CN107859723A - A kind of multi-mode hydraulic machinery stepless speed change device - Google Patents
A kind of multi-mode hydraulic machinery stepless speed change device Download PDFInfo
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- CN107859723A CN107859723A CN201711163954.4A CN201711163954A CN107859723A CN 107859723 A CN107859723 A CN 107859723A CN 201711163954 A CN201711163954 A CN 201711163954A CN 107859723 A CN107859723 A CN 107859723A
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- 239000010720 hydraulic oil Substances 0.000 claims description 18
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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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
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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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
- F16H2047/045—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion the fluid gearing comprising a plurality of pumps or motors
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Abstract
The present invention relates to Vehicle Engineering drive apparatus field, specifically a kind of multi-mode hydraulic machinery stepless speed change device.Including housing and the double planet wheel rows of mixing machinery speed changer and hydraulic transformer that are arranged in parallel in housing, it is additionally provided with housing for controlling the independent speed change output of double planet wheel rows of mixing machinery speed changer, the independent speed change output of control hydraulic transformer or control double planet wheel rows of mixing machinery speed changer and the pattern gear of hydraulic transformer mixing speed change output to switch execution system；It is contemplated that being not only able to realize large-scale stepless speed regulation performance, and it disclosure satisfy that multi-mode demand of the vehicle in different operating mode downward drivings.
Description
Technical Field
The invention relates to the field of vehicle engineering transmission equipment, in particular to a multi-mode hydraulic mechanical stepless speed change device.
Background
The hydraulic transmission has the advantages of convenient arrangement, high power density, no influence of input rotating speed on output torque and rotating speed, easy realization of stepless speed regulation and automatic control and the like, but has the defects of low transmission efficiency and the like, and the defect of low transmission efficiency is more prominent particularly under the high-speed and low-speed transmission working conditions. The gear mechanical transmission has the advantages of accurate and reliable transmission motion, constant instantaneous transmission ratio, compact structure, capability of realizing larger transmission ratio, high transmission power, high transmission efficiency and the like, but automatic speed change is not easy to realize, and stepless speed change can not be realized. When medium and large-sized engineering machinery works, a transmission system is often required to transmit larger power, and high-efficiency speed and torque conversion can be carried out on a power source according to the working condition and the load change. The requirement of medium and large engineering machinery on a transmission system is difficult to perfectly meet by using mechanical transmission or hydraulic transmission singly.
Disclosure of Invention
The invention aims to provide a multi-mode hydraulic mechanical stepless speed change device which not only can realize the stepless speed regulation performance in a large range, but also can meet the multi-mode requirements of vehicles running under different working conditions.
In order to solve the technical problems, the invention adopts the technical scheme that: a multi-mode hydraulic mechanical stepless speed change device comprises a shell, a double-planet-row mechanical speed changer and a hydraulic speed changer which are arranged in the shell in parallel, wherein a mode gear switching execution system for controlling single speed change output of the double-planet-row mechanical speed changer, single speed change output of the hydraulic speed changer or mixed speed change output of the double-planet-row mechanical speed changer and the hydraulic speed changer is also arranged in the shell; the double-planet-row mechanical transmission comprises a front planet row and a rear planet row which are serially connected through the same sun shaft; one end of the sun shaft, which is opposite to the rear planet row, is arranged outside the shell and is used as an input shaft to be in transmission connection with the engine; the front planet row comprises a front sun gear fixedly arranged on the sun shaft, a front gear ring rotatably arranged in the shell, a plurality of front planet gears meshed and connected between the front sun gear and the front gear ring, and a front planet carrier arranged on the plurality of front planet gears, and a first gear is coaxially and fixedly arranged on the front planet carrier; the rear planet row comprises a rear sun gear, a rear gear ring, a plurality of rear planet gears and a rear planet carrier, wherein the rear sun gear is fixedly arranged on the sun shaft, the rear gear ring is rotatably arranged in the shell, the rear planet gears are connected between the rear sun gear and the rear gear ring in a meshed mode, the rear planet carrier is arranged on the plurality of rear planet gears, a second gear is coaxially and fixedly arranged on the rear gear ring, an output shaft with one end penetrating through the outer portion of the shell is coaxially arranged on the rear planet carrier, and a third gear is fixedly arranged on the portion, located in the shell.
Preferably, the hydraulic transmission comprises a variable hydraulic pump and a variable hydraulic motor which are connected through a hydraulic circulation pipeline, a fourth gear is fixedly arranged on an input shaft of the variable hydraulic pump and is in meshed connection with the first gear, and a fifth gear in meshed connection with the second gear and a sixth gear in meshed connection with the third gear are detachably arranged on an output shaft of the variable hydraulic motor.
Preferably, the mode gear shift execution system comprises a first brake arranged on the inner wall of the shell and used for controlling the rotation of the front gear ring, a second brake arranged on the inner wall of the shell and used for controlling the rotation of the rear gear ring, a first clutch arranged between the fifth gear and the output shaft of the variable hydraulic motor, and a second clutch arranged between the sixth gear and the output shaft of the variable hydraulic motor.
Preferably, the multi-mode hydraulic mechanical stepless speed change device further comprises a hydraulic control system for controlling a mode shift switching execution system, a variable hydraulic pump and a variable hydraulic motor, wherein the hydraulic control system comprises a hydraulic oil tank, an oil supplementing pump, an execution hydraulic pump, a brake solenoid valve, a clutch solenoid valve, a first servo variable device for adjusting the output flow of the variable hydraulic pump and a second servo variable device for adjusting the input flow of the variable hydraulic motor; the inlet ends of the oil supplementing pump and the execution hydraulic pump are respectively connected with a hydraulic oil tank, and the outlet end of the oil supplementing pump is connected with a hydraulic circulation pipeline between the variable hydraulic pump and the variable hydraulic motor through an oil supplementing one-way valve and a high-pressure safety valve; the clutch electromagnetic valve, the brake electromagnetic valve, the first servo variable device and the second servo variable device are respectively connected with the outlet end of the execution hydraulic pump, the brake electromagnetic valve is a three-position four-way reversing valve, two of the four-way interfaces of the brake electromagnetic valve are respectively connected with the outlet end of the execution hydraulic pump and a hydraulic oil tank, and the other two interfaces are respectively connected with a first brake executing mechanism for controlling the first brake and a second brake executing mechanism for controlling the second brake through a one-way throttle valve; the clutch electromagnetic valve is a three-position four-way reversing valve with an H-shaped neutral position function, two of four-way interfaces of the clutch electromagnetic valve are respectively connected with the outlet end of the execution hydraulic pump and the hydraulic oil tank, and the other two interfaces are connected with a double-oil-cavity clutch execution mechanism used for controlling the first clutch and the second clutch.
Preferably, a main overflow valve connected to the hydraulic oil tank is provided on a connection line between the brake solenoid valve and an outlet end of the actuating hydraulic pump.
Advantageous effects
When the multi-mode hydraulic mechanical stepless speed change device works, the front planet row and the rear planet row which are connected in series are used as a mechanical transmission path, the variable hydraulic pump and the variable hydraulic motor which are connected in series are used as a hydraulic transmission path, and the transmission conversion under a pure mechanical mode, a hydraulic mechanical hybrid power mode and a pure hydraulic mode is realized through the logic control of each brake and each clutch by the hydraulic control system, so that the speed change range is improved, and the multi-working condition working requirements of long-distance transition operation and the like of large engineering machinery are met to a great extent. The pure mechanical mode has high transmission efficiency and can be used for long-distance high-speed transition driving; the hydraulic mechanical hybrid power mode can realize stepless speed regulation performance on the basis of mechanical transmission, has strong adaptability and is suitable for most working condition requirements; although the transmission efficiency of the pure hydraulic mode is lower than that of the hydraulic mechanical hybrid power mode, the engine can be always operated in a high-efficiency region, the output torque and the rotating speed are not influenced by the input torque and the rotating speed, and the power requirements of the engineering machinery on large load and low speed can be met.
Compared with the existing hydraulic mechanical stepless speed change device with more applications, the multi-mode hydraulic mechanical stepless speed change device has the advantages that the structure is simpler and more compact, the multi-working-condition multi-mode switching control is more flexible on the premise of meeting more modes, the speed switching stability of the working vehicle at different stages is kept, the impact is reduced, and the dynamic property of the vehicle is improved. In addition, a reverse gear device is not needed, under a pure hydraulic mode, a hydraulic element can meet the four-quadrant working requirement of a rotating speed-torque coordinate plane, the forward performance and the backward performance are basically symmetrical, and a pure hydraulic mechanical hybrid transmission device is usually required to be provided with reverse gear in a rear gearbox, so that the reverse gear area self-locking condition possibly occurring in the using process is avoided.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic diagram of a portion of the hydraulic control system of the present invention;
the labels in the figure are: 1. a first brake, 2, a front ring gear, 3, a front planet gear, 4, a variable hydraulic pump, 5, a fourth gear, 6, a sun shaft, 7, a housing, 8, a first gear, 9, a front sun gear, 10, a front carrier, 11, a second brake, 12, a rear planet gear, 13, a rear sun gear, 14, a rear carrier, 15, a second gear, 16, a third gear, 17, an output shaft, 18, a variable hydraulic motor, 19, a fifth gear, 20, a second clutch, 21, a sixth gear, 22, a first clutch, 23, a rear ring gear, 24, a hydraulic oil tank, 25, a make-up oil pump, 26, an execution hydraulic pump, 27, a brake solenoid valve, 28, a clutch solenoid valve, 29, a first servo variable device, 30, a second servo variable device, 31, a make-up check valve, 32, a high-pressure relief valve, 33, a check throttle valve, 34, a first brake actuator, 35. a second brake actuating mechanism 36, a double-oil-chamber clutch actuating mechanism 37 and a main overflow valve.
Detailed Description
As shown in fig. 1 and fig. 2, the multi-mode hydromechanical continuously variable transmission of the present invention includes a housing 7, and a double-planetary-row mechanical transmission and a hydraulic transmission which are arranged in parallel in the housing 7, and a mode shift execution system for controlling single-shift output of the double-planetary-row mechanical transmission, single-shift output of the hydraulic transmission, or mixed-shift output of the double-planetary-row mechanical transmission and the hydraulic transmission is further arranged in the housing 7.
The double-planet-row mechanical transmission comprises a front planet row and a rear planet row which are serially connected through the same sun shaft 6; one end of the sun shaft 6, which is opposite to the rear planet row, is arranged outside the shell 7 and is used as an input shaft to be in transmission connection with the engine; the front planet row comprises a front sun gear 9 fixedly arranged on a sun shaft 6, a front gear ring 2 rotatably arranged in a shell 7, a plurality of front planet gears 3 meshed and connected between the front sun gear 9 and the front gear ring 2, and a front planet carrier 10 arranged on the front planet gears 3, and a first gear 8 is coaxially and fixedly arranged on the front planet carrier 10; the rear planet row comprises a rear sun gear 13 fixedly arranged on the sun shaft 6, a rear gear ring 23 rotatably arranged in the shell 7, a plurality of rear planet gears 12 connected between the rear sun gear 13 and the rear gear ring 23 in a meshing way, and a rear planet carrier 14 arranged on the plurality of rear planet gears 12, wherein a second gear 15 is coaxially and fixedly arranged on the rear gear ring 23, an output shaft 17 with one end penetrating through the outside of the shell 7 is coaxially arranged on the rear planet carrier 14, and a third gear 16 is fixedly arranged on the output shaft 17 at the part positioned in the shell 7.
The hydraulic speed changer comprises a variable hydraulic pump 4 and a variable hydraulic motor 18 which are connected through a hydraulic circulation pipeline, wherein a fourth gear 5 is fixedly arranged on an input shaft of the variable hydraulic pump 4, the fourth gear 5 is meshed with the first gear 8, and a fifth gear 19 meshed with the second gear 15 and a sixth gear 21 meshed with the third gear 16 are arranged on an output shaft 17 of the variable hydraulic motor 18 in a clutchable manner.
The mode gear shift execution system includes a first brake 1 provided on an inner wall of the housing 7 for controlling rotation of the front ring gear 2, a second brake 11 provided on an inner wall of the housing 7 for controlling rotation of the rear ring gear 23, a first clutch 22 provided between the fifth gear 19 and the output shaft 17 of the variable hydraulic motor 18, and a second clutch 20 provided between the sixth gear 21 and the output shaft 17 of the variable hydraulic motor 18.
The multi-mode hydraulic mechanical stepless speed change device also comprises a hydraulic control system used for controlling a mode gear shifting execution system, the variable hydraulic pump 4 and the variable hydraulic motor 18, wherein the hydraulic control system comprises a hydraulic oil tank 24, an oil supplementing pump 25, an execution hydraulic pump 26, a brake solenoid valve 27, a clutch solenoid valve 28, a first servo variable device 29 used for adjusting the output flow of the variable hydraulic pump 4 and a second servo variable device 30 used for adjusting the input flow of the variable hydraulic motor 18; the inlet ends of the oil replenishing pump 25 and the execution hydraulic pump 26 are respectively connected with the hydraulic oil tank 24, and the outlet end of the oil replenishing pump 25 is connected with a hydraulic circulation pipeline between the variable hydraulic pump 4 and the variable hydraulic motor 18 through an oil replenishing one-way valve 31 and a high-pressure safety valve 32; the clutch solenoid valve 28, the brake solenoid valve 27, the first servo variable device 29, and the second servo variable device 30 are connected to an outlet end of the actuator hydraulic pump 26, respectively, and a main relief valve 37 connected to the hydraulic oil tank 24 is provided on a connection line between the brake solenoid valve and the outlet end of the actuator hydraulic pump 26. The brake electromagnetic valves 27 are three-position four-way reversing valves, two of the four-way interfaces of the brake electromagnetic valves 27 are respectively connected with the outlet end of the execution hydraulic pump 26 and the hydraulic oil tank 24, and the other two interfaces are respectively connected with a first brake actuating mechanism 34 for controlling the first brake 1 and a second brake actuating mechanism 35 for controlling the second brake 11 through a one-way throttle valve 33; the clutch solenoid valve 28 is a three-position four-way reversing valve with an H-shaped middle position function, two of the four-way interfaces of the clutch solenoid valve 28 are respectively connected with the outlet end of the execution hydraulic pump 26 and the hydraulic oil tank 24, and the other two interfaces are respectively connected with a double-oil chamber clutch execution mechanism 36 for controlling the first clutch 22 and the second clutch 20.
The invention discloses a hydraulic rotary speed-adjustable planetary speed reducer, wherein the rotary speed input from a sun shaft 6 is divided into two paths at a front planetary row, one path is a hydraulic path, the rotary speed is transmitted to a rear planetary row through the displacement adjustment of a variable hydraulic pump 4 and a variable hydraulic motor 18, the other path is a mechanical path, the input rotary speed is directly transmitted to a rear sun gear 13 of the rear planetary row, and then the rotary speed is transmitted to a rear planet carrier 14 of the rear planetary row, namely, an output shaft 17 is connected with the rear planet carrier 14, so that the final output rotary speed is obtained.
The multi-mode control logic of the hydraulic mechanical stepless speed change device is as follows:
| mode (M) | First brake | Second brake | First clutch | Second clutch |
| Purely mechanical mode | × | ● | × | × |
| Hybrid mode | ● | × | ● | × |
| Pure hydraulic mode | ● | × | × | ● |
"●" indicates functioning; "×" indicates no effect
The characteristic parameters of the front planet row are set asThe characteristic parameter of the rear planet row isThen the front planet row satisfies the characteristic equationThe rear planet row satisfies the characteristic equation。
Wherein,the rotating speeds of the front sun gear 9, the front gear ring 2 and the front planet carrier 10 are respectively;respectively a rear sun gear 13, a rear gear ring 23 and a rear rowThe rotational speed of the planet carrier 14.
A first brake 1 is arranged between the front gear ring 2 of the front planetary row and the shell 7, a second brake 11 is arranged between the rear gear ring 23 of the rear planetary row and the shell 7, and the switching between the modes of the hydraulic mechanical stepless speed change device is realized by adjusting the opening and closing of the first brake 1 and the second brake 11.
A high-speed fifth gear 19, a low-speed sixth gear 21, and a first clutch 22 and a second clutch 20 for fixedly connecting the high-speed fifth gear 19 and the low-speed sixth gear 21 to the rotor shaft of the variable hydraulic motor 18, respectively, are attached to the rotor shaft of the variable hydraulic motor 18, and the high-speed fifth gear 19 and the second gear 15 or the low-speed sixth gear 21 are drivingly connected to the third gear 16 by controlling the opening and closing of the first clutch 22 and the second clutch 20.
The first brake 1 is not locked, the front gear ring 2 is separated from the shell 7, all components of the front planetary row are in a free state, at the moment, the variable hydraulic pump 4 has no rotating speed input, the hydraulic circuit has no power transmission, and the engine power is transmitted to the rear sun gear 13 of the rear planetary row through the front planetary row; the second brake 11 is locked, the rear gear ring 23 is fixed on the shell 7, the rear planet row is in a single-input single-output state, the clutch electromagnetic valve 28 is switched off, the oil pressure of the left cavity and the oil pressure of the right cavity of the double-oil cavity clutch actuating mechanism 36 are equal, the piston rod is restored to a middle position state under the action of the spring, the first clutch 22 and the second clutch 20 do not work at the moment, power is directly transmitted to the rear planet carrier 14 from the rear sun gear 13 to be output, and the speed change device is in a pure mechanical transmission working condition at the moment.
The first brake 1 is locked, the front gear ring 2 is fixed on the shell 7, the front planet row is in a single-input and single-output state, the power of the engine realizes moment division at the front planet row, one path is transmitted through a hydraulic path, and the other path is transmitted through a mechanical path; the second brake 11 is not locked, the first clutch 22 is engaged, the rear planetary gear is in a two-input single-output state, the power of a hydraulic circuit is transmitted to the rear planetary gear through the high-speed fifth gear 19, power confluence is realized at the rear planetary gear, the final power is output to rotate speed through the rear planetary carrier 14, at the moment, the speed changing device is in a mechanical and hydraulic hybrid power transmission mode, the displacement of the variable hydraulic pump 4 and the variable hydraulic motor 18 in the hydraulic road roller is adjusted, the output speed of the hydraulic transmission branch is changed, the rotating speed of the output shaft 17 of the device is controlled, and hybrid transmission can be divided into two working conditions of acceleration and deceleration.
The first brake 1 is locked, the front gear ring 2 is fixed on the shell 7, the front planet row is in a single-input and single-output state, the power of the engine is divided into moments at the front planet row, one path is transmitted through a hydraulic path, and the other path is transmitted to the rear planet row through a mechanical path; the second brake 11 is not locked, the second clutch 20 is engaged, the rear ring gear 23 is in a free state, and the transmission of the mechanical path power at the rear planetary gear set is interrupted, and the hydraulic path power is transmitted to the third gear 16 via the low-speed sixth gear 21, and finally the rotation speed is output from the output shaft 17. At the moment, the speed change device is in a pure hydraulic stepless transmission mode, the displacement of the variable hydraulic pump 4 and the variable hydraulic motor 18 in the hydraulic transmission branch is adjusted, and the magnitude and the direction of the output rotating speed of the hydraulic circuit are changed, so that the stepless speed regulation control of the forward or backward movement of the output shaft 17 of the device is realized.
In purely mechanical mode, the overall gear ratio of the transmissionOutput rotational speed for the deviceAnd input rotational speedIn a ratio ofIn this mode, the first and second electrodes are, in this mode,according to the characteristic equation of the rear planet rowThus, the overall gear ratio of the transmission is:. In the working process of the vehicle, when the pure mechanical transmission can meet the operation requirement, the pure mechanical transmission working condition is used as much as possible to obtain higher transmission efficiency and vehicle speed.
Under the mechanical hydraulic hybrid power mode, the function of stepless speed regulation can be realized by regulating the displacement of the variable hydraulic pump 4 and the variable hydraulic motor 18 in the hydraulic road roller on the basis of pure mechanical transmission. The ratio of the rotation speed of the first gear 8 to the rotation speed of the fourth gear 5 is set asThe ratio of the rotational speed of the fifth gear 19 to the rotational speed of the second gear 15 isThe ratio of the rotation speeds of the variable displacement hydraulic pump 4 and the variable displacement hydraulic motor 18 isUnder the working condition, the air conditioner can be used,the characteristic equation of the front planet row can be obtained: the rotation speed of the front carrier 10, the rotation speed of the variable hydraulic motor 18, and the rotation speed of the second gear 15 areAccording to the characteristic equation of the front planet row, the following can be obtained:bringing the above conditions into availability: total gear ratio of transmission:. The mode can meet the power requirement of the engineering machinery during high-speed transition operationAnd (4) demand.
In a pure hydraulic transmission mode, the variable hydraulic pump 4 and the variable hydraulic motor 18 are in a series working relationship, all power of the engine is transmitted through a hydraulic road, and at the moment, the transmission ratio of the whole system is realized only through the displacement regulation of the variable hydraulic pump 4 and the variable hydraulic motor 18. The rotation speed ratio of the sixth gear 21 to the third gear 16 is set toThe total gear ratio of the transmission, without counting hydraulic circuit pressure and leakage losses:. The mode can meet the requirements of low-speed and high-torque working conditions of the engineering machinery and reverse gear running.
The hydraulic control system adopted by the multi-mode hydraulic mechanical stepless speed change device mainly controls the variable hydraulic pump 4, the variable hydraulic motor 18, the first brake 1, the second brake 11, the second clutch 20 and the first clutch 22. The hydraulic control loop of the variable hydraulic pump 4 and the variable hydraulic motor 18 consists of two electro-proportional valves, two swash plate actuating hydraulic cylinders, two high-pressure safety valves 32, two oil-supplementing one-way valves 31, a flushing valve, a flushing overflow valve and a cooling device; the hydraulic control mechanism of the first brake 1 and the second brake 11 is composed of one brake solenoid valve 27, two one-way throttle valves 33, a first brake actuator 34, and a second brake actuator 35.
The control of the displacement of the variable displacement hydraulic pump 4 and the variable displacement hydraulic motor 18 is realized by an electro proportional valve, and the control signals are respectively input to the proportional valve, so that the position of a piston rod of a swash plate execution hydraulic cylinder of the variable displacement hydraulic pump 4 and the position of a piston rod of a swash plate execution hydraulic cylinder of the variable displacement hydraulic motor 18 are controlled, the displacement control of the variable displacement hydraulic pump 4 and the variable displacement hydraulic motor 18 is realized, and the required transmission ratio is obtained.
The control of the first clutch 22 and the second clutch 20 is realized by a three-position four-way electromagnetic directional valve with an H-shaped middle position function, and the control signal is input to the clutch electromagnetic valve 28, so that the flow direction of hydraulic oil flowing into the double-oil chamber clutch actuating mechanism 36 is changed, the position of a piston rod of the double-oil chamber clutch actuating mechanism 36 is further changed, and finally the piston rod drives the clutches to realize the engagement and the disengagement of the first clutch 22 and the second clutch 20 with the high-speed fifth gear 19 and the low-speed sixth gear 21 respectively. The specific implementation is as follows: in a hydraulic mechanical hybrid power mode, under the action of an electric signal, a valve core of a clutch electromagnetic valve 28 moves leftwards, at the moment, oil enters a left cavity of a hydraulic cylinder of a double-oil-cavity clutch actuating mechanism 36, the pressure is increased, oil exits from a right cavity, and the pressure is reduced, so that a piston rod moves rightwards by overcoming the resistance of a spring to drive a second clutch 20 to be engaged with a sixth gear 21 at a low speed, and a first clutch 22 is separated from a fifth gear 19 at a high speed, so that the power transmission in the hybrid power mode is realized; in a pure hydraulic mode, under the action of an electric signal, the clutch electromagnetic valve 28 moves to the right, at the moment, oil is fed into the right cavity of the hydraulic cylinder of the double-oil-cavity clutch actuating mechanism 36, the pressure is increased, oil is discharged from the left cavity, and the pressure is reduced, so that the piston rod overcomes the spring resistance and moves to the left to drive the first clutch 22 to be connected with the high-speed fifth gear 19, and the second clutch 20 is separated from the low-speed sixth gear 21, so that the power transmission in the pure hydraulic mode is realized; in the pure mechanical mode, no current flows, and the piston rod of the hydraulic cylinder of the dual chamber clutch actuator 36 returns to the neutral position by the spring force, so that the first clutch 22 is not engaged with the high-speed fifth gear 19 and the second clutch 20 is not engaged with the low-speed sixth gear 21, thereby achieving power transmission in the pure mechanical mode.
The control of the first brake 1 and the second brake 11 is realized by a common three-position four-way electromagnetic directional valve and a one-way throttle valve 33, and by inputting control signals to the brake electromagnetic valve 27, the flow direction of hydraulic oil flowing into the first brake actuator 34 and the second brake actuator 35 is changed, the positions of piston rods of the first brake actuator 34 and the second brake actuator 35 are changed, and finally the piston rods drive the brakes to realize the locking and unlocking of the front gear ring 2 and the rear gear ring 23 with the shell 7. The specific implementation is as follows: in a pure mechanical mode, under the action of an electric signal, a valve core of the brake electromagnetic valve 27 moves to the right, high-pressure oil flows into an oil cavity of the second brake executing mechanism 35 through the one-way throttle valve 33 corresponding to the rear gear ring 23, the pressure of the oil cavity rises, a piston rod is pushed to stretch out of the oil cylinder by overcoming the resistance of a spring, the second brake 11 is driven to implement locking braking on the rear gear ring 23, meanwhile, the high-pressure oil in the oil cavity of the first brake executing mechanism 34 flows back to the oil tank, the pressure is reduced, the piston rod retracts to the oil cylinder under the action of the elastic force of the spring, and therefore the first. In a hydraulic mechanical hybrid power mode, under the action of an electric signal, a valve core of a brake electromagnetic valve 27 moves leftwards, high-pressure oil flows into an oil cavity of a first brake executing mechanism 34 through a one-way throttle valve 33 corresponding to a front gear ring 2, the pressure of the oil cavity rises, a piston rod is pushed to stretch out of an oil cylinder by overcoming the resistance of a spring to drive a first brake 1 to implement locking braking on the front gear ring 2, meanwhile, high-pressure oil in the oil cavity of a second brake executing mechanism 35 flows back to an oil tank, the pressure is reduced, the piston rod retracts to the oil cylinder under the action of the spring elasticity, and therefore the second brake 11 implements unlocking action on. In the pure hydraulic mode, the operation of the first brake 1 and the second brake 11 is the same as that in the hydromechanical hybrid mode, and will not be described in detail herein.
Claims (5)
1. A multi-mode hydraulic mechanical stepless speed change device is characterized in that: the dual-planetary-row mechanical transmission and hydraulic transmission device comprises a shell (7), and a dual-planetary-row mechanical transmission and a hydraulic transmission which are arranged in the shell (7) in parallel, wherein a mode gear switching execution system for controlling single speed change output of the dual-planetary-row mechanical transmission, single speed change output of the hydraulic transmission or mixed speed change output of the dual-planetary-row mechanical transmission and the hydraulic transmission is also arranged in the shell (7); the double-planet-row mechanical transmission comprises a front planet row and a rear planet row which are serially connected through the same sun shaft (6); one end of the sun shaft (6), which is opposite to the rear planet row, is arranged outside the shell (7) and is used as an input shaft to be in transmission connection with the engine; the front planet row comprises a front sun gear (9) fixedly arranged on the sun shaft (6), a front gear ring (2) rotatably arranged in the shell (7), a plurality of front planet gears (3) connected between the front sun gear (9) and the front gear ring (2) in a meshing manner, and a front planet carrier (10) arranged on the front planet gears (3), wherein a first gear (8) is coaxially and fixedly arranged on the front planet carrier (10); the rear planet row comprises a rear sun gear (13) fixedly arranged on the sun shaft (6), a rear gear ring (23) rotatably arranged in the shell (7), a plurality of rear planet gears (12) connected between the rear sun gear (13) and the rear gear ring (23) in a meshed mode, and a rear planet carrier (14) arranged on the plurality of rear planet gears (12), wherein a second gear (15) is coaxially and fixedly arranged on the rear gear ring (23), an output shaft (17) with one end penetrating through the outer portion of the shell (7) is coaxially arranged on the rear planet carrier (14), and a third gear (16) is fixedly arranged on the portion, positioned in the shell (7), of the output shaft (17).
2. The multi-mode hydromechanical continuously variable transmission of claim 1, wherein: the hydraulic speed changer comprises a variable hydraulic pump (4) and a variable hydraulic motor (18) which are connected through a hydraulic circulation pipeline, wherein a fourth gear (5) is fixedly arranged on an input shaft of the variable hydraulic pump (4), the fourth gear (5) is meshed with a first gear (8), and a fifth gear (19) meshed with a second gear (15) and a sixth gear (21) meshed with a third gear (16) are arranged on an output shaft (17) of the variable hydraulic motor (18) in a clutching mode.
3. The multi-mode hydromechanical continuously variable transmission of claim 2, wherein: the mode gear shifting execution system comprises a first brake (1) arranged on the inner wall of a shell (7) and used for controlling the rotation of a front gear ring (2), a second brake (11) arranged on the inner wall of the shell (7) and used for controlling the rotation of a rear gear ring (23), a first clutch (22) arranged between a fifth gear (19) and an output shaft (17) of a variable hydraulic motor (18), and a second clutch (20) arranged between a sixth gear (21) and the output shaft (17) of the variable hydraulic motor (18).
4. A multi-mode hydromechanical continuously variable transmission as claimed in claim 3, wherein: the multi-mode hydraulic mechanical stepless speed change device also comprises a hydraulic control system used for controlling a mode gear shift execution system, a variable hydraulic pump (4) and a variable hydraulic motor (18), wherein the hydraulic control system comprises a hydraulic oil tank (24), an oil supplementing pump (25), an execution hydraulic pump (26), a brake electromagnetic valve (27), a clutch electromagnetic valve (28), a first servo variable device (29) used for adjusting the output flow of the variable hydraulic pump (4) and a second servo variable device (30) used for adjusting the input flow of the variable hydraulic motor (18); the inlet ends of an oil supplementing pump (25) and an execution hydraulic pump (26) are respectively connected with a hydraulic oil tank (24), and the outlet end of the oil supplementing pump (25) is connected with a hydraulic circulation pipeline between a variable hydraulic pump (4) and a variable hydraulic motor (18) through an oil supplementing one-way valve (31) and a high-pressure safety valve (32); the clutch electromagnetic valve (28), the brake electromagnetic valve (27), the first servo variable device (29) and the second servo variable device (30) are respectively connected with the outlet end of the execution hydraulic pump (26), the brake electromagnetic valve (27) is a three-position four-way reversing valve, two of four-way interfaces of the brake electromagnetic valve (27) are respectively connected with the outlet end of the execution hydraulic pump (26) and the hydraulic oil tank (24), and the other two interfaces are respectively connected with a first brake actuating mechanism (34) used for controlling the first brake (1) and a second brake actuating mechanism (35) used for controlling the second brake (11) through a one-way throttle valve (33); the clutch electromagnetic valve (28) is a three-position four-way reversing valve with an H-shaped middle position function, two of four-way interfaces of the clutch electromagnetic valve (28) are respectively connected with the outlet end of the execution hydraulic pump (26) and the hydraulic oil tank (24), and the other two interfaces are respectively connected with a double-oil-chamber clutch execution mechanism (36) used for controlling the first clutch (22) and the second clutch (20).
5. The multi-mode hydromechanical continuously variable transmission of claim 4, wherein: and a main overflow valve (37) connected with a hydraulic oil tank (24) is arranged on a connecting pipeline between the brake electromagnetic valve and the outlet end of the execution hydraulic pump (26).
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| CN201711163954.4A CN107859723B (en) | 2017-11-21 | 2017-11-21 | A kind of multi-mode hydraulic machinery stepless speed change device |
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| CN201711163954.4A CN107859723B (en) | 2017-11-21 | 2017-11-21 | A kind of multi-mode hydraulic machinery stepless speed change device |
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| CN107859723B CN107859723B (en) | 2019-05-21 |
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| CN201711163954.4A Expired - Fee Related CN107859723B (en) | 2017-11-21 | 2017-11-21 | A kind of multi-mode hydraulic machinery stepless speed change device |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113099835A (en) * | 2021-05-19 | 2021-07-13 | 山东巨明机械有限公司 | Non-row self-propelled corn harvester |
| CN115013525A (en) * | 2022-05-31 | 2022-09-06 | 合肥工业大学 | Control method for transmission mode switching of double-flow transmission speed change system |
| US20220373072A1 (en) * | 2020-07-20 | 2022-11-24 | Jiangsu University | Power split and power convergence combined hydro-mechanical hybrid transmission device |
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| CN105090427A (en) * | 2015-09-09 | 2015-11-25 | 长安大学 | Mechanical-hydraulic hybrid stepless speed change device with secondary elements |
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| CN2221124Y (en) * | 1995-03-10 | 1996-02-28 | 王宪平 | Tandem planetary gear differential sped reducer |
| RU2307758C1 (en) * | 2006-07-24 | 2007-10-10 | Государственное образовательное учреждение высшего профессионального образования "Южно-Уральский государственный университет" | Transmission of high-speed crawler vehicle |
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| US20220373072A1 (en) * | 2020-07-20 | 2022-11-24 | Jiangsu University | Power split and power convergence combined hydro-mechanical hybrid transmission device |
| US11614151B2 (en) * | 2020-07-20 | 2023-03-28 | Jiangsu University | Power split and power convergence combined hydro-mechanical hybrid transmission device |
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| CN115013525A (en) * | 2022-05-31 | 2022-09-06 | 合肥工业大学 | Control method for transmission mode switching of double-flow transmission speed change system |
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| CN107859723B (en) | 2019-05-21 |
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