CN111692300B - Mechanical hydraulic composite transmission device suitable for heavy vehicle - Google Patents

Mechanical hydraulic composite transmission device suitable for heavy vehicle Download PDF

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Publication number
CN111692300B
CN111692300B CN202010220333.0A CN202010220333A CN111692300B CN 111692300 B CN111692300 B CN 111692300B CN 202010220333 A CN202010220333 A CN 202010220333A CN 111692300 B CN111692300 B CN 111692300B
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row
planet
gear
clutch
planetary row
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CN111692300A (en
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马晓枫
王超凡
郭致远
刘春林
李剑峰
葛立坤
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China North Vehicle Research Institute
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China North Vehicle Research Institute
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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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0095—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising four reverse speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Abstract

The invention discloses a mechanical hydraulic composite transmission device suitable for a heavy vehicle, belongs to the technical field of vehicle transmission, and enhances the starting, traction and acceleration performances of the vehicle so that the vehicle has good dynamic property. The device comprises a forward clutch (6), a reverse clutch (7), a pump motor (2) and a first planet row (3); a second planetary row (4), a third planetary row (5); brake Z1(22), brake Z2(29), clutch L1(30) and clutch L2 (31). The invention can realize the stepless speed change of the vehicle, realize the amplification effect of the output power on the hydraulic power through the action of the planetary coupling mechanism, and reduce the power requirement on the hydraulic element, thereby selecting the hydraulic element with smaller specification and realizing larger transmission power. The simple diagram can be directly applied to a transmission system of a wheeled vehicle, and can be applied to the field of tracked vehicles after the supplementary steering flow.

Description

Mechanical hydraulic composite transmission device suitable for heavy vehicle
Technical Field
The invention relates to the technical field of vehicle transmission, in particular to a mechanical hydraulic composite transmission device suitable for a heavy vehicle, and particularly suitable for a transmission system of the heavy vehicle.
Background
The mechanical hydraulic compound transmission can be understood as a transmission system which connects a machine and a hydraulic device in parallel and respectively transmits power flow, the power flow input into the transmission system by an engine is firstly divided into two paths, one path is the power flow (which can be regulated steplessly) transmitted by the hydraulic system, the other path is the power flow (which is transmitted in a pure mechanical mode) and then is converged by a set of planetary differential mechanism.
Compared with the traditional mechanical transmission, the mechanical hydraulic transmission device can realize stepless speed change by changing the discharge capacity of the hydraulic pump, has ideal power characteristics, and reduces the power loss and gear shifting impact of an engine; the average running speed of the vehicle is improved, and the maneuvering performance is enhanced; the fuel consumption of the engine is reduced, so that the engine can work under the optimal working condition; the hydraulic element has the functions of vibration reduction and buffering, and the transmission is stable. In the 80 s of the 20 th century, in the process of developing novel armored vehicles in the United states, a great deal of comparative tests were carried out on an HMPT500 type mechanical hydraulic composite transmission device and a hydraulic mechanical transmission device which are developed in the 60 s of the 20 th century by GE company, and evaluation results show that the HMPT500 type mechanical hydraulic composite transmission device has the characteristics of simple structure, small volume, light weight and high specific power, and is beyond the capability of the HMPT500 type mechanical hydraulic composite transmission device in the aspects of stepless speed change, stepless steering, power braking and the like. In this project, therefore, hydromechanical transmissions were abandoned, and instead, the GE HMPT500 model hydrostatic transmission was used. After that, the HMPT series are continuously improved, HMPT600, HMPT800, HMPT1000 and the like appear, the input power of the HMPT600 is 450kW, and the HMPT is suitable for 33t armored vehicles; the input power of the HMPT800 is 597kW, and the HMPT is suitable for 30-40 t armored vehicles; the HMPT1000 is an advanced and low-profile stepless speed change device, an advanced electric control system is adopted, accurate matching of the rotating speed of an engine and a transmission speed ratio can be provided, so that the optimal fuel efficiency is obtained, the input power of the transmission device is 745kW, the power density is up to 1050kW/m3, the vehicle can be accelerated more quickly, the maneuverability is higher, the steering performance is better, the maintenance is easier, and the HMPT is suitable for 30-40 t armored vehicles. The input power of HMPT1500 developed in recent years is up to 1120kW, and the HMPT is suitable for 30-40 t armored vehicles.
An HMT comprehensive transmission case is developed in Japan for a long time, and an HMT related hydraulic mechanical comprehensive transmission device is developed in 1982 by Xiaosong manufacturers, and belongs to a speed change and steering integrated type, namely the speed change and steering cannot be separated in function. Bench tests were completed in 1989, and actual road use tests were conducted in 1990. The engine power used by the self-propelled low recoil gun is 478-552 kW, and the self-propelled low recoil gun is used for the self-propelled low recoil gun in Japan. According to data introduction, a ten-type main battle tank developed successfully in Japan in 2009 adopts a 4-stroke 8-cylinder water-cooled turbocharged diesel engine with the power of 882 kilowatts. The maximum speed of the vehicle is about 70km/h, the newly developed transmission is a hydro-mechanical continuously variable transmission (HMT) with 3 gears, the transmission actually transmits higher power to the driving wheel by adopting a combination mode of a hydraulic element and a planetary gear, and important guarantee is provided for the miniaturization of a power unit and the miniaturization and light weight of the vehicle. Compared with hydraulic mechanical transmission, the transmission has less power loss, can automatically change speed, can convert forward and backward modes through a hydraulic element, and can reach the highest forward and backward speeds of 70 km/h. As can be seen from a comparison of Japanese 10-type tank transmission with other old equipment in Table 4, the steering performance of a 10-type tank is optimized.
The comfort of the weapon system operator is also an important element in increasing the generation of combat power, preventing premature fatigue of the driver by reducing the operational burden, increasing the level of driving automation, etc. has already been mentioned to an increasingly important place.
The mechanical hydraulic transmission system has the advantages that: the stepless speed change can be continuously and stably carried out in the working conditions of forward and backward running, and the performance is close to the ideal output characteristic; parts of a transmission system are greatly reduced, so that the arrangement is convenient, the ground clearance of the vehicle can be increased, and the vehicle trafficability can be improved; dynamic braking can be carried out by a method of increasing the resistance of the liquid circulation; the working condition of the engine can be automatically adjusted to keep the working condition at the optimum condition; the speed change is controlled by an operating valve, and the operation is convenient.
Disclosure of Invention
The invention solves the technical problem of providing a mechanical hydraulic composite transmission device suitable for heavy vehicles, which is characterized in that the stepless speed regulation characteristic of a hydraulic element is introduced, the high-efficiency characteristic of mechanical transmission is coupled, the mode conversion of the hydraulic element is adopted, the speed change range of a transmission system is expanded, the starting, traction and acceleration performances of the vehicle are enhanced, and the vehicle has good dynamic property. Meanwhile, the working state of the engine is optimized, and the fuel economy of the vehicle is improved. Another technical problem solved by the present invention is that the transmission (simplified) can greatly reduce the power demand of the transmission system on the hydraulic pump motor, thereby reducing the model specification of the pump motor, and can realize the stepless output characteristic of the vehicle through the coupling of mechanical flow and hydraulic flow power.
The technical scheme of the invention is as follows: a mechanical-hydraulic compound transmission adapted for use with a heavy-duty vehicle, comprising: a forward clutch, a reverse clutch, a pump motor, a first planet row; a second planet row, a third planet row; brake Z1, brake Z2, clutch L1, clutch L2; the forward clutch is only used for the forward gear running working condition, when the mechanical power flow and the hydraulic power flow work simultaneously, the power of the forward clutch comes from the gear, the gear is meshed with the gear, and the driving part and the driven part of the forward clutch are respectively the gear and the gear; after the forward clutch is combined, the mechanical flow provides mechanical power to the first planetary row through meshing of the gear and the gear; the reverse clutch is used for reverse gear running conditions, and when mechanical and hydraulic power flows work simultaneously, power is from the gear and the gear; the gear is meshed with the gear; the gear is meshed with the gear; the rotating direction is opposite to that of the forward clutch, and the driving and driven parts of the reverse clutch are respectively a gear and a gear; after the reverse clutch is combined, the mechanical flow supplies electric power to the first planetary row through meshing of gears; the pump motor, the pump power comes from gear, gear; the output end of the pump motor is connected with the sun gear of the first planet row; the gear is meshed with the gear; the first planet row consists of a sun gear of the first planet row, a first planet row planet gear set, a first planet row planet carrier and a first planet row gear ring; the gear is connected with the third planet row planet carrier into a whole; the second planet row consists of a second planet row sun gear, a second planet row planet gear set, a second planet row planet carrier and a second planet row gear ring; the third planet row consists of a third planet row sun gear, a third planet row planet gear set, a third planet row planet carrier and a third planet row gear ring; the third planet row sun gear is connected with the first planet row gear ring and the second planet row sun gear into a whole; one end of the central shaft of the second planet row sun gear is connected with the central shaft of the first planet row gear ring into a whole; the other end of the central shaft of the second planet row sun gear is connected with the central shaft of the third planet row sun gear into a whole; the third planet carrier and the first planet gear ring are connected into a whole; the first planet row, the second planet row and the third planet row are collectively called as a planet row; its own structure is specifically defined as: the planet row consists of a sun gear, a planet wheel set, a planet carrier and a gear ring; the sun gear, the gear ring and the planet carrier have a common fixed rotation axis, and planet wheels of the planet wheel set are supported on planet gear shafts fixed on the planet carrier, are externally meshed with the sun gear and are internally meshed with the gear ring; when the planet row runs, the planet wheel on the planet carrier revolves around the sun wheel along with the planet carrier while rotating around the planet wheel shaft, and the planet wheel set is composed of a plurality of planet wheels of the planet row where the planet wheel set is located.
Further, the brake Z1 is characterized in that the brake component is a third planet carrier;
the brake Z2 is characterized in that the brake component is a third planet row gear ring;
the clutch L1 is characterized in that the operated components are a first planet row planet carrier and a second planet row planet carrier respectively;
the clutch L2 is characterized in that the operated components are a third planet carrier and a third planet ring gear respectively; when the clutch L2 is engaged, the third planetary row ring gear of the third planetary row is integrally connected with the third planetary row carrier, and the third planetary row integrally rotates.
Further, the structure of the forward clutch is the same as that of the reverse clutch, and the rotating speed is the same.
Further, the forward operating range has four modes or four ranges in total:
in the mode I, the brake Z1 and the clutch L1 are combined, only one path of the pump motor works, the mechanical path has no power input, the first planetary row and the second planetary row work, and power is output through a gear ring of the second planetary row and a planet carrier of the third planetary row; the pump motor is in a pure hydraulic working condition;
in a mode II, the forward clutch Lf and the brake Z2 are combined, the first planetary row and the third planetary row work simultaneously, the second planetary row idles, and power is output to a gear by a gear ring of the third planetary row after being coupled; the pump motor is in a mechanical hydraulic composite transmission working condition;
in the mode III, the forward clutch Lf and the clutch L1 are combined, the first planet row and the second planet row work, the third planet row idles, and power is output by a gear ring of the second planet row and a planet carrier of the third planet row; the pump motor is in a mechanical hydraulic composite transmission working condition;
in a mode IV, the forward clutch Lf and the clutch L2 are combined, the first planetary row and the third planetary row work, the third planetary row rotates integrally, and power is output by a planetary carrier of the third planetary row; the pump motor is in a mechanical hydraulic composite transmission working condition.
Further, the reverse condition has four modes or gears in total:
in the mode I, the brake Z1 and the clutch L1 are combined, only one pump motor works, the mechanical path has no power input, the first planetary row and the second planetary row work, and power is output through a gear ring of the second planetary row and a planet carrier of the third planetary row; pump motor,The working condition is pure hydraulic pressure;
in the mode II, the reverse clutch Lr and the brake Z2 are combined, the first planetary row and the third planetary row work simultaneously, the second planetary row idles, and power is output to a gear by a gear ring of the third planetary row after being coupled; the pump motor is in a mechanical hydraulic composite transmission working condition;
in the mode-III, the reverse clutch Lr and the clutch L1 are combined, the first planet row and the second planet row work, the third planet row idles, power is output by a gear ring of the second planet row and a planet carrier of the third planet row, and a pump motor is in a mechanical hydraulic compound transmission working condition;
in the mode IV, the reverse gear clutch Lr and the clutch L2 are combined, the first planetary row and the third planetary row work, the third planetary row rotates integrally, power is output by a planetary carrier of the third planetary row, and a pump motor is in a mechanical hydraulic composite transmission working condition.
The invention has the technical effects that:
1) suitable for wheeled or tracked vehicle drive systems;
2) the structure is relatively simple, the transmission efficiency of the device is high, and the power density is high;
3) by means of the power coupling mechanism, the power requirement for the hydraulic components is reduced. The hydraulic element with smaller specification can realize larger total power output, namely, the power amplification factor is higher.
4) Can be applied to tracked vehicles by simply adding steering flow
The invention can realize the stepless speed change of the vehicle, realize the amplification effect of the output power on the hydraulic power through the action of the planetary coupling mechanism, and reduce the power requirement on the hydraulic element, thereby selecting the hydraulic element with smaller specification and realizing larger transmission power. The simple diagram can be directly applied to a transmission system of a wheeled vehicle, and can be applied to the field of tracked vehicles after the supplementary steering flow.
Drawings
FIG. 1 is a simplified drive diagram of a mechanical-hydraulic compound transmission suitable for heavy vehicles.
FIG. 2 is a schematic diagram of the operation of the various sections of a hydraulic machine suitable for use in a mechanical-hydraulic compound transmission for a heavy-duty vehicle.
Detailed Description
The invention is suitable for a transmission system of a wheeled or tracked vehicle, an engine is an input port of the transmission system, and a planet carrier of the last row in three planet rows is an output member of an output end. Including a forward clutch, a reverse clutch, a hydraulic pump motor, three planetary rows, and four operators of the planetary rows, etc. The planetary mechanism consists of three simple planetary rows, the motor is connected with the sun gear of the first planetary row, and the mechanical flow input is connected with the planetary carrier of the first planetary row. In addition to the forward and reverse clutches, the system includes two clutches, two brakes, and six operating members, and different driving modes can be obtained by means of different combinations of the operating members. The invention can realize the stepless speed change of the vehicle, so that the vehicle has good maneuvering performance, and the total power of the system transmission is amplified through the planetary power coupling mechanism at the output end. The device is suitable for heavy wheeled or tracked vehicles and is easy to arrange a vehicle power transmission system.
The technical solution of the present invention is further described with reference to the accompanying drawings of the present invention,
as shown in fig. 1, a mechanical hydraulic compound transmission schematic diagram for a heavy vehicle comprises: a forward clutch (6), a reverse clutch (7), a pump motor (2), a first planet row (3); a second planetary row (4), a third planetary row (5); brake Z1(28), brake Z2(29), clutch L1(30), and clutch L2 (31).
The forward clutch (6) is only used in a forward gear running condition, and when mechanical and hydraulic power flows work simultaneously, the power of the forward clutch comes from the gear (8), the gear (14), and the clutch driving and driven parts are the gear (14) and the gear (12) respectively. After the clutch is combined, the mechanical flow provides mechanical power to the first planetary row (3) through the gear (12) and the gear (13);
the reverse clutch (7) is used for reverse gear running conditions, when mechanical power flow and hydraulic power flow work simultaneously, power is obtained from a gear (8), a gear (9), a gear (10) and a gear (11), the rotating direction of the reverse clutch is opposite to that of the forward clutch (6), and a clutch driving driven part is the gear (11) and a clutch driven part is the gear (12) respectively. After the clutch is combined, the mechanical flow supplies electric power to the first planetary row (3) through the gear (12) and the gear (13);
the pump motor (2) and the pump power come from a gear (8), a gear (14) and a gear (15). The output end of the motor is connected with a sun wheel (16) of the first planet row (3);
the first planet row (3) consists of a sun gear (16), a planet gear set (17), a planet carrier (18) and a gear ring (19); the gear (13) and the planet carrier (18) are the same component.
The second planet row (4) consists of a sun gear (20), a planet gear set (21), a planet carrier (22) and a gear ring (23); the sun gear (20) and the first planet row ring gear (19) are the same component.
The third planet row (5) consists of a sun gear (24), a planet gear set (25), a planet carrier (26) and a gear ring (27); the sun gear (24) and the first planet row ring gear (19) and the second planet row sun gear (20) are the same component. The planet carrier (26) and the first planet row gear ring (23) are the same component
The brake Z1(28) is characterized in that the brake component is a first planet carrier (18).
And the brake Z2(29) is characterized in that the brake component is a third planet row ring gear (27).
The clutch L1(30) is operated by the planet carrier 18 of the first planet row and the planet carrier 22 of the second planet row.
The clutch L2(31) is operated by a third planet carrier (26) and a third planet ring gear (27). When the clutch L2(31) is engaged, the ring gear (27) of the third planetary row (5) is integrally connected to the carrier (26), and the third planetary row (5) rotates as a whole.
A third planet carrier (26) acts to output power from the transmission to the output member.
All the planet rows adopted in the invention are composed of a sun wheel, a gear ring, a planet carrier and a plurality of planet wheels. The sun wheel, the ring gear and the planet carrier have a common fixed axis of rotation, and the planet wheels are supported on planet wheel shafts fixed to the planet carrier, and are in external engagement with the sun wheel and at the same time are in internal engagement with the ring gear. When the planet row operates, the planet wheels which are sleeved on the planet carrier rotate around the planet wheel shafts, and simultaneously revolve around the sun wheel along with the planet carrier. The planetary gear set is composed of a plurality of (at least 3) planetary gears of the planetary row.
The forward clutch (6), the reverse clutch (7), the brake Z1(28), the brake Z2(29), the clutch L1(30) and the clutch L2(31) are all wet friction plate type elements.
The invention relates to a working principle of a mechanical hydraulic composite transmission device transmission diagram suitable for a heavy vehicle, which comprises the following steps: different driving modes can be obtained by means of different combinations of the operating members and the transmission characteristics of the planetary mechanism, and the driving state of the vehicle comprises a forward driving working condition and a reverse driving working condition.
Forward operating conditions the schematic has a total of four modes or gears
In the mode I, a brake Z1(28) and a clutch L1(30) are combined, only a pump motor works in one way, a mechanical path has no power input, a first planetary row (3) and a second planetary row (4) work, and power is output through a ring gear (23) of the second planetary row (4) and a planet carrier (26) of a third planetary row (5). Swash plate of pump motor (2) from 0 → Vpmax,The working condition is pure hydraulic pressure.
In the mode II, a front gear clutch Lf (6) and a brake Z2(29) are combined, a first planetary row (3) and a third planetary row (5) work simultaneously, a second planetary row (4) idles, and power is coupled and then is output by a gear ring (19) of the third planetary rowOut to the gear (24). The first planetary row (3) plays a role of power coupling, and the third planetary row (5) only plays a role of speed reduction and torque increase. The swash plate of the pump motor (2) is driven by a V at the end of the mode Ipmax,→0→-Vpmax,The method is a mechanical hydraulic composite transmission working condition.
In the mode III, a front-stage clutch Lf (6) and a clutch L1(30) are combined, a first planetary row (3) and a second planetary row (4) work, a third planetary row (5) idles, and power is output by a ring gear (23) of the second planetary row (4) and a planet carrier (26) of the third planetary row. The first planetary row (3) acts as a power coupling. The swash plate of the pump motor (2) is changed from-V at the end of mode IIpmax,→0→+Vpmax,The method is a mechanical hydraulic composite transmission working condition.
In the mode IV, the front-stage clutch Lf (6) and the clutch L2(31) are combined, the first planetary row (3) and the third planetary row (5) work, the third planetary row (5) integrally rotates, and power is output by a planet carrier (26) of the third planetary row (5). The first planetary row (3) acts as a power coupling. The swash plate of the pump motor (2) is changed to + V at the end of the mode IIIpmax,→0→-Vpmax,When the vehicle reaches the highest speed, the mechanical hydraulic compound transmission working condition is adopted.
Reverse operating mode the diagram has a total of four modes or gears
In mode-i, the brake Z1(28) and the clutch L1(30) are engaged, only the pump motor is operated in one path, the mechanical path has no power input, the first planetary row (3) and the second planetary row (4) are operated, and power is output through the ring gear (23) of the second planetary row (4) and the planet carrier (26) of the third planetary row (5). The swash plate of the pump motor (2) is changed from 0 → -Vpmax,The working condition is pure hydraulic pressure.
In the mode II, a reverse gear clutch Lr (7) and a brake Z2(29) are combined, a first planetary row (3) and a third planetary row (5) work simultaneously, a second planetary row (4) idles, and power is coupled and output to a gear (24) by a gear ring (19) of the third planetary row. The first planetary row (3) plays a role of power coupling, and the third planetary row (5) only plays a role of speed reduction and torque increase. The swash plate of the pump motor (2) is terminated by-V of mode Ipmax,→0→+Vpmax,The method is a mechanical hydraulic composite transmission working condition.
In the mode III, the reverse gear clutch Lr (7) and the clutch L1(30) are combined, the first planetary row (3) and the second planetary row (4) work, the third planetary row (5) idles, and power is output by a ring gear (23) of the second planetary row (4) and a planet carrier (26) of the third planetary row. The first planetary row (3) acts as a power coupling. The swash plate of the pump motor (2) is changed to + V at the end of the mode IIpmax,→0→-Vpmax,The method is a mechanical hydraulic composite transmission working condition.
In the mode-IV, the reverse gear clutch Lr (7) and the clutch L2(31) are combined, the first planetary row (3) and the third planetary row (5) work, the third planetary row (5) integrally rotates, and power is output by a planet carrier (26) of the third planetary row (5). The first planetary row (3) acts as a power coupling. The swash plate of the pump motor (2) is changed from-V at the end of mode IIIpmax,→0→+Vpmax,When the vehicle reaches the highest speed of the reverse gear, the mechanical hydraulic compound transmission working condition is adopted.
Mode(s) Clutch Lf Clutch Lr Brake Z1 Brake Z2 Clutch L1 Clutch L2
Mode I Is loosened Is loosened Bonding of Is loosened Bonding of Is loosened
Mode II Bonding of Is loosened Is loosened Bonding of Is loosened Is loosened
Mode III Bonding of Is loosened Is loosened Is loosened Bonding of Is loosened
Mode IV Bonding of Is loosened Is loosened Is loosened Is loosened Bonding of
mode-I Is loosened Is loosened Bonding of Is loosened Bonding of Is loosened
Mode II Is loosened Bonding of Is loosened Bonding of Is loosened Is loosened
mode-III Is loosened Bonding of Is loosened Is loosened Bonding of Is loosened
mode-IV Is loosened Bonding of Is loosened Is loosened Is loosened Bonding of
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principles of the present invention are intended to be included within the scope of the present invention.

Claims (10)

1. A mechanical-hydraulic compound transmission adapted for use with a heavy-duty vehicle, comprising: a forward clutch (6), a reverse clutch (7), a pump motor (2), a first planet row (3); a second planetary row (4), a third planetary row (5); brake Z1(28), brake Z2(29), clutch L1(30), clutch L2 (31);
the forward clutch (6) is only used in a forward gear running condition, when mechanical and hydraulic power flows work simultaneously, power of the forward clutch comes from a gear eight (8), the gear eight (8) is meshed with a gear fourteen (14), and a driving driven part and a driven part of the forward clutch are respectively a gear fourteen (14) and a gear twelve (12); after the forward clutch is engaged, the mechanical flow provides mechanical power to the first planetary row (3) through the meshing of gear twelve (12) and gear thirteen (13);
the reverse clutch (7) is used for reverse gear running conditions, and when mechanical and hydraulic power flows work simultaneously, power is from a gear nine (9) and a gear ten (10); the gear nine (9) is meshed with the gear ten (10); the gear ten (10) is meshed with the gear eleven (11); the rotating direction is opposite to that of the forward clutch (6), and the driving and driven parts of the reverse clutch are a gear eleven (11) and a gear twelve (12) respectively; after the reverse clutch is engaged, the mechanical flow provides electrical power to the first planetary row (3) through engagement of gear twelve (12) and gear thirteen (13);
the pump motor (2) has pump power from eight (8) gears, fourteen (14) gears and fifteen (15) gears; the output end of the pump motor is connected with a sun wheel (16) of the first planet row (3); the gear fourteen (14) and the gear fifteen (15) are meshed;
the first planet row (3) consists of a sun gear (16) of the first planet row, a first planet row planet gear set (17), a first planet row planet carrier (18) and a first planet row gear ring (19); a gear thirteen (13) is connected with a third planet carrier (18) into a whole;
the second planet row (4) consists of a second planet row sun gear (20), a second planet row planet gear set (21), a second planet row planet carrier (22) and a second planet row gear ring (23);
the third planet row (5) consists of a third planet row sun gear (24), a third planet row planet gear set (25), a third planet row planet carrier (26) and a third planet row gear ring (27); the third planet row sun gear (24) is connected with the first planet row gear ring (19) and the second planet row sun gear (20) into a whole;
one end of the central shaft of the second planet row sun gear (20) is connected with the central shaft of the first planet row gear ring (19) into a whole; the other end of the central shaft of the second planet row sun gear (20) is connected with the central shaft of the third planet row sun gear (24) into a whole; the third planet carrier (26) is connected with the first planet gear ring (23) into a whole;
the first planet row, the second planet row and the third planet row are collectively called as a planet row; its own structure is specifically defined as:
the planet row consists of a sun gear, a planet wheel set, a planet carrier and a gear ring; the sun gear, the gear ring and the planet carrier have a common fixed rotation axis, and planet wheels of the planet wheel set are supported on planet gear shafts fixed on the planet carrier, are externally meshed with the sun gear and are internally meshed with the gear ring; when the planet row runs, the planet wheel on the planet carrier revolves around the sun wheel along with the planet carrier while rotating around the planet wheel shaft, and the planet wheel set is composed of a plurality of planet wheels of the planet row where the planet wheel set is located.
2. The electro-hydraulic compound transmission for heavy vehicles according to claim 1, wherein:
the brake Z1(28) is characterized in that the brake component is a third planet carrier (26);
the brake Z2(29) is characterized in that the brake component is a third planet row ring gear (27);
the clutch L1(30), the operated components are a first planet row planet carrier (18) and a second planet row planet carrier (22) respectively;
the clutch L2(31), the operated components are a third planet carrier (26) and a third planet ring gear (27); when the clutch L2(31) is engaged, the third planetary row ring gear (27) of the third planetary row (5) and the third planetary row carrier (26) are integrally connected, and the third planetary row (5) integrally rotates.
3. The electro-hydraulic compound transmission for heavy vehicles according to claim 2, wherein: the structure of the forward clutch (6) is the same as that of the reverse clutch (7), and the rotating speed is the same.
4. A mechano-hydraulic compound transmission adapted for heavy vehicles according to claim 3, wherein:
the forward gear operating mode has four modes or four gears:
in the mode I, a brake Z1(28) and a clutch L1(30) are combined, only a pump motor works in one way, a mechanical path has no power input, a first planetary row (3) and a second planetary row (4) work, and power is output through a ring gear (23) of the second planetary row (4) and a planet carrier (26) of a third planetary row (5); the pump motor (2) is under a pure hydraulic working condition;
in a mode II, a forward clutch Lf (6) and a brake Z2(29) are combined, a first planet row (3) and a third planet row (5) work simultaneously, a second planet row (4) idles, and power is coupled and then output to a third planet row sun gear (24) through a gear ring (19) of the third planet row; the pump motor (2) is in a mechanical hydraulic composite transmission working condition;
in the mode III, a forward clutch Lf (6) and a clutch L1(30) are combined, a first planetary row (3) and a second planetary row (4) work, a third planetary row (5) idles, and power is output by a ring gear (23) of the second planetary row (4) and a planet carrier (26) of the third planetary row; the pump motor (2) is in a mechanical hydraulic composite transmission working condition;
in the mode IV, a forward clutch Lf (6) and a clutch L2(31) are combined, a first planetary row (3) and a third planetary row (5) work, the third planetary row (5) integrally rotates, and power is output by a planet carrier (26) of the third planetary row (5); the pump motor (2) is in a mechanical and hydraulic compound transmission working condition.
5. A mechano-hydraulic compound transmission adapted for heavy vehicles according to claim 3, wherein:
the reverse operating condition has four modes or gears:
in the mode I, a brake Z1(28) and a clutch L1(30) are combined, only a pump motor works in one way, a mechanical path has no power input, a first planetary row (3) and a second planetary row (4) work, and power is output through a ring gear (23) of the second planetary row (4) and a planet carrier (26) of a third planetary row (5); the pump motor (2) is under a pure hydraulic working condition;
in the mode II, a reverse clutch Lr (7) and a brake Z2(29) are combined, a first planetary row (3) and a third planetary row (5) work simultaneously, a second planetary row (4) idles, and power is coupled and then output to a third planetary row sun gear (24) through a gear ring (19) of the third planetary row; the pump motor (2) is in a mechanical hydraulic composite transmission working condition;
in the mode-III, the reverse clutch Lr (7) and the clutch L1(30) are combined, the first planetary row (3) and the second planetary row (4) work, the third planetary row (5) idles, power is output by a gear ring (23) of the second planetary row (4) and a planet carrier (26) of the third planetary row, and the pump motor (2) is in a mechanical hydraulic compound transmission working condition;
in a mode IV, the reverse clutch Lr (7) and the clutch L2(31) are combined, the first planetary row (3) and the third planetary row (5) work, the third planetary row (5) integrally rotates, power is output by a planetary carrier (26) of the third planetary row (5), and the pump motor (2) is in a mechanical hydraulic composite transmission working condition.
6. The mechano-hydraulic compound transmission of any one of claims 1-4, wherein: the pump motor (2) is of an integrated structure and is of a central perforated structure.
7. The mechano-hydraulic compound transmission of any one of claims 1-4, wherein: the pump motor (2) is of a split arrangement.
8. The mechano-hydraulic compound transmission of claim 6, wherein: the pump motor (2) is a variable pump and a fixed-displacement motor.
9. The mechano-hydraulic compound transmission of claim 5, wherein: the forward clutch (6), the reverse clutch (7), the brake Z1(28), the brake Z2(29), the clutch L1(30) and the clutch L2(31) are all wet friction plate type elements.
10. The mechano-hydraulic compound transmission of claim 1, wherein:
the forward gear operating mode has four modes or four gears:
in the mode I, a brake Z1(28) and a clutch L1(30) are combined, only a pump motor works in one way, a mechanical path has no power input, a first planetary row (3) and a second planetary row (4) work, and power is output through a ring gear (23) of the second planetary row (4) and a planet carrier (26) of a third planetary row (5); the pump motor (2) is under a pure hydraulic working condition;
in a mode II, a forward clutch Lf (6) and a brake Z2(29) are combined, a first planet row (3) and a third planet row (5) work simultaneously, a second planet row (4) idles, and power is coupled and then output to a third planet row sun gear (24) through a gear ring (19) of the third planet row; the pump motor (2) is in a mechanical hydraulic composite transmission working condition;
in the mode III, a forward clutch Lf (6) and a clutch L1(30) are combined, a first planetary row (3) and a second planetary row (4) work, a third planetary row (5) idles, and power is output by a ring gear (23) of the second planetary row (4) and a planet carrier (26) of the third planetary row; the pump motor (2) is in a mechanical hydraulic composite transmission working condition;
in the mode IV, a forward clutch Lf (6) and a clutch L2(31) are combined, a first planetary row (3) and a third planetary row (5) work, the third planetary row (5) integrally rotates, and power is output by a planet carrier (26) of the third planetary row (5); the pump motor (2) is in a mechanical and hydraulic composite transmission working condition;
the reverse operating condition has four modes or gears:
in the mode I, a brake Z1(28) and a clutch L1(30) are combined, only a pump motor works in one way, a mechanical path has no power input, a first planetary row (3) and a second planetary row (4) work, and power is output through a ring gear (23) of the second planetary row (4) and a planet carrier (26) of a third planetary row (5); the pump motor (2) is under a pure hydraulic working condition;
in the mode II, a reverse clutch Lr (7) and a brake Z2(29) are combined, a first planetary row (3) and a third planetary row (5) work simultaneously, a second planetary row (4) idles, and power is coupled and then output to a third planetary row sun gear (24) through a gear ring (19) of the third planetary row; the pump motor (2) is in a mechanical hydraulic composite transmission working condition;
in the mode-III, the reverse clutch Lr (7) and the clutch L1(30) are combined, the first planetary row (3) and the second planetary row (4) work, the third planetary row (5) idles, power is output by a gear ring (23) of the second planetary row (4) and a planet carrier (26) of the third planetary row, and the pump motor (2) is in a mechanical hydraulic compound transmission working condition;
in a mode IV, the reverse clutch Lr (7) and the clutch L2(31) are combined, the first planetary row (3) and the third planetary row (5) work, the third planetary row (5) integrally rotates, power is output by a planetary carrier (26) of the third planetary row (5), and the pump motor (2) is in a mechanical hydraulic composite transmission working condition.
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CN114087334B (en) * 2021-11-17 2023-11-03 浙江盘毂动力科技有限公司 Hydraulic mechanical combined type comprehensive transmission device and vehicle
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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102537269A (en) * 2012-02-07 2012-07-04 北京理工大学 Three-section hydraulic mechanical continuous stageless transmission device and method thereof
CN106342041B (en) * 2012-06-29 2014-07-30 中国北方车辆研究所 A kind of electromechanical compound gearing for series parallel hybrid power endless-track vehicle
CN204647180U (en) * 2015-01-28 2015-09-16 南京农业大学 A kind of big-power tractor hydraulic mechanical stepless gearbox
CN108591410A (en) * 2018-04-25 2018-09-28 中国北方车辆研究所 A kind of four-part form Hydromechanical Stepless Transmission device for endless-track vehicle
CN109318696A (en) * 2017-07-31 2019-02-12 迪尔公司 Multi-mode dynamical system
CN208951239U (en) * 2018-09-06 2019-06-07 南京农业大学 A kind of big-powered tractor infinitely variable transmission
CN110822053A (en) * 2019-10-08 2020-02-21 江苏大学 Multi-power distribution mode mechanical-hydraulic composite transmission device and control method

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9121492B2 (en) * 2011-01-12 2015-09-01 Gm Global Technology Operations, Llc Hybrid transmission arrangement having a motor damper

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102537269A (en) * 2012-02-07 2012-07-04 北京理工大学 Three-section hydraulic mechanical continuous stageless transmission device and method thereof
CN106342041B (en) * 2012-06-29 2014-07-30 中国北方车辆研究所 A kind of electromechanical compound gearing for series parallel hybrid power endless-track vehicle
CN204647180U (en) * 2015-01-28 2015-09-16 南京农业大学 A kind of big-power tractor hydraulic mechanical stepless gearbox
CN109318696A (en) * 2017-07-31 2019-02-12 迪尔公司 Multi-mode dynamical system
CN108591410A (en) * 2018-04-25 2018-09-28 中国北方车辆研究所 A kind of four-part form Hydromechanical Stepless Transmission device for endless-track vehicle
CN208951239U (en) * 2018-09-06 2019-06-07 南京农业大学 A kind of big-powered tractor infinitely variable transmission
CN110822053A (en) * 2019-10-08 2020-02-21 江苏大学 Multi-power distribution mode mechanical-hydraulic composite transmission device and control method

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