body D1 through bearings D2, a three-gear driven gear A32 in constant meshing with a three-gear driving gear A22, a two-gear driven gear A33 in constant meshing with a two-gear driving gear A24, a first-gear driven gear A34 in constant meshing with the first-gear driving gear A26 and a reverse-gear driven gear A35 in constant meshing with a reverse-gear intermediate gear A42 are sequentially arranged on the secondary shaft A31 through splines, the axial positions of the three-gear driven gear A32, the two-gear driven gear A33, the first-gear driven gear A34 and the reverse-gear driven gear A35 relative to the secondary shaft A31 are limited, the three-gear driven gear A32, the two-gear driven gear A33 and the reverse-gear driven gear A35 are power input gears relative to the power transmission of the secondary shaft A31, and the first-gear A34 is a power input gear and a power output gear;
one end of the reverse gear shaft A41 is mounted on the box body D1 through a bearing D2, and the other end is provided with a reverse gear intermediate gear A42 which is used for being simultaneously meshed with the reverse gear driven gear A35 and the reverse gear driving gear A28;
the power double-current transmission assembly B comprises a left driving assembly B1, a right driving assembly B2 and a power double-current transmission assembly B3, the left driving assembly B1 comprises a ring gear frame B11, an input gear B12, a left planetary gear B13, a left planetary gear frame B14, a left driving gear B15, a left sun gear B16 and a left ring gear B17, the right driving assembly B2 comprises a ring gear frame B11, an input gear B12, a right planetary gear B23, a right planetary gear frame B24, a right driving gear B25, a right sun gear B26 and a right ring gear B27, the power double-current transmission assembly B3 comprises a planetary gear B31, a driving bevel gear B32, a driven bevel gear B33, a planetary gear B34, a connecting shaft B34, a steering shaft B34, a driven gear B34 and a steering gear B34, the ring gear frame B34 is mounted on the steering shaft B34 through a bearing D34, the inner side of the ring gear frame B34 and the inner side of the ring gear B34 and the inner side of the left ring gear B34 is provided with a free gear 34, the ring gear frame B34, the input gear B34 and the input gear B, the left sun gear B16 is mounted on the steering shaft B36 in a spline fit mode, the left planetary gears B13 are uniformly distributed around the left sun gear B16 through a left planetary gear carrier B14, the number of the left planetary gears B13 is n (n is any one of 2, 3 and 4), one end of the left planetary gear carrier B14 is mounted on the box body D1 through a bearing D2, the other end of the left planetary gear carrier B14 is sleeved on the connecting shaft B35 through a bearing D2 in an empty mode, and the left driving gear B15 is mounted on the left planetary gear carrier B14 in a spline fit mode; a right sun gear B26 is mounted on the steering shaft B36 by spline fitting, right planetary gears B23 are uniformly distributed around the right sun gear B26 by a right planetary carrier B24, the number of right planetary gears B23 is n (n is any one of 2, 3 and 4), a right planetary carrier B24 is mounted on the box body D1 by a bearing D2, and a right drive gear B25 is mounted on the right planetary carrier B24 by spline fitting;
two ends of a steering shaft B36 are mounted on a box body D1 through bearings D2, one end of a connecting shaft B35 is mounted on a box body D1 through a bearing D2, the other end of the connecting shaft B35 is sleeved on a steering shaft B36 in a hollow mode, a steering driven gear B37 meshed with a steering driving gear B38 is mounted on the steering shaft B36 through splines, a driven bevel gear B33 is mounted on the connecting shaft B35 through spline matching, a planetary gear B31 is sleeved on a planetary gear shaft B34, a planetary gear shaft B34 is fixed on a differential steering end cover D3, one side of a planetary gear B31 is in meshing transmission with the driven bevel gear B33, and the other side of the planetary gear B31 is in meshing transmission; the driving bevel gear B32 and the driven bevel gear B33 form a constant speed reverse transmission mechanism through a planetary gear shaft B34 and a planetary gear B31, and a steering driving gear B38 is installed on a quantitative motor E11; the bearing D2 limits the axial freedom degree of the steering shaft B36 and the connecting shaft B35;
the power output assembly C comprises a left driving assembly C1 and a right driving assembly C2, the left driving assembly C1 consists of a left driving driven gear C11 and a left driving shaft C12, the right driving assembly C2 consists of a right driving driven gear C21 and a right driving shaft C22, the left driving driven gear C11 is connected to a left driving shaft C12 through a spline, the left driving driven gear C11 is constantly meshed with a left driving gear B15, one end of the left driving shaft C12 is installed on a box D1 through a bearing D2, and the other end of the left driving shaft C12 is installed on a left driving end cover D5; the right driving driven gear C21 is connected to the right driving shaft C22 through a spline, the right driving driven gear C21 is in constant mesh transmission with the right driving gear B25, one end of the right driving shaft C22 is installed on the box body D1 through a bearing D2, and the other end of the right driving shaft C22 is installed on the right driving end cover D6;
the box body assembly D comprises a box body D1, a bearing D2, a differential steering end cover D3, a bolt D4, a left driving end cover D5 and a right driving end cover D6, wherein the left driving end cover D5 is installed on the box body D1 through a bolt D4, and the right driving end cover D6 is installed on the box body D1 through a bolt D4;
the hydraulic system comprises a fixed-displacement motor E11, an oil tank E12, a bidirectional variable pump E13, an oil pipe E14, a one-way valve E15, an overflow valve E16, a filter E21, an oil supplementing pump E22, a two-position four-way electromagnetic directional valve E31 and an electromagnet E32, wherein, the bidirectional variable pump E13, the one-way valve E15, the overflow valve E16, the two-position four-way electromagnetic directional valve E31 and the fixed-displacement motor E11 form a reversible hydrostatic stepless speed change loop, the oil tank E12, the filter E21, the oil supplement pump E22, the oil pipe E14 and the overflow valve E16 form an oil supplement loop, the bidirectional variable pump E13 and the fixed-displacement motor E11 form a hydrostatic stepless speed change transmission loop, the oil supplement loop can supplement oil when the hydrostatic stepless speed change transmission loop works, when the hydraulic oil pump is in a non-working state, the overflow valve E16 unloads the hydraulic oil to the oil tank E12, the electromagnet E32 is installed on the two-position four-way electromagnetic directional valve E31, and the electromagnet E32 is interactively connected with the first shifting fork shaft A13, so that the operation difficulty is reduced.
1) A power transmission route:
first gear: the first shifting fork shaft A13 moves leftwards, the first shifting fork A15 drives the first combination sleeve A27 to move leftwards, power is transmitted to the first combination sleeve A27 through a first spline hub A28 by a shaft A21, then transmitted to the first gear driven gear A34 through a first gear driving gear A26, and output from the first gear driven gear A34;
and (2) second: the second shift fork shaft A14 moves rightwards, the second and third shift fork A15 drives the second and third gear combination sleeve A23 to move rightwards, power is transmitted to the second and third gear combination sleeve A23 from the first shaft A21 through the second and third gear spline hub A25, then is transmitted to the second driven gear A33 through the second driving gear A24, is transmitted to the second shaft A31 through the second driven gear A33, and is output from the first driven gear A34;
and (3) third gear: the second-gear shifting fork shaft A14 moves leftwards, the second-gear and third-gear shifting fork A15 drives the second-gear and third-gear combination sleeve A23 to move leftwards, power is transmitted to the second-gear and third-gear combination sleeve A23 through the second-gear and third-gear spline hub A25 by the first shaft A21, then is transmitted to the third-gear driven gear A32 through the third-gear driving gear A22, is transmitted to the second shaft A31 by the third-gear driven gear A32, and is output from the first-gear driven gear A34;
reversing gear: the first shifting fork shaft A13 moves rightwards, the first shifting fork A15 drives the first combination sleeve A27 to move rightwards, power is transmitted to the first combination sleeve A27 through a first spline hub A29 by a first shaft A21, then is transmitted to the reverse gear intermediate gear A42 through a reverse gear driving gear A28, is transmitted to the reverse gear driven gear A35 through the reverse gear intermediate gear A42, and is transmitted to a second shaft A31 by the reverse gear driven gear A35 and is output from the first gear driven gear A34;
2) power double flow afflux
The first gear driven gear A34 is in constant mesh with the input gear B12, and the running power transmitted by variable speed is transmitted to the left gear ring B17 and the right gear ring B27 through the input gear B11;
the steering power input by the hydraulic system E is input by a fixed displacement motor E11, the fixed displacement motor E11 drives a steering driving gear B38 to be meshed with a steering driven gear B37, further drives a steering shaft B36, and the steering shaft B36 drives a left sun gear B16 and a right sun gear B26;
the running power is input from a left gear ring B17 and a right gear ring B27, the steering power is input from a left sun gear B16 and a right sun gear B26, and the double-flow power is converged and then output from a left planetary gear carrier B14 and a right planetary gear carrier B24 of the planetary gear mechanism;
3) working principle of straight line running
The power is transmitted to an input gear B12 through variable speed, then the power is divided into two paths, one path is transmitted to a left gear ring B17, the other path is transmitted to a right gear ring B27, when the vehicle runs linearly, a swash plate of a bidirectional variable pump E13 is arranged at a middle zero position, a quantitative motor E11 does not rotate because no hydraulic oil flows in a hydrostatic stepless variable transmission loop, all gears arranged on a steering shaft B36 do not rotate because a quantitative motor E11 does not rotate, and the power of the left gear ring B17 is transmitted to a left driving shaft C12 through a left planet wheel B13, a left planet wheel carrier B14, a left driving gear B15 and a left driving driven gear C11, so as to drive a left crawler belt; the power of the right gear ring B27 is driven by a right planet wheel B23, a right planet wheel carrier B24, a right driving gear B25, a right driving driven gear C21 and a right driving shaft C22 to further drive a right crawler; because the rotation characteristics of the left sun wheel B16 and the right sun wheel B26 are the same rotation speed and opposite directions, when the agricultural crawler belt carrier is in straight line driving, the force acting on the steering shaft B36 through the left sun wheel B16 and the right sun wheel B26 is a pair of forces with the same magnitude and opposite directions, the steering shaft B36 is self-locked, the agricultural crawler belt carrier is in straight line driving, and the driving power cannot be output to the quantitative motor E11 from the steering shaft B36;
4) forward steering driving
When the variable speed drive is placed in forward gear, the swash plate of the bidirectional variable pump E13 is placed in a non-neutral zero position, and electromagnet E32 is not energized:
the variable speed power is transmitted to an input gear B12 through variable speed, then the power is divided into two paths, one path is transmitted to a left gear ring B17, the other path is transmitted to a right gear ring B27, because a swash plate of a bidirectional variable pump E13 is arranged at a non-middle zero position, a quantitative motor E11 rotates under the hydraulic action, all gears arranged on a steering shaft B36 are driven to rotate, because the rotating speeds of a left sun gear B16 and a right sun gear B26 are the same and are opposite in direction, the rotating speeds of a left planetary gear carrier B14 and a right planetary gear carrier B24 are increased and decreased after the power is converged through double flows, and finally the rotating speeds transmitted to a left driving shaft B15 and a right driving shaft B25 are increased and decreased, so that the rotating speed difference between a left crawler and a right crawler occurs, and the steering is realized; the direction of the steering is in a certain relation with the deflection direction of the swash plate of the bidirectional variable pump E13, and the angular speed of the steering is in a certain proportion relation with the deflection angle of the swash plate of the bidirectional variable pump E13;
5) backward steering driving
It can be known from forward steering, when the input gear B12 rotates in the opposite direction, because the rotating direction of the fixed-displacement motor E11 for steering is not changed, the motion law of the steering system is not changed, after power is converged, the rotating speed change law of the left-side crawler belt and the right-side crawler belt is not changed, so that under the same steering operation condition, the forward and reverse driving directions are reversed, which brings great inconvenience to driving and even influences driving safety, in order to solve the above problems, a two-position four-way electromagnetic directional valve E31 which is synchronously opened under the reverse condition is arranged:
when the variable speed transmission is set to a reverse gear, the swash plate of the bidirectional variable pump E13 is set to a non-intermediate zero position, and the electromagnet E32 is electrified, the power for running in a reverse mode is transmitted to the input gear B12 through variable speed, then the power is divided into two paths, one path is transmitted to the left gear ring B17, the other path is transmitted to the right gear ring B27, because the swash plate of the bidirectional variable pump E13 is set to the non-intermediate zero position, the electromagnet E32 is electrified, and the two-position four-way electromagnetic reversing valve reverses the hydraulic oil path between the bidirectional variable pump E13 and the quantitative motor E11, so after the power is converged in the planetary gear mechanism, the reverse turning law of the agricultural crawler is the same as the forward turning law, so that the reverse turning running in a reverse mode is realized, and in order to reduce the operation difficulty, the electromagnet E32.
The foregoing shows and describes the general principles and broad features of the present invention and advantages thereof. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only to illustrate the principle of the present invention, but that various changes and modifications may be made therein without departing from the spirit and scope of the present invention, which fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (9)
1. A variable-speed transmission method for a crawler carrier is characterized in that a variable-speed transmission device for the crawler carrier is adopted to implement variable-speed transmission, power is transmitted to an input gear of the variable-speed transmission device for the crawler carrier through variable-speed transmission, then the power is divided into two paths, one path of power is transmitted to a left gear ring, the other path of power is transmitted to a right gear ring, when the crawler carrier is driven in a straight line, a swash plate of a bidirectional variable pump is placed at a middle zero position, a hydrostatic oil does not flow in a stepless variable-speed transmission loop, a quantitative motor does not rotate, all gears arranged on a steering shaft do not rotate because the quantitative motor does not rotate, and the power of the left gear ring is transmitted to a left driving shaft through a left planet wheel, a left planet wheel carrier, a left driving gear; the power of the right gear ring drives the right crawler belt through a right planet wheel, a right planet wheel carrier, a right driving gear, a right driving driven gear and a right driving shaft; because the rotating speeds of the left sun wheel and the right sun wheel are the same and the directions are opposite, the forces acting on the steering shaft through the left sun wheel and the right sun wheel are the same and the directions are opposite, the steering shaft is self-locked, and the agricultural crawler transport vehicle runs linearly;
when the variable speed transmission is arranged at a forward gear, a swash plate of the bidirectional variable pump is arranged at a non-intermediate zero position, an electromagnet is not electrified, variable speed power is transmitted to an input gear through variable speed, then the power is divided into two paths, one path of power is transmitted to a left gear ring, the other path of power is transmitted to a right gear ring, a quantitative motor rotates under the hydraulic action due to the fact that the swash plate of the bidirectional variable pump is arranged at the non-intermediate zero position, all gears arranged on a steering shaft are driven to rotate, and the power is converged through double flows to enable the rotating speeds of a left planetary gear carrier and a right planetary gear carrier to be increased and reduced, and finally the rotating speeds transmitted to the left driving shaft and the right driving shaft are increased and reduced, so that a rotating speed difference occurs between a left crawler belt and a right crawler belt, and steering is achieved;
when the variable speed transmission is arranged in a reverse gear, the swash plate of the bidirectional variable pump is arranged in a non-middle zero position, when the electromagnet is electrified, the power for running in reverse is transmitted to the input gear through variable speed, then the power is divided into two paths, one path of power is transmitted to the left gear ring, the other path of power is transmitted to the right gear ring, because the swash plate of the bidirectional variable pump is arranged in the non-middle zero position, the electromagnet is electrified, and the two-position four-way electromagnetic reversing valve reverses the hydraulic oil path between the bidirectional variable pump and the quantitative motor, so that after the power is converged in the planetary gear mechanism, the reverse turning rule of the agricultural crawler is the same as the forward turning rule, thereby realizing;
a variable speed drive for crawler includes variable speed drive subassembly, power double current transmission subassembly, power take off subassembly, box subassembly and hydraulic system, and variable speed drive subassembly, power double current transmission subassembly are connected with hydraulic system, and variable speed drive subassembly is connected with power double current transmission subassembly, and power double current transmission subassembly is connected with power take off subassembly, and variable speed drive subassembly, power double current transmission subassembly and power take off subassembly are installed in the box subassembly, and concrete structure is as follows:
in the variable-speed transmission assembly, a gear lever for controlling gear shifting is arranged on a box body, the bottom end of the gear lever is in switching connection with a first shifting fork shaft and a second shifting fork shaft and is used for controlling the first shifting fork shaft and the second shifting fork shaft to realize gear shifting movement, a second shifting fork and a third shifting fork are arranged on the second shifting fork shaft, and a first shifting fork is arranged on the first shifting fork shaft;
a first shaft is arranged on the box body, a third gear driving gear, a second gear driving gear, a first gear driving gear and a reverse gear driving gear are sequentially sleeved on the first shaft in an empty mode, a second spline hub and a first spline hub are arranged on the first shaft, a second combination sleeve used for being combined with a second shifting fork is arranged on the second spline hub, a first combination sleeve used for being combined with the first shifting fork is arranged on the first spline hub, a shifting groove used for inserting the second shifting fork is circumferentially arranged outside the second combination sleeve, and a shifting groove used for inserting the first shifting fork is circumferentially arranged outside the first combination sleeve;
the external spline hub is arranged on one side, adjacent to the second spline hub, of the third-gear driving gear, the external spline hub is arranged on one side, adjacent to the second spline hub, of the second-gear driving gear, the external spline hub is arranged on one side, adjacent to the first spline hub, of the first-gear driving gear, and the external spline hub is arranged on one side, adjacent to the first spline hub, of the reverse-gear driving gear;
the second shaft is arranged on the box body, and is provided with a three-gear driven gear normally meshed with the three-gear driving gear, a two-gear driven gear normally meshed with the two-gear driving gear, a first-gear driven gear normally meshed with the first-gear driving gear and a reverse-gear driven gear;
one end of the reverse gear shaft is arranged on the box body, and the other end of the reverse gear shaft is provided with a reverse gear intermediate gear which is used for being meshed with the reverse gear driven gear and the reverse gear driving gear simultaneously;
in the power double-flow transmission assembly, a gear ring frame is installed on a steering shaft, an input gear is arranged on the outer side of the gear ring frame, a left gear ring and a right gear ring are arranged on the inner side of the gear ring frame, a left sun gear and a right sun gear are respectively installed on the steering shaft, a plurality of left planetary gears are uniformly distributed around the left sun gear through a left planetary gear carrier, one end of the left planetary gear carrier is installed on a box body, the other end of the left planetary gear carrier is sleeved on a connecting shaft in a hollow mode, a left driving gear is installed on the left planetary gear carrier, a plurality of right planetary gears are uniformly distributed around the right sun gear through a right planetary gear carrier, the right planetary gear carrier is; the steering shaft is arranged on the box body, one end of the connecting shaft is arranged on the box body, the other end of the connecting shaft is sleeved on the steering shaft in a hollow mode, a steering driven gear meshed with the steering driving gear is arranged on the steering shaft, a driven bevel gear is arranged on the connecting shaft, the planetary gear is sleeved on a planetary gear shaft, the planetary gear shaft is fixed on the differential steering end cover, one side of the planetary gear is in meshed transmission with the driven bevel gear, and the other side of the planetary gear is in meshed transmission with the driving bevel gear; the steering driving gear is arranged on the quantitative motor;
in the power output assembly, a left driving driven gear is connected to a left driving shaft, the left driving driven gear is normally meshed with a left driving gear, one end of the left driving shaft is installed on a box body, and the other end of the left driving shaft is installed on a left driving end cover; the right driving driven gear is connected to the right driving shaft, the right driving driven gear is normally meshed with the right driving gear, one end of the right driving shaft is installed on the box body, and the other end of the right driving shaft is installed on the right driving end cover;
the box body assembly comprises a box body, a differential steering end cover for mounting a planetary gear shaft, a left driving end cover and a right driving end cover, wherein the left driving end cover and the right driving end cover are mounted on the box body;
the hydraulic system is provided with a reversible hydrostatic stepless speed change loop, an oil supplement loop and a hydrostatic stepless speed change transmission loop, wherein the oil supplement loop supplements oil when the hydrostatic stepless speed change transmission loop works and unloads hydraulic oil when the hydrostatic stepless speed change transmission loop does not work, the reversible hydrostatic stepless speed change loop consists of an electromagnet, a bidirectional variable pump, a one-way valve, an overflow valve, a two-position four-way electromagnetic reversing valve and a quantitative motor, and the electromagnet is in interactive connection with a first shifting fork shaft.
2. The method of claim 1, wherein the second splined hub is located on a shaft between the third drive gear and the second drive gear.
3. The method of claim 1, wherein the first splined hub is located on a shaft between the first drive gear and the reverse drive gear.
4. The variable speed transmission method for a crawler carrier according to claim 1, wherein the number of the left planetary gears is any one of 2, 3 and 4.
5. The variable speed transmission method for a crawler carrier according to claim 1, wherein the number of the right planetary gears is any one of 2, 3 and 4.
6. The method of claim 1, wherein the electromagnets are mounted on a two-position four-way electromagnetic directional valve.
7. The variable speed transmission method for the tracked vehicle according to claim 1, wherein the oil supplementing loop is composed of an oil tank, a filter, an oil supplementing pump, an oil pipe and an overflow valve.
8. The variable speed transmission method for a tracked vehicle according to claim 1, characterized in that the hydrostatic continuously variable transmission circuit consists of a bidirectional variable pump and a fixed displacement motor.
9. The method of claim 1, wherein the shift lever is mounted to the housing at a central portion thereof by a support.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811038953.1A CN108916346B (en) | 2018-09-06 | 2018-09-06 | Variable-speed transmission method for crawler |
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| CN201811038953.1A CN108916346B (en) | 2018-09-06 | 2018-09-06 | Variable-speed transmission method for crawler |
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| CN108916346B true CN108916346B (en) | 2021-02-26 |
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| CN108843787B (en) * | 2018-09-06 | 2019-12-24 | 湖南农业大学 | Variable speed transmission device for crawler transport vehicle |
| CN110239638A (en) * | 2019-04-30 | 2019-09-17 | 长沙桑铼特农业机械设备有限公司 | A kind of two track drive tractor proportion expressions steering drive method |
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| DE102011115002A1 (en) * | 2011-10-06 | 2013-04-11 | Liebherr-Components Biberach Gmbh | Power split transmission |
| KR101900264B1 (en) * | 2014-05-29 | 2018-09-20 | 대동공업주식회사 | Transmission assembly of an agriculture vehicle |
| CN204942497U (en) * | 2015-09-16 | 2016-01-06 | 湖南省农友机械集团有限公司 | A kind of double dynamical input type three keeps off endless-track vehicle speed changer |
| CN106080772B (en) * | 2016-06-24 | 2018-11-20 | 湖南农业大学 | Self-lock differential formula crawler belt driving and steering system |
| CN106697089B (en) * | 2017-02-15 | 2018-02-02 | 长沙桑铼特农业机械设备有限公司 | A kind of multichannel crawler equipment remote control equipment |
| CN107264657B (en) * | 2017-07-26 | 2023-08-18 | 长沙九十八号工业设计有限公司 | Two-crawler tractor with high-efficiency power speed change system and transmission method thereof |
| CN108999949B (en) * | 2018-09-06 | 2021-04-09 | 湖南农业大学 | Differential steering variable speed transmission device for tracked vehicle |
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