CN105128934B - Double dynamical input and differential type turn to endless-track vehicle speed changer - Google Patents

Abstract

Dual power input and differential steering crawler vehicle transmission, in which the power input mechanism, dual power input mechanism, intermediate transmission mechanism, differential drive mechanism and PTO power output mechanism are all installed on the box body; the left crawler drive mechanism, right The crawler drive mechanism has the same structure and is symmetrically installed on both sides of the box body. The power input mechanism is respectively connected with the PTO power output mechanism and the double power input mechanism. The transmission of the double power input mechanism is connected with the intermediate transmission mechanism, and the intermediate transmission mechanism is connected with the differential drive mechanism. , the power output is driven by the differential drive mechanism to drive the left crawler drive mechanism and the right crawler drive mechanism; through the conversion of the coupling sleeve, the problem of the combination of mechanical direct transmission and hydraulic stepless type is solved, and the high transmission efficiency and the control performance of the crawler vehicle are effectively improved; At the same time, the hydraulic motor is used to control the positive and negative rotation of the planetary gears of the planetary gear mechanism on both sides of the driving wheel to change the speed at both ends of the driving drive power output shaft, and then realize the steering.

Description

Dual Power Input and Differential Steering Tracked Vehicle Transmission

technical field

The invention relates to the technical field of tracked vehicle drive, in particular to a dual power input and differential steering tracked vehicle transmission.

Background technique

my country is the largest rice producer and consumer in the world, with an annual planting area of about 28.6 million hectares, accounting for 1/5 of the global rice planting area, and an annual output of 185 million tons of rice, accounting for 1/3 of the world's total output. The southern rice field area is mainly Including Hunan, Jiangxi, Guangdong, Guangxi and other ten provinces, rice production accounts for more than 60% of the country, and it is the main rice producing area in my country. Paddy fields in the south mainly grow rice and rapeseed crops, and the paddy fields are almost full of water all the year round, there is no freezing in winter, the land is wet, and the soil bearing capacity is poor. The gear teeth damage the structure of the plow bottom layer, causing the plow bottom layer to be soft. And with the repeated operation of the wheeled operation machinery, the depth of the plow bottom layer continues to deepen. Every time plowing will cause the plow bottom mud layer to deepen once. When the plow bottom layer deepens, larger diameter wheels and larger horsepower and weight Driven by operating machinery, it will cause a vicious circle, making the paddy field a field with deep mud feet. Finally, when it reaches a certain level, it will easily lead to the inability of tillage machines, rice transplanters, combine harvesters and other machinery to work in the field. Although flooded rice fields can increase crop yields, reduce heavy metal pollution, reduce the amount of chemical fertilizers, and protect farmland water and soil, continuous flooding near the rice harvest season will make the rice fields softer, and traditional wheeled agricultural machinery is prone to slipping or getting stuck when entering the rice fields , so that the basic work cannot be completed.

Because the grounding area of tracked vehicles is large, and the grounding specific pressure of the crawler is small, its value is close to the grounding specific pressure of human beings, so it is especially suitable for the southern paddy fields. At present, the crawler-type operating vehicles in the southern paddy fields mainly include crawler tractors and crawler harvesters. However, the variable speed transmission systems of these tracked vehicles usually adopt two types, one is the pure mechanical power transmission system to transmit power, which has the advantages of simple structure and high efficiency, but the pure mechanical power transmission mechanism has complex gear shifting operations, and at the same time Because agricultural machinery operators usually do not have the skills to drive cars or tractors, it is difficult to control the coordination of clutch, accelerator and gear shifting, which limits the development of tractors; The drive system, because the driving operability of the crawler tractor with the stepless drive system has been improved, the agricultural machinery operator does not need to participate in professional technical training, and only needs simple training to master the driving skills, so it is accepted by the majority of users and has achieved very good results. effect, but after adding the hydraulic system, the complexity and manufacturing cost of the operating system are increased. In daily production and use, crawler tractors are usually attached to agricultural machinery. When agricultural machinery is working in the field, the engine is generally in a state of high throttle, which is close to the rated operating condition of the engine. The speed changes little, and the power and torque of the machine are relatively large. , so easily lead to problems such as high energy consumption, high heat generation, and poor high-temperature stability in the hydraulic system, and even the conventional plowing operation cannot be realized, which seriously limits the application range of crawler tractors and increases energy consumption.

At the same time, because the working principle of the tracked vehicle driving system is similar to that of the two-wheeled agricultural machinery, the transmission usually integrates one or more functions such as steering, differential speed, main deceleration, and braking; but at least the steering function is integrated, Its steering function usually uses the steering rod to operate the jaw clutch and multi-disc brake. The specific realization process is: when the crawler tractor turns to the left, the driver operates the left steering rod to separate the left jaw clutch. Braking with the left output shaft, because the transmission power on the left side of the crawler tractor vehicle is interrupted and braked to stop the rotation, at this time, driven by the power on the right side of the tractor, the implement turns to the left; similarly, it can turn to the right, but This steering mechanism is realized by separating and combining jaw clutches and brakes, which has low steering precision and poor steering controllability.

Contents of the invention

The technical problem to be solved by the present invention is to provide a dual power input and differential steering crawler vehicle transmission to solve the above-mentioned shortcomings in the background technology.

The technical problem solved by the present invention adopts following technical scheme to realize:

Dual power input and differential steering crawler vehicle transmission, including power input mechanism, dual power input mechanism, intermediate transmission mechanism, differential drive mechanism, left crawler drive mechanism, right crawler drive mechanism, PTO power output mechanism and box; Among them, the power input mechanism, double power input mechanism, intermediate transmission mechanism, differential drive mechanism and PTO power output mechanism are all installed on the box body; the left crawler drive mechanism and the right crawler drive mechanism have the same structure and are symmetrically installed on both sides of the box body , the power input mechanism is respectively connected with the PTO power output mechanism and the double power input mechanism. Part of the power input through the power input mechanism is output by the PTO power output mechanism, and the power is transmitted to the external operation part through the PTO power output mechanism, and the other part of the power is It is transmitted to the intermediate transmission mechanism through the double power input mechanism, the intermediate transmission mechanism is connected with the differential drive mechanism, and the power output is driven by the differential drive mechanism to drive the left crawler drive mechanism and the right crawler drive mechanism; the power input mechanism is used to realize high-speed and Low-speed switching, the dual power input mechanism is used for the output of forward gear and reverse gear, and the differential drive mechanism is used to realize steering control; the specific connection structure of each mechanism is as follows:

The power input mechanism is connected with the PTO power output mechanism; one end of the first power input shaft is installed on the input end cover, the other end is installed on the box body, and the input end cover is fastened on the box body; The set is equipped with double sliding shift gears, and a power shift fork is inserted on the PTO double sliding shift gears, and a power input bevel gear is installed at the end of the first power input shaft; The power input first shaft at the upper end of the input bevel gear is fitted with a sleeve, which is used to adjust the gap between the shafts of the power input first shaft and limit the power input bevel gear;

One end of the PTO power transmission shaft is installed on the PTO power outer end cover, and the other end is installed in the PTO power inner end cover, and the PTO power outer end cover and the PTO power inner end cover are respectively fastened and installed on the box; and the PTO power The PTO dual shift gear and the PTO main deceleration driving gear are installed on the transmission shaft;

One end of the PTO output shaft is installed on the output outer end cover, and the other end is installed on the output inner end cover. The output outer end cover and the output inner end The PTO output shaft seals the sealing ring, the PTO main deceleration driven gear is set on the PTO output shaft, and a sleeve is installed on the PTO output shaft on the side of the output outer end cover, which is used to adjust the inter-shaft of the PTO output shaft Clearance and limit the PTO main deceleration driven gear;

The PTO double shift gear meshes with the PTO double shift gear, and the PTO main reduction driving gear meshes with the PTO main reduction driven gear; by moving the power shift fork to slide the PTO double slip shift gear left and right, To realize the high-speed and low-speed switching of the PTO output shaft;

In the left crawler drive mechanism, one end of the left crawler drive shaft is installed in the drive end cover, and the other end is installed with a crawler drive tooth plate, and the drive end cover is fastened on the box; the brake disc is set on the left crawler drive shaft, and Installed on the track drive tooth disc, the brake disc is equipped with a brake shoe on one side, and a brake is installed under the brake shoe; at the same time, the left track drive shaft is also equipped with a support front sleeve, a support middle sleeve, and a support middle sleeve. One end is connected with the support front sleeve, and the other end is connected with the drive end cover;

In the intermediate transmission mechanism, the two ends of the intermediate shaft have the same structure and are respectively installed in the transmission end cover. The transmission end cover is fastened on the box body, and the intermediate shaft transmission gear and the intermediate shaft driven gear are set on the intermediate shaft; the reversing shaft Both ends have the same structure and are respectively installed in the transmission end cover. The transmission end cover is tightly installed on the box body, and the reversing gear is installed on the reversing shaft and meshed with the intermediate shaft transmission gear;

In the dual power input mechanism, the hydrostatic continuously variable transmission is installed on one side of the box body, and the hydrostatic continuously variable transmission power input shaft and the hydrostatic continuously variable transmission power output shaft are arranged on the hydrostatic continuously variable transmission. The power input shaft of the transmission is nested in one end of the second power input shaft, the other end of the second power input shaft is installed in the power end cover, and the power end cover is fastened on the box body; the power output shaft of the hydrostatic continuously variable transmission is fitted with The power output gear of the hydrostatic continuously variable transmission, the mechanical gear driving gear and the driven bevel gear are set on the second shaft of the power input, and are limited by a snap ring. The driven bevel gear and the power set on the first power input shaft The input bevel gear meshes; both ends of the third shaft are respectively installed in the shaft end cover, and the shaft end cover is tightly installed on the box body; the third shaft mechanical gear and the third shaft stepless gear are vacantly sleeved on the upper end of the third shaft In the sliding idle state, the lower end of the third shaft is fitted with the third shaft input gear, and the double power input spline hub is located between the third shaft mechanical gear and the third shaft stepless gear, and is fitted on the third shaft through splines , the combination sleeve is set on the double power input spline hub, and the transmission shift fork is installed on the combination sleeve; in addition, the third shaft continuously variable gear meshes with the power output gear of the hydrostatic continuously variable transmission, and the third shaft mechanical gear Mesh with mechanical gear drive gear;

In the differential drive mechanism, the two ends of the steering shaft are respectively installed in the reversing end cover, and the reversing end cover is fastened on the box, and the differential steering left gear and the reversing idler are set on the steering shaft. , the hydraulic motor is installed on the box between the steering shaft and the sun gear support shaft, one end of the sun gear support shaft is set in the left track drive shaft, and the other end is set in the right track drive shaft, which is used to output power in the form of Drive the left crawler drive mechanism and the right crawler drive mechanism to walk; the outer end surface of the sun gear support shaft is processed with external teeth, and the other teeth are used to play the role of the sun gear of the planetary gear mechanism, and the middle part of the sun gear support shaft is equipped with the main deceleration driven Gears, one side of the main deceleration driven gear is provided with a right planetary gear mechanism, the other side is provided with a left planetary gear mechanism, the motor drive shaft of the hydraulic motor is equipped with a motor gear, and the motor gear meshes with the reversing idler gear.

In the present invention, a sealing ring for sealing the power input first shaft is installed in the input end cover.

In the present invention, a snap ring for limiting the position of the first power input shaft is installed in the input end cover.

In the present invention, a sealing ring for sealing the PTO output shaft is installed in the output outer end cover.

In the present invention, snap rings are respectively installed on both sides of the left crawler drive shaft on which the crawler drive chainring end is installed, and are used to limit the position of the left crawler drive shaft.

In the present invention, a deep groove ball bearing is installed in the supporting front sleeve, and a lip seal ring is arranged above the deep groove ball bearing for sealing the left crawler drive shaft.

In the present invention, a sleeve is arranged between the intermediate shaft transmission gear and the intermediate shaft driven gear.

In the present invention, a sleeve is sleeved on the power input second shaft located below the driven bevel gear.

In the present invention, the mechanical gear of the third shaft and the continuously variable gear of the third shaft respectively slide and idle on the upper end of the third shaft through the sliding bearing sleeve.

In the present invention, a sleeve is sleeved on the intermediate shaft below the reversing idler wheel.

In the present invention, the two ends of the sun gear support shaft are respectively provided with needle bearings, which are used to receive the axial component force when the left crawler drive shaft and the right crawler drive shaft dynamically rotate and transmit power.

In the present invention, in the left planetary gear mechanism, the left planetary gear is sleeved on the left planetary gear support shaft, and is arranged symmetrically in four groups on the circumference along the left planetary gear fixed frame, and the left planetary gear fixed frame passes through the sliding bearing sleeve Installed on the sun gear support shaft, the left planet carrier gear is hooked on the sun gear support shaft and the external teeth of the left crawler drive shaft, and meshes with the motor gear through the reversing idler gear.

In the present invention, in the right planetary gear mechanism, the right planetary gear is sleeved on the right planetary gear support shaft, and is arranged symmetrically in four groups on the circumference along the right planetary gear fixing frame, and the right planetary gear fixing frame passes through the sliding bearing sleeve. Installed on the sun gear support shaft, the right planet carrier gear is hooked on the sun gear support shaft and the outer teeth of the right crawler drive shaft, and meshes with the motor gear.

In the present invention, the internal splines of the main deceleration driven gear are tooth-shaped splines, which are combined with the external teeth on the outer end surface of the sun gear type support shaft to form a pair of splines.

In the present invention, when turning to the left, the differential steering left gear meshes with the left planetary gear, and when turning to the right, the motor gear meshes with the left planetary gear; The sleeve moves up and is fixed on the double power input spline hub and the third shaft continuously variable gear. The power is transmitted from the power output gear of the hydrostatic continuously variable transmission to the third shaft continuously variable gear and then transmitted to the double power input spline hub , and then transmitted to the input gear of the third shaft. At this time, the transmission is hydrostatic continuously variable, and the transmission can output continuously variable forward gear and reverse gear; slide the transmission shift fork downward, and the combination sleeve moves down and is fixed on the double On the power input spline hub and the third shaft mechanical gear, the power is transmitted from the hydrostatic continuously variable transmission power output gear to the third shaft mechanical gear and then to the dual power input spline hub, and then to the third shaft input gear , at this time the transmission is a mechanical gear;

Since one end of the hydraulic motor directly drives the right planetary carrier gear, and the other end drives the left planetary carrier gear after reversing through the reversing idler gear, and the modulus and number of teeth of the motor gear and the differential steering left gear are the same, so when the hydraulic motor drives, The left planetary gear and the right planetary gear rotate at the same speed but in opposite directions to form a planetary gear differential steering mechanism driven by a hydraulic motor;

When the differential steering mechanism of the planetary gear carrier is locked and output at the same speed, the power is transmitted from the main reduction driven gear to the sun gear support shaft, and the left end of the sun gear support shaft reaches the left planetary gear, and is transmitted to the left planetary gear from the left planetary gear. Track drive shaft, the right end of the sun gear support shaft to the right planetary gear, and the right planetary gear is transmitted to the right track drive shaft; when the output is constant, the hydraulic motor does not work, and when the hydraulic motor does not rotate, the differential turns to the left gear and the reversing idler The force of the wheels is equal in size and opposite in direction, the steering shaft is self-locking, the left planetary gear and the right planetary gear are fixed, the left planetary gear rotates on the left planetary gear support shaft, and the right planetary gear rotates on the right planetary gear support shaft. At this time, the left crawler drive shaft and the right crawler drive shaft output at the same speed;

When the differential steering mechanism of the planetary gear carrier differential steering mechanism outputs the differential speed, the hydraulic motor rotates, the input direction of the left planetary carrier gear and the right planetary carrier gear is opposite, and the output power is equal to the rotational speed. This power and the constant speed lock output generate compound motion. , so that the left planetary gear rotates around the left planetary gear support shaft and revolves around the sun gear support shaft, and the right planetary gear both rotates around the right planetary gear support shaft and revolves around the sun gear support shaft, and the two sides revolve in the same direction , which means that the speed of the left track drive shaft on one side increases, while the speed of the right track drive shaft on the other side decreases, thereby realizing steering.

Beneficial effects: the present invention adopts the parallel connection mode of mechanical direct transmission and hydraulic stepless transmission, solves the problem of mechanical direct transmission and hydraulic stepless combination by converting the coupling sleeve, effectively improves the high transmission efficiency and the control performance of tracked vehicles; at the same time, adopts hydraulic The motor controls the positive and negative rotation of the planetary gears of the planetary gear mechanism on both sides of the drive wheel to change the speed at both ends of the driving drive power output shaft, and then realize the steering. This steering structure can realize precise steering by adjusting the speed of the hydraulic motor, and even turn around in the field. Moreover, it is convenient to realize remote electromechanical-hydraulic integrated control, which effectively overcomes the problems of the existing tracked vehicles such as lateral resistance, serious steering mud at the head of the field, and difficult control.

Description of drawings

Fig. 1 is a schematic structural diagram of a preferred embodiment of the present invention.

Fig. 2 is a sectional view at A-A in Fig. 1 .

Fig. 3 is a schematic structural diagram of the power input mechanism and the PTO power output mechanism in a preferred embodiment of the present invention.

Fig. 4 is a sectional view at C-C in Fig. 1 .

Fig. 5 is a schematic structural view of the left crawler drive mechanism in a preferred embodiment of the present invention.

Fig. 6 is a schematic structural diagram of the intermediate transmission mechanism in a preferred embodiment of the present invention.

Fig. 7 is a schematic structural diagram of a dual power input mechanism in a preferred embodiment of the present invention.

Fig. 8 is a cross-sectional view at H-H in Fig. 7 .

Fig. 9 is a sectional view at I-I in Fig. 7 .

Fig. 10 is a sectional view at J-J in Fig. 7 .

Fig. 11 is a sectional view at K-K in Fig. 7 .

Fig. 12 is a schematic structural diagram of a differential drive mechanism in a preferred embodiment of the present invention.

Fig. 13 is a sectional view at U-U in Fig. 12 .

Fig. 14 is a cross-sectional view at V-V in Fig. 12 .

Fig. 15 is a sectional view at W-W in Fig. 12 .

Fig. 16 is a sectional view at Y-Y in Fig. 12 .

Fig. 17 is a sectional view at Z-Z in Fig. 12 .

Fig. 18 is a schematic structural view of the left planetary gear mechanism in a preferred embodiment of the present invention.

Fig. 19 is a schematic structural view of the right planetary gear mechanism in a preferred embodiment of the present invention.

detailed description

In order to make the technical means, creative features, goals and effects achieved by the present invention easy to understand, the present invention will be further described below in conjunction with specific illustrations.

Refer to Figure 1-2 for the dual power input and differential steering crawler vehicle transmission, including power input mechanism P, double power input mechanism S, intermediate transmission mechanism M, differential drive mechanism D, left crawler drive mechanism Q, right The crawler drive mechanism R, the PTO power output mechanism T and the box body X; among them, the power input mechanism P, the double power input mechanism S, the intermediate transmission mechanism M, the differential drive mechanism D and the PTO power output mechanism T are all installed in the box body On X, the left crawler drive mechanism Q and the right crawler drive mechanism R with the same structure are installed symmetrically on both sides of the box X; the power input mechanism P is connected with the PTO power output mechanism T and the double power input mechanism S respectively, For the input power, part of the power is output by the PTO power output mechanism T, and the power is transmitted to the external working part through the PTO power output mechanism T, and the other part of the power is transmitted to the intermediate transmission mechanism M through the double power input mechanism S, and the intermediate transmission mechanism M and the differential The high-speed drive mechanism D is connected, and the power output is driven by the differential drive mechanism D to drive the left crawler drive mechanism Q and the right crawler drive mechanism R; the power input mechanism P is used to realize high-speed and low-speed switching, and the double power input mechanism S is used to move forward Gear, reverse output, differential drive mechanism D is used to achieve steering control.

Referring to Figures 3 to 4, the power input mechanism P includes a power input bevel gear P1, a PTO double shift gear P2, a power input first shaft P3, a power shift fork P4, and a PTO double shift gear P5 , PTO power transmission shaft P6; PTO power output mechanism T includes PTO output shaft T1, PTO main deceleration driven gear T2, PTO main deceleration driving gear T3; input cover G1, snap ring G2, sealing ring G3, thrust bearing G4, Bolt G5, deep groove ball bearing G6, sleeve G7, output outer end cover G11, PTO power outer end cover G17, PTO power inner end cover G18, output inner end cover G19; one end of the power input first shaft P3 passes through the thrust bearing G4 Installed on the input end cover G1, the other end is installed on the box body X through the deep groove ball bearing G6, the input end cover G1 is fastened on the box body X by the bolt G5, and a The sealing ring G3 for sealing the first power input shaft P3 and the snap ring G2 for positioning the thrust bearing G4 in the hole direction; A power shift fork P4 is inserted on the sliding shift gear P2, and a power input bevel gear P1 is installed on one end of the first power input shaft P3, and at the same time, a power input bevel gear P1 located at the upper end of the power input bevel gear P1 A sleeve G7 is set on the first shaft P3, which is used to adjust the gap between the shafts of the first power input shaft P3 and limit the position of the power input bevel gear P1;

One end of the PTO power transmission shaft P6 is installed in the PTO power outer end cover G17 through the deep groove ball bearing G6, and the other end is installed in the PTO power inner end cover G18 through the deep groove ball bearing G6, and the PTO power outer end cover G17 and the PTO power The inner end cover G18 is fastened and installed on the box body X by bolts G5, and is used to limit the position of the deep groove ball bearing G6. The PTO double shift gear P5 is set on one end of the PTO power transmission shaft P6, and the PTO power transmission shaft P6 The other end is equipped with PTO main reduction driving gear T3;

One end of the PTO output shaft T1 is installed on the output outer end cover G11 through the deep groove ball bearing G6, and the other end is installed on the output inner end cover G19 through the deep groove ball bearing G6. The output outer end cover G11 and the output inner end cover G19 are used for The deep groove ball bearing G6 is limited, and it is fastened and installed on the box body X by the bolt G5, and the sealing ring G3 for sealing the PTO output shaft T1 is installed in the output outer end cover G11, and the PTO main deceleration slave The moving gear T2 is set on the PTO output shaft T1, and a sleeve G7 is installed on the PTO output shaft T1 on the side of the output outer end cover G11, which is used to adjust the inter-shaft clearance of the PTO output shaft T1 and adjust the PTO main reduction gear from The moving gear T2 is limited;

The PTO dual sliding shift gear P2 meshes with the PTO dual shift gear P5, and the PTO main deceleration driving gear T3 meshes with the PTO main deceleration driven gear T2.

The PTO double sliding shift gear P2 moves from left to right on the first power input shaft P3 to realize the switching between high gear and low gear, as shown in Figure 4, and the transmission route is illustrated by taking low gear as an example: PTO The right gear of the dual sliding shift gear P2 meshes with the right gear of the PTO dual shift gear P5 → the PTO dual shift gear P5 drives the PTO power transmission shaft P6 to rotate → the PTO power transmission shaft P6 drives the PTO main reduction gear The driving gear T3 rotates to transmit power → the PTO main reduction driving gear T3 meshes with the PTO main reduction driven gear T2 → the PTO main reduction driven gear T2 drives the PTO output shaft T1 to rotate. The shifting fork P4 slides the PTO dual sliding shift gear P2 left and right to realize the high-speed and low-speed switching of the PTO output shaft T1.

As shown in Figure 5, the left crawler drive mechanism Q includes the left crawler drive shaft Q1, the crawler drive chainring Q2, the brake disc Q3, the support front sleeve Q4, the support middle sleeve Q5, the brake Q6, the brake shoe Q7, and the snap ring G2, bolt G5, deep groove ball bearing G6, lip seal ring G8, drive end cover G12; one end of the left crawler drive shaft Q1 is installed in the drive end cover G12 through the deep groove ball bearing G6, and the other end is installed with a crawler drive sprocket Q2, the drive end cover G12 is fastened and installed on the box body X through the bolt G5, and snap rings G2 are respectively installed on both sides of the left crawler drive shaft Q1 where the crawler drive sprocket Q2 end is installed, for aligning the left crawler drive shaft Q1 To limit the position; the brake disc Q3 is set on the left track drive shaft Q1, and is installed on the track drive tooth disc Q2 through the bolt G5, and the brake shoe Q7 is installed on the side of the brake disc Q3, and the bottom of the brake shoe Q7 A brake Q6 is installed; at the same time, a supporting front sleeve Q4 and a supporting middle sleeve Q5 are set on the left crawler drive shaft Q1. One end of the supporting middle sleeve Q5 is connected with the supporting front sleeve Q4, and the other end is connected with the driving end cover G12 to support the front sleeve. A deep groove ball bearing G6 is installed inside Q4, and a lip seal ring G8 is arranged above the deep groove ball bearing G6 to seal the left crawler drive shaft Q1;

The left crawler drive mechanism Q has the same structure as the right crawler drive mechanism R, and is symmetrical about the main reduction driven gear D10.

Referring to Figure 6, the intermediate transmission mechanism M includes the intermediate shaft M1, the intermediate shaft transmission gear M2, the intermediate shaft driven gear M3, the reversing gear M4, the reversing shaft M5, the snap ring G2, the bolt G5, and the deep groove ball bearing G6 , sleeve G7 and transmission end cover G13; both ends of the intermediate shaft M1 and reversing shaft M5 have the same structure, and are respectively installed in the transmission end cover G13 through deep groove ball bearings G6, and the transmission end cover G13 is fastened to the box by bolts G5 Body X, and a sleeve G7 is set on the intermediate shaft M1, the intermediate shaft transmission gear M2 is set on the intermediate shaft M1 above the sleeve G7, and meshes with the reversing gear M4, which is installed on the reversing gear On the shaft M5, the intermediate shaft driven gear M3 is set on the intermediate shaft M1 under the sleeve G7; at the same time, snap rings G2 are respectively installed on the intermediate shaft M1 and the reversing shaft M5 for the reversing gear M4 and the intermediate shaft. The transmission gear M2 is limited; the purpose of adding the reversing shaft M5 is to change the mechanical gear. After the transmission is installed on the engine, the mechanical gear can only make the engine rotate after this reversing, and the tracked vehicle can move forward. The mechanical gear of the tracked vehicle will always be in reverse gear.

Referring to Figures 7 to 11, the dual power input mechanism S includes a hydrostatic continuously variable transmission S1, a power input shaft S2 of the hydrostatic continuously variable transmission, a mechanical gear driving gear S3, a second power input shaft S4, a driven bevel gear S5, Hydrostatic continuously variable transmission power output gear S6, hydrostatic continuously variable transmission power output shaft S7, transmission shift fork S8, coupling sleeve S9, double power input spline hub S10, third shaft S11, third shaft input gear S12 , The third shaft mechanical gear S13, the third shaft continuously variable gear S14, the snap ring G2, the thrust bearing G4, the bolt G5, the deep groove ball bearing G6, the sleeve G7, the sliding bearing sleeve G10, the power end cover G14, the shaft The end cover G15; the hydrostatic continuously variable transmission S1 is installed on the side of the box body X, and the hydrostatic continuously variable transmission S2 and the hydrostatic continuously variable transmission power output shaft S7 are arranged on the hydrostatic continuously variable transmission S1. The power input shaft S2 of the hydraulic continuously variable transmission is nested in one end of the second power input shaft S4, and the other end of the second power input shaft S4 is installed in the power end cover G14 through the thrust bearing G4, and the power end cover G14 is fastened and installed by bolts G5 On the box X; the power output shaft S7 of the hydrostatic continuously variable transmission is fitted with the power output gear S6 of the hydrostatic continuously variable transmission, the driving gear S3 of the mechanical gear and the driven bevel gear S5 are set on the second power input shaft S4, and The position is limited by the snap ring G2, and the sleeve G7 is set on the power input second shaft S4 below the driven bevel gear S5, and the driven bevel gear S5 and the power input bevel gear set on the power input first shaft P3 P1 meshing;

Both ends of the third shaft S11 are respectively installed in the shaft end cover G15 through deep groove ball bearings G6, and the shaft end cover G15 is fastened and installed on the box X through bolts G5; the third shaft mechanical gear S13, the third shaft stepless The gears S14 are in a sliding idle state on the third shaft S11 through the sliding bearing sleeves G10 respectively, and the double power input spline hub S10 is located between the mechanical gear S13 of the third shaft and the continuously variable gear S14 of the third shaft, and Set on the third shaft S11 through the spline, the combination sleeve S9 is set on the double power input spline hub S10, the transmission shift fork S8 is installed on the combination sleeve S9; at the same time, the sleeve G7 is set on the third shaft S11 , one end of the sleeve G7 is connected to the third-axis mechanical gear S13, and the other end is connected to the third-axis input gear S12; in addition, the third-axis continuously variable gear S14 meshes with the power output gear S6 of the hydrostatic continuously variable transmission, and the third Shaft mechanical gear S13 meshes with mechanical gear drive gear S3; slide shift shift fork S8 upwards, and coupling sleeve S9 moves up, and is fixed on double power input spline hub S10 and third shaft continuously variable gear S14, the power is provided by The power output gear S6 of the hydrostatic continuously variable transmission is transmitted to the third shaft continuously variable gear S14 and then transmitted to the double power input spline hub S10, and then transmitted to the third shaft input gear S12. At this time, the transmission is a hydrostatic continuously variable transmission. The transmission can output continuously variable forward gear and reverse gear; slide the transmission shift fork S8 down, and the combination sleeve S9 moves down, and is fixed on the double power input spline hub S10 and the third shaft mechanical gear S13, and the power is provided by The power output gear S6 of the hydrostatic continuously variable transmission is transmitted to the third shaft mechanical gear S13 and then to the double power input spline hub S10, and then transmitted to the third shaft input gear S12. The reverse gear cannot be output when the first-speed forward gear is used. This gear is mainly used for efficient field operations of tracked vehicles; the dual power input focuses on solving the problem of high-efficiency transmission of mechanical gears during field work and the convenience of hydraulic stepless transmission control in other working conditions. question.

In this embodiment, dual power input is adopted, including mechanical gear and hydrostatic stepless gear, and the power transmission route of the two gears is as follows:

The power transmission route of the mechanical gear is: the power input bevel gear P1 on the first power input shaft P3 meshes with the driven bevel gear S5 → the driven bevel gear S5 drives the power input and the second shaft S4 rotates to transmit power → the driving gear S3 of the mechanical gear rotates → The mechanical gear driving gear S3 meshes with the third shaft mechanical gear S13 → the third shaft mechanical gear S13 drives the third shaft S11 to rotate → the third shaft S11 drives the third shaft input gear S12 to rotate → the third shaft input gear S12 turns The power is transmitted to the intermediate transmission mechanism M;

The hydrostatic stepless power transmission route is as follows: the power input bevel gear P1 on the first power input shaft P3 meshes with the driven bevel gear S5 → the driven bevel gear S5 drives the power input second shaft S4 to rotate and transmit power → power from The power input shaft S2 of the hydrostatic continuously variable transmission is transmitted into the continuously variable transmission of the hydrostatic continuously variable transmission S1, and then output from the power output shaft S7 of the hydrostatic continuously variable transmission → the power output shaft S7 of the hydrostatic continuously variable transmission drives the power of the hydrostatic continuously variable transmission The output gear S6 rotates → the power output gear S6 of the hydrostatic continuously variable transmission meshes with the third shaft continuously variable gear S14 → the third shaft continuously variable gear S14 drives the third shaft S11 to rotate → the third shaft S11 drives the third shaft input gear S12 rotates → the third shaft input gear S12 transmits the power to the intermediate transmission mechanism M.

Referring to Figures 12-19, the differential drive mechanism D includes differential steering left gear D1, steering shaft D2, reversing idler gear D3, hydraulic motor D4, motor drive shaft D5, motor gear D6, sun gear support Shaft D7, right planetary gear mechanism D8, left planetary gear mechanism D9, main deceleration driven gear D10, right planetary gear support shaft D81, right planetary gear D82, right planetary carrier gear D83, right planetary gear fixed frame D84, left Planetary gear support shaft D91, left planetary gear D92, left planetary gear D93, left planetary gear fixed frame D94, left track drive shaft Q1, right track drive shaft R1, snap ring G2, thrust bearing G4, bolt G5, deep groove ball Bearing G6, sleeve G7, needle roller bearing G9, sliding bearing sleeve G10, reversing end cover G16; both ends of the steering shaft D2 are respectively installed in the reversing end cover G16 through deep groove ball bearings G6, and the reversing end cover G16 passes through The bolt G5 is fastened on the box X, and the differential steering left gear D1 and the reversing idler gear D3 are set on the steering shaft D2, and the sleeve G7 is set on the steering shaft D2 under the reversing idler D3. The hydraulic motor D4 is installed on the box X between the steering shaft D2 and the sun gear support shaft D7. One end of the sun gear support shaft D7 is set in the left crawler drive shaft Q1 through the deep groove ball bearing G6, and the other end is passed through the deep groove The ball bearing G6 is set in the right crawler drive shaft R1, and is used to output the power to drive the left crawler drive mechanism Q and the right crawler drive mechanism R. It is used to undertake the axial component force when the left crawler drive shaft Q1 and the right crawler drive shaft R1 dynamically rotate and transmit power; the outer end surface of the sun gear support shaft D7 is processed with external teeth, and the other teeth are used for the sun gear of the planetary gear mechanism Function: The middle part of the sun gear support shaft D7 is equipped with the main deceleration driven gear D10, the main deceleration driven gear D10 is equipped with the right planetary gear mechanism D8, the other side is equipped with the left planetary gear mechanism D9, and the hydraulic motor D4 A motor gear D6 is installed on the motor drive shaft D5, and the motor gear D6 meshes with the reversing idler wheel D3;

In the left planetary gear mechanism D9, the left planetary gear D92 is set on the left planetary gear support shaft D91, and is arranged symmetrically in four groups on the circumference along the left planetary gear fixing frame D94. The left planetary gear fixing frame D94 passes through the sliding bearing sleeve G10 is installed on the sun gear support shaft D7, and the left planet carrier gear D93 is hooked on the sun gear support shaft D7 and the external gear of the left crawler drive shaft Q1, and meshes with the motor gear D6 through the reversing idler gear D3; When turning to the left, the differential steering left gear D1 meshes with the left planetary gear D92, and when turning to the right, the motor gear D6 meshes with the left planetary gear D92;

In the right planetary gear mechanism D8, the right planetary gear D82 is set on the right planetary gear support shaft D81, and is arranged symmetrically in four groups on the circumference along the right planetary gear fixing frame D84, and the right planetary gear fixing frame D84 passes through the sliding bearing sleeve G10 is installed on the sun gear support shaft D7, and the right planet carrier gear D83 is hooked on the sun gear support shaft D7 and the outer teeth of the right crawler drive shaft R1, and meshes with the motor gear D6.

In this embodiment, the internal splines of the main deceleration driven gear D10 are toothed splines, which are combined with the external teeth on the outer end surface of the sun gear support shaft D7 to form a pair of splines.

In this embodiment, the left planetary gear mechanism D9 is interconnected with the right planetary gear mechanism D8: since one end of the hydraulic motor D4 directly drives the right planetary gear D83, the other side drives the left planetary carrier after reversing through the reversing idler gear D3 Gear D93, and the motor gear D6 has the same modulus and the same number of teeth as the differential steering left gear D1, so when the hydraulic motor D4 drives, the left planetary carrier gear D93 and the right planetary carrier gear D83 rotate at the same speed, but in opposite directions. Planetary carrier differential steering mechanism driven by hydraulic motor D4; its working principle:

1. Drive (constant velocity lock output):

The power is transmitted from the main reduction driven gear D10 to the sun gear support shaft D7, the left end of the sun gear support shaft D7 is connected to the left planetary gear D92, and then transmitted to the left track drive shaft Q1 by the left planetary gear D92, and the sun gear support shaft D7 From the right end to the right planetary gear D82, the right planetary gear D82 is transmitted to the right crawler drive shaft R1; when the output is constant, the hydraulic motor D4 does not work, and when the hydraulic motor D4 does not rotate, the differential speed turns to the left gear D1 and the reversing idler wheel D3 The force is equal in magnitude and opposite in direction, the steering shaft D2 is self-locking, the left planetary gear D93 and the right planetary gear D83 are fixed, the left planetary gear D92 rotates on the left planetary gear support shaft D91, and the right planetary gear D82 is supported by the right planetary gear The axis D81 rotates on itself, and at this time, the left track drive shaft Q1 and the right track drive shaft R1 output at a constant speed;

2. Differential steering output:

When the hydraulic motor D4 rotates, the input direction of the left planetary gear D93 and the right planetary gear D83 are opposite, and the output power is equal to the rotational speed; at this time, the power and drive (constant speed lock output) produce a compound motion, prompting the left planetary gear D92 It not only rotates around the left planetary gear support shaft D91 but also revolves around the sun gear support shaft D7, and the right planetary gear D82 both rotates around the right planetary gear support shaft D81 and revolves around the sun gear support shaft D7, and its two sides revolve in the same direction , that is, the speed of the left crawler drive shaft Q1 on one side increases, while the speed of the right crawler drive shaft R1 on the other side decreases, thereby realizing steering.

The basic principles and main features of the present invention and the advantages of the present invention have been shown and described above. Those skilled in the industry should understand that the present invention is not limited by the above-mentioned embodiments. What are described in the above-mentioned embodiments and the description only illustrate the principle of the present invention. Without departing from the spirit and scope of the present invention, the present invention will also have Variations and improvements are possible, which fall within the scope of the claimed invention. The protection scope of the present invention is defined by the appended claims and their equivalents.

Claims (10)

1. double dynamical input and differential type turn to endless-track vehicle speed changer, comprise power input mechanism, double dynamical input mechanism, intermediate transmission mechanism, differential speed type driving mechanism, left track driving mechanism, right-hand track chiain driving mechanism, PTO power take-off mechanism and casing; It is characterized in that, power input mechanism, double dynamical input mechanism, intermediate transmission mechanism, differential speed type driving mechanism and PTO power take-off mechanism are installed on casing; Left track driving mechanism, the identical symmetry of right-hand track chiain driving mechanism structure are arranged on casing both sides; The concrete syndeton of each mechanism is as follows:

Power input mechanism is connected with PTO power take-off mechanism; Wherein, power is inputted first axle one end and is arranged on input and covers, and the other end is arranged on casing, and input covers tightly Guan County and is loaded on casing; Power is inputted on the first axle and is set with duplex slippage power shift gear, on PTO duplex slippage power shift gear, is fitted with power shifting shift fork, and inputs the first axle one side end at power power input bevel gear is installed; Input on the first axle and be set with sleeve at the power that is positioned at power input bevel gear upper end simultaneously, input the between centers gap of the first axle and carry out spacing to power input bevel gear for motivation of adjustment;

PTO power transmission shaft one end is arranged on PTO power outer end cap, and the other end is arranged in PTO power internal end cover, and PTO power outer end cap and PTO power internal end cover fastening being installed on casing respectively; And PTO duplex power shift gear and the main deceleration driving gear of PTO be installed on PTO power transmission shaft;

PTO output shaft one end is arranged on output outer end cap, the other end is arranged in output internal end cover, internal end cover is fastening is installed on casing with output for output outer end cap, the main deceleration driven gear of PTO is sleeved on PTO output shaft, and on the PTO output shaft that is positioned at output outer end cap one side, sleeve is installed, for adjusting the between centers gap of PTO output shaft and carrying out spacing to the main deceleration driven gear of PTO;

PTO duplex slippage power shift gear engages with PTO duplex power shift gear, and the main deceleration driving gear of PTO engages with the main deceleration driven gear of PTO

In left track driving mechanism, left track drive axle one end is arranged in Driving terminal, and the other end is provided with track drive fluted disc, and Driving terminal is fastening to be installed on casing; Brake disc is sleeved on left track drive axle, and is arranged on track drive fluted disc, and brake disc one side is provided with shoe brake, and shoe brake below is provided with brake; Cover during while is also set with and supports protheca and support on left track drive axle, overlaps one end and is connected with support protheca in support, the other end is connected with Driving terminal;

In intermediate transmission mechanism, jackshaft two-end structure is identical, is arranged on respectively in transmission end cap, and driving end covers tightly Guan County and is loaded on casing, is set with jackshaft travelling gear and counter shaft driven gear on jackshaft; Reversing shaft two-end structure is identical, is arranged on respectively in transmission end cap, and driving end covers tightly Guan County and is loaded on casing, and tumbler gear is arranged on reversing shaft, and engages with jackshaft travelling gear;

In double dynamical input mechanism, hydrostatic buncher is arranged on casing one side, and on hydrostatic buncher, be provided with hydrostatic buncher power input shaft and hydrostatic buncher power output shaft, hydrostatic buncher power input shaft is nested in power and inputs second axle one end, power is inputted the second axle other end and is arranged in power end cap, and power end covers tightly Guan County and is loaded on casing; On hydrostatic buncher power output shaft, be set with hydrostatic buncher power output gear, machinery gear driving gear and driven wheel of differential are sleeved on power and input on the second axle, and undertaken by snap ring spacing, driven wheel of differential be sleeved on power and input power on the first axle input bevel gear and engage; The 3rd axle two ends are arranged on respectively in hubcap, and hubcap is fastening to be installed on casing; The 3rd shaft mechanical gear gear, the stepless gear gear of the 3rd axle empty set are at the 3rd axle upper end slip idling conditions, the 3rd axle lower end is set with the 3rd axle input gear, double dynamical input splined hub is between the 3rd shaft mechanical gear gear and the stepless gear gear of the 3rd axle, and by spline package on the 3rd axle, combined cover is arranged in double dynamical input splined hub, and gear shift shift fork is arranged on combined cover; In addition, the stepless gear gear of the 3rd axle engages with hydrostatic buncher power output gear, and the 3rd shaft mechanical gear gear engages with machinery gear driving gear;

In differential speed type driving mechanism, steering spindle two ends are arranged on respectively in commutation end cap, commutating, end cap is fastening to be installed on casing, and in steering spindle, be set with differential steering left side gear and reverse idler gear, hydraulic motor is arranged on the casing between steering spindle and the wheeled back shaft of the sun, the wheeled back shaft of sun one end is sleeved in left track drive axle, and the other end is sleeved in right-hand track chiain driving shaft, for outputing power to drive left track driving mechanism and the walking of right-hand track chiain driving mechanism; The wheeled back shaft of sun outer face is processed with external tooth, this external tooth is for playing the sun gear effect of planetary gears, the wheeled back shaft of sun middle part is set with main deceleration driven gear, main deceleration driven gear one side is provided with right side planetary gears, opposite side is provided with left side planetary gears, on the motor drive shaft of hydraulic motor, motor gear is installed, motor gear engages with reverse idler gear.

2. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, in input end cap, are provided with for power being inputted to the sealing ring that the first axle seals.

3. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, in input end cap, are provided with for power being inputted to the first axle and carry out spacing snap ring.

4. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, the left track drive axle both sides that track drive fluted disc end is installed are separately installed with snap ring.

5. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, support in protheca deep groove ball bearing is installed, and deep groove ball bearing top is provided with lip-shaped sealed ring.

6. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, the power that is positioned at driven wheel of differential below is inputted on the second axle and is set with sleeve.

7. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, the wheeled back shaft of sun two ends are respectively arranged with needle bearing.

8. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, in the planetary gears of left side, left lateral star gear set is on left planetary gear back shaft, and on circumference, dividing equally four groups along left planetary gear fixed mount is arranged symmetrically with, left planetary gear fixed mount is arranged on the wheeled back shaft of the sun by sliding bearing sleeve, left planet carrier gear is articulated on the external tooth of the wheeled back shaft of the sun, left track drive axle, and engages with motor gear by reverse idler gear.

9. double dynamical input according to claim 1 and differential type turn to endless-track vehicle speed changer, it is characterized in that, in the planetary gears of right side, right lateral star gear set is on right planetary gear back shaft, and on circumference, dividing equally four groups along right planetary gear fixed mount is arranged symmetrically with, right planetary gear fixed mount is arranged on the wheeled back shaft of the sun by sliding bearing sleeve, and right planet carrier gear is articulated on the external tooth of the wheeled back shaft of the sun, right-hand track chiain driving shaft, and engages with motor gear.

10. turn to endless-track vehicle speed changer according to the double dynamical input described in claim 1～9 any one and differential type, it is characterized in that, in the time turning to the left, differential steering left side gear engages with left planetary gear, in the time turning to the right, motor gear engages with left planetary gear; Simultaneously when upward sliding gear shift shift fork, on combined cover, move, be fixed on double dynamical input splined hub and the stepless gear gear of the 3rd axle, power is passed to the stepless gear gear of the 3rd axle by hydrostatic buncher power output gear and is passed to double dynamical input splined hub again, then be passed to the 3rd axle input gear, now speed changer is hydrostatic stepless gear, the exportable infinite variable speed forward gear of speed changer and reverse gear shift; Down sliding gear shift shift fork, combined cover moves down, be fixed on double dynamical input splined hub and the 3rd shaft mechanical gear gear, power is passed to the 3rd shaft mechanical gear gear by hydrostatic buncher power output gear and is passed to double dynamical input splined hub again, then be passed to the 3rd axle input gear, now speed changer is machinery gear;

Because hydraulic motor one end directly drives right planet carrier gear, the other end is by the reverse idler gear left planet carrier gear of rear drive that commutates, and motor gear is identical with modulus, the number of teeth of differential steering left side gear, therefore in the time of fluid motor-driven, left planet carrier gear, right planet carrier gear rotational speed equate, and opposite direction, to form the pinion frame differential steering system by fluid motor-driven;

In the time that pinion frame differential steering system constant speed locking is exported, power transfers to the wheeled back shaft of the sun by main deceleration driven gear input, the wheeled back shaft left end of the sun is to left planetary gear, transfer to left track drive axle by left planetary gear, the wheeled back shaft right-hand member of the sun is to right planetary gear, and right planetary gear transfers to right-hand track chiain driving shaft; When equispeed output, hydraulic motor is not worked, in the time that hydraulic motor does not rotate, differential port side gear equates with the amount of force of reverse idler gear, opposite direction, steering spindle self-locking, left planet carrier gear, right planet carrier gear are fixed, the rotation on left planetary gear back shaft of left planetary gear, the rotation on right planetary gear back shaft of right planetary gear, now left track drive axle, right-hand track chiain driving shaft equispeed output;

In the time that the differential steering of pinion frame differential steering system is exported, hydraulic motor rotates, left planet carrier gear, the input direction of right planet carrier gear is contrary, the power that output speed is equal, this power and the output of constant speed locking produce compound motion, impel left planetary gear both also to revolve round the sun around the wheeled back shaft of the sun around the rotation of left planetary gear back shaft, right planetary gear both also revolved round the sun around the wheeled back shaft of the sun around the rotation of right planetary gear back shaft, and the direction of its both sides revolution is identical, both made the left track drive axle rotating speed of a side increase, and the rotating speed of opposite side right-hand track chiain driving shaft reduces, and then realization turns to.