CN108468781B - Combined double-flow variable-speed transmission device - Google Patents

Abstract

A combined double-flow variable-speed transmission device mainly comprises an input transmission module, a low-gear transfer case, a low-gear hydraulic transmission module, a low-gear mechanical transmission module, a high-gear transfer case, a high-gear hydraulic transmission module, a high-gear mechanical transmission module, a hydraulic motor, a motor output transmission module and an output shaft. The scheme combines two sets of front-mounted power internal shunt double-flow transmission systems to form a combined transmission device, so that the combined transmission device has the characteristics of a hydraulic-mechanical double-flow transmission system, can realize the speed change and gear shift functions of the double-clutch transmission, and further improves the performance of the speed change transmission device. The double-clutch transmission device has the gear shifting function of the double clutches, can transmit power in three transmission modes of hydraulic transmission, hydraulic-mechanical double-flow transmission and mechanical transmission, has the characteristics of stepless speed regulation of hydraulic transmission and high efficiency of mechanical transmission in the transmission process, and can better meet the requirements of vehicles, particularly engineering machinery, agricultural machinery and other complex and changeable use conditions of running conditions.

Description

Combined double-flow variable-speed transmission device

Technical Field

The invention belongs to the field of vehicle variable-speed transmission, and particularly relates to a vehicle double-flow variable-speed transmission device which is formed by compounding two sets of hydraulic-mechanical double-flow transmission devices based on hydraulic-mechanical double-flow transmission by using the variable-speed transmission principle of a double-clutch (DCT) transmission, can realize uninterrupted power in the gear shifting process, has the characteristics and advantages of hydraulic transmission and mechanical transmission, and is suitable for various passenger and goods road transport vehicles, agricultural equipment, engineering machinery and other non-road vehicles.

Background

Because the driving scene of the vehicle is changeable, the road condition is complex, and the driving speed variation range is large, the variable speed transmission system is an indispensable key component of various vehicles. Different use purposes and application occasions have different requirements on the performance of the vehicle. In vehicles powered by an internal combustion engine in the market AT present, the mounted speed change transmission systems mainly include a manual mechanical transmission, a semi-Automatic Mechanical Transmission (AMT), a power shift automatic transmission (fixed shaft AT), a rotary shaft Automatic Transmission (AT), a mechanical continuously variable automatic transmission (CVT), a dual clutch automatic transmission (DCT, DSG) and the like, and the transmissions have different structures and performances but have the common characteristic of transmitting power in a mechanical transmission mode. In order to meet the use requirements of low speed and large load change, a hydrostatic transmission product based on hydrostatic transmission is often mounted and applied on a part of off-road vehicles with low working speed, such as engineering machinery, agricultural equipment and the like. In addition, a part of engineering machinery, agricultural equipment and special vehicles are also provided with a hydraulic-mechanical double-flow transmission product which simultaneously utilizes two transmission modes of hydraulic and mechanical.

The mechanical variable transmission mainly takes gears and shaft parts as transmission system components, and meets the requirements on the output rotating speed and torque of the transmission by forming the change of the transmission ratio through the combination of different gears. Generally speaking, the mechanical variable speed transmission has the advantages of relatively simple structure, high transmission efficiency, mature process, low manufacturing cost and the like, but the matching with an engine cannot always reach the optimal level due to the characteristics of the mechanical variable speed transmission.

The hydraulic transmission generally includes hydraulic elements and components such as a hydraulic pump, a hydraulic motor, and hydraulic valves and hydraulic pipes with various functions, wherein the hydraulic pump is a "primary transduction element" for converting mechanical energy of an input system into hydraulic energy, and the hydraulic motor is a "secondary transduction element" for converting hydraulic energy into mechanical energy. The working principle of the hydraulic speed changer is as follows: the hydraulic pump converts the mechanical energy of the engine input system into hydraulic energy represented by oil pressure and flow, and the hydraulic energy is transmitted to the hydraulic motor through a hydraulic pipeline and then converted into mechanical energy by the motor to be output, so that the hydraulic transmission process is realized by two energy processes of 'machine-liquid' and 'liquid-machine', and when the hydraulic pump or the hydraulic motor with variable displacement or the displacement of the hydraulic motor and the hydraulic motor are variable, the transmission ratio of the system can be conveniently changed to realize variable-speed transmission by simply adjusting the displacement ratio of the hydraulic pump to the hydraulic motor. The hydraulic transmission has the characteristics of high energy transmission density, simple system composition, light weight, easy realization of stepless speed regulation, convenient flexible arrangement on the whole vehicle and the like, but the inherent oil leakage and heating problems of the hydraulic transmission often cause the hydraulic transmission efficiency to be relatively low, and meanwhile, the working rotating speed of a hydraulic pump and a hydraulic motor high-efficiency area is relatively low compared with that of mechanical transmission, so that the adaptability to high-rotating-speed output working conditions is poor.

The Hydraulic-Mechanical double-flow Transmission is also called as HMT (Hydraulic-Mechanical Transmission), and is a hybrid Transmission mode, and the Transmission is characterized in that power is divided into Hydraulic power and Mechanical power at a certain node of a Transmission chain, and the Hydraulic power and the Mechanical power are transmitted to the next node in parallel in the Hydraulic Transmission and Mechanical Transmission modes and then output in parallel. At an input node, the hydraulic-mechanical double-flow transmission is characterized in that input power is divided into hydraulic power and mechanical power through a special transfer device and then is transmitted backwards, and the hydraulic-mechanical double-flow transmission is called as 'front transfer type double-flow transmission'; on the output node, a hydraulic-mechanical double-flow transmission is called as a post-confluence double-flow transmission, wherein the power transmitted in parallel by the previous node in a hydraulic mode and a mechanical mode is converged by a special converging device and then transmitted backwards. The transfer gear is of the same type as the collector gear, and is usually a hydraulic transducer element (hydraulic pump or hydraulic motor) or a combination of a hydraulic transducer element and a planetary gear mechanism. When a single hydraulic transduction element is used as a transfer device or a confluence device, as the transfer or confluence is completed in the hydraulic transduction element, the transmission is called as power internal shunt or power internal confluence, when one hydraulic transduction element is used as a front transfer device, the transmission is called as a front power internal shunt double-flow transmission system, and when one hydraulic transduction element is used as a rear confluence device, the transmission is called as a rear power internal confluence double-flow transmission system; the transfer or confluence device formed by a hydraulic energy conversion element and a planetary gear mechanism is called as power external shunt or power external confluence because the transfer or confluence is completed outside the hydraulic energy conversion element, when the hydraulic energy conversion element and the planetary gear mechanism are combined to be used as a front transfer device, the transfer or confluence device is called as a front power external shunt double-flow transmission system, and when the hydraulic energy conversion element and the planetary gear mechanism are combined to be used as a rear confluence device, the transfer or confluence device is called as a rear power external confluence double-flow transmission system. The existing market mainly adopts an external shunting technology, and products loaded with the technology have a front-mounted power external shunting double-current transmission system and a rear-mounted power external converging double-current transmission system, but have no case of successful application of the internal shunting technology.

Disclosure of Invention

The invention provides a combined double-flow variable-speed transmission device, which aims to form the combined transmission device by combining two sets of front-mounted power internal-shunt double-flow transmission systems, so that the combined transmission device has the characteristics of a hydraulic-mechanical double-flow transmission system, can realize the variable-speed and gear-shifting functions of a double-clutch transmission and further improves the performance of the variable-speed transmission device.

In order to achieve the purpose, the invention adopts the technical scheme that: a combined double-flow variable-speed transmission device mainly comprises an input transmission module, a low-gear transfer case, a low-gear hydraulic transmission module, a low-gear mechanical transmission module, a high-gear transfer case, a high-gear hydraulic transmission module, a high-gear mechanical transmission module, a hydraulic motor, a motor output transmission module and an output shaft.

The input transmission module consists of an input shaft, an input gear, a low-gear input shaft, a low-gear meshing sleeve, a high-gear input gear, a high-gear input shaft and a high-gear meshing sleeve.

The input shaft is rotatably supported on the housing of the transmission device, and the input gear is fixedly arranged on the input shaft and is simultaneously meshed with the low-gear input gear and the high-gear input gear.

The low-gear input gear is provided with a central shaft and is rotatably supported on the shell by the central shaft; the low-gear input shaft and the low-gear input gear are coaxially arranged, the low-gear meshing sleeve is sleeved at one end of the low-gear input shaft and can axially slide along the low-gear input shaft, when the low-gear meshing sleeve slides to one side of the low-gear input gear and is combined with the low-gear input gear, the low-gear input gear and the low-gear input shaft form transmission connection, and when the low-gear meshing sleeve slides to the other side, the low-gear input gear and the low-gear input shaft are disconnected.

The high-gear input gear is provided with a central shaft and is rotatably supported on the shell by the central shaft; the high-gear input shaft and the high-gear input gear are coaxially arranged, the high-gear meshing sleeve is sleeved at one end of the high-gear input shaft and can axially slide along the high-gear input shaft, when the high-gear meshing sleeve slides to one side of the high-gear input gear and is combined with the high-gear input gear, the high-gear input gear and the high-gear input shaft form transmission connection, and when the high-gear meshing sleeve slides to the other side, the high-gear input gear and the high-gear input shaft are disconnected.

The low-gear transfer case mainly comprises a low-gear displacement pump, a low-gear oil inlet seal and a low-gear oil discharge seal, wherein a rotor of the low-gear displacement pump is used as a low-gear driving end of the low-gear transfer case to be in transmission connection with a low-gear input shaft, and a stator of the low-gear displacement pump is used as a low-gear driven end of the low-gear transfer case to be in rotary support relative to the shell; the low-gear oil inlet seal is a rotary seal channel for low-gear displacement pump oil inlet, the rotary seal channel is provided with a low-gear oil inlet fixed port and a low-gear oil inlet rotary port, the low-gear oil inlet rotary port is connected with an oil inlet of the low-gear displacement pump and communicated with a low-pressure cavity of the low-gear displacement pump, and the low-gear oil inlet fixed port is used as an oil inlet of a low-gear transfer case; the low-gear oil discharge seal is a rotary seal channel for discharging oil of a low-gear displacement pump, the rotary seal channel is provided with a low-gear oil discharge fixed port and a low-gear oil discharge rotary port, the low-gear oil discharge rotary port is connected with an oil discharge port of the low-gear displacement pump and communicated with a high-pressure cavity of the low-gear displacement pump, and the low-gear oil discharge fixed port serves as an oil discharge port of a low-gear transfer case.

The low-gear hydraulic transmission module comprises a low-gear one-way valve, a low-gear switch valve, a low-gear throttle valve and a low-gear check valve.

The low-gear one-way valve is communicated with an oil path from the oil tank to the oil inlet of the low-gear transfer case in a one-way mode, and a low-gear inlet converging point is arranged between the low-gear one-way valve and the oil inlet of the low-gear transfer case.

The low-gear switch valve is a two-position two-way switch valve and is provided with a low-gear switch valve inlet and a low-gear switch valve outlet, an oil discharge oil way is formed in the outward extension of an oil discharge port of the low-gear transfer case, a low-gear diversion point and a confluence point are sequentially arranged on the oil discharge oil way in advance, the low-gear switch valve is connected in series on the oil discharge oil way between the oil discharge port of the low-gear transfer case and the low-gear diversion point, the inlet of the low-gear switch valve is communicated with the oil discharge port of the low-gear transfer case, the outlet of the low-gear switch valve is communicated with the low-gear diversion point, when the low-gear switch valve is in the left position, the oil way from the oil discharge port of the low-gear transfer case to the low-gear diversion point is cut off, when the low-gear switch valve is in the right position, the oil way from the oil discharge.

The low-gear throttle valve is an adjustable throttle valve, the opening adjusting range of the low-gear throttle valve is from full-closed to full-open, the low-gear throttle valve is provided with a low-gear throttle valve inlet and a low-gear throttle valve outlet, the low-gear throttle valve inlet is communicated with a low-gear splitting point, the low-gear throttle valve outlet is communicated with a low-gear inlet confluence point, when the low-gear throttle valve is fully closed, an oil path from the low-gear splitting point to the low-gear inlet confluence point is cut off, when the low-gear throttle valve is fully opened, the oil path from the low-gear splitting point to the low-gear inlet confluence point is completely communicated, when the low-gear throttle valve is partially opened, the oil path from the low-gear splitting point to the low-gear inlet confluence point is partially communicated, and the communicating degree of the oil.

The low-gear check valve is a one-way valve and is provided with a low-gear check valve inlet and a low-gear check valve outlet, the low-gear check valve is communicated with the oil way from a low-gear shunting point to a converging point in a one-way mode, the low-gear check valve inlet is communicated with the low-gear shunting point, and the low-gear check valve outlet is communicated with the converging point.

The low-gear mechanical transmission module comprises a low-gear driven shaft, a low-gear driving gear and a low-gear driven gear; the low-gear driven shaft is rotatably supported on the shell, one end of the low-gear driven shaft is in transmission connection with a low-gear driven end of the low-gear transfer case, the other end of the low-gear driven shaft is in transmission connection with a low-gear driving gear, the low-gear driving gear is in transmission connection with a low-gear driven gear, and the low-gear driven gear is in transmission connection with the output shaft.

The high-gear transfer case mainly comprises a high-gear displacement pump, a high-gear oil inlet seal and a high-gear oil discharge seal, wherein a rotor of the high-gear displacement pump is used as a high-gear driving end of the high-gear transfer case and is in transmission connection with a high-gear input shaft, and a stator of the high-gear displacement pump is used as a high-gear driven end of the high-gear transfer case and is in rotary support relative to the shell; the high-gear oil inlet seal is a rotary seal channel for oil inlet of the high-gear positive displacement pump, the rotary seal channel is provided with a high-gear oil inlet fixed port and a high-gear oil inlet rotary port, the high-gear oil inlet rotary port is connected with an oil inlet of the high-gear positive displacement pump and communicated with a low-pressure cavity of the high-gear positive displacement pump, and the high-gear oil inlet fixed port is used as an oil inlet of a high-gear transfer case; the high-gear oil discharge seal is a rotary seal channel for discharging oil of a high-gear displacement pump, the rotary seal channel is provided with a high-gear oil discharge fixed port and a high-gear oil discharge rotary port, the high-gear oil discharge rotary port is connected with an oil discharge port of the high-gear displacement pump and communicated with a high-pressure cavity of the high-gear displacement pump, and the high-gear oil discharge fixed port serves as an oil discharge port of a high-gear transfer case.

The high-gear hydraulic transmission module comprises a high-gear one-way valve, a high-gear switch valve, a high-gear throttle valve and a high-gear check valve.

The high-gear one-way valve is communicated with an oil way from the oil tank to the oil inlet direction of the high-gear transfer case in a one-way mode, and a high-gear inlet converging point is arranged between the high-gear one-way valve and the oil inlet of the high-gear transfer case.

The high-gear switch valve is a two-position two-way switch valve and is provided with a high-gear switch valve inlet and a high-gear switch valve outlet, an oil discharge oil way is formed in the oil discharge port of the high-gear transfer case in an outward extending mode, a high-gear shunting point is arranged on the oil discharge oil way, the high-gear switch valve is connected in series with the oil discharge oil way between the oil discharge port of the high-gear transfer case and the high-gear shunting point, the inlet of the high-gear switch valve is communicated with the oil discharge port of the high-gear transfer case, the outlet of the high-gear switch valve is communicated with the high-gear shunting point, when the high-gear switch valve is in the left position, the oil way from the oil discharge port of the high-gear transfer case to the high-gear shunting point is cut off, when the high-gear switch valve is in the right position, the oil way from the.

The high-gear throttle valve is an adjustable throttle valve, the opening adjusting range of the high-gear throttle valve is from full-closed to full-open, the high-gear throttle valve is provided with a high-gear throttle valve inlet and a high-gear throttle valve outlet, the high-gear throttle valve inlet is communicated with a high-gear splitting point, the high-gear throttle valve outlet is communicated with a high-gear inlet confluence point, when the high-gear throttle valve is fully closed, an oil path from the high-gear splitting point to the high-gear inlet confluence point is cut off, when the high-gear throttle valve is fully opened, the oil path from the high-gear splitting point to the high-gear inlet confluence point is completely conducted, when the high-gear throttle valve is partially opened, the oil path from the high-gear splitting point to the high-gear inlet confluence point is partially conducted, and the conducting degree of the high.

The high-gear check valve is a one-way valve and is provided with a high-gear check valve inlet and a high-gear check valve outlet, the high-gear check valve is communicated with an oil way from a high-gear shunting point to a converging point in a one-way mode, the high-gear check valve inlet is communicated with the high-gear shunting point, and the high-gear check valve outlet is communicated with the converging point.

The high-gear mechanical transmission module comprises a high-gear driven shaft, a high-gear driving gear and a high-gear driven gear; the high-gear driven shaft is rotatably supported on the shell, one end of the high-gear driven shaft is in transmission connection with a high-gear driven end of the high-gear transfer case, the other end of the high-gear driven shaft is in transmission connection with a high-gear driving gear, the high-gear driving gear is in transmission connection with a high-gear driven gear, and the high-gear driven gear is in transmission connection with the output shaft.

The hydraulic motor is a positive displacement variable displacement hydraulic motor, a stator of the hydraulic motor is fixedly arranged on the shell, the hydraulic motor is provided with an oil inlet and an oil outlet, the confluence point is communicated with the oil inlet of the hydraulic motor, and the oil outlet of the hydraulic motor is communicated with an oil tank.

The motor output transmission module comprises an overrunning clutch, a motor shaft, a motor driving gear and a motor driven gear.

The overrunning clutch has the characteristic of unidirectional power transmission and is provided with a driving end and a driven end, the driving end of the overrunning clutch is in transmission connection with a motor shaft, the motor shaft is rotatably supported on the shell, the motor shaft is in transmission connection with a rotor of the hydraulic motor, the driven end of the overrunning clutch is fixedly arranged on a motor driving gear, when the hydraulic motor outputs rotating speed through the motor shaft and the output rotating speed has the trend of exceeding the rotating speed of a motor driving gear, the overrunning clutch is combined, the power of the hydraulic motor is transmitted to the motor driving gear, and when the rotating speed of the motor shaft is lower than the rotating speed of the motor driving gear, the overrunning clutch is separated and interrupts the motor shaft to transmit power to the motor driving gear; the motor driving gear is meshed with the motor driven gear, the motor driven gear is in transmission connection with the output shaft, and the output shaft is rotatably supported on the shell.

The related technical content of the technical scheme is explained as follows:

1. in the above scheme, referring to fig. 1, since the low-gear transfer FD1 is a positive displacement pump, the low-gear driving end IM1 is a rotor of the positive displacement pump and is in transmission connection with the low-gear input shaft IZ1, the low-gear driven end DM1 is a stator of the positive displacement pump and is fixedly arranged at one end of the low-gear driven shaft DZ1, and the low-gear driving end IM1 and the low-gear driven end DM1 can rotate synchronously or in differential speed with respect to the casing KT, the low-gear transfer FD1 can generate an effect of sucking and discharging oil when the low-gear driving end IM1 and the low-gear driven end DM1 have a difference in rotation speed. In the process of sucking and discharging oil by the low-gear transfer case FD1, when the discharged oil pressure is 0, the low-gear transfer case FD1 only outputs hydraulic flow but does not form hydraulic power output, and meanwhile, mechanical power output does not exist, at the moment, the low-gear transfer case FD1 does not have transmission and transfer functions, and the state is equivalent to the 'separation' working condition of a clutch; when the discharged oil pressure is not 0, the low-gear transfer FD1 outputs hydraulic power, meanwhile, the oil pressure in the internal closed working cavity is transmitted to the low-gear driven end DM1, so that the low-gear driven end DM1 can generate torque relative to the low-gear driven shaft DZ1, and mechanical power output is formed when the low-gear driven shaft DZ1 rotates, so that the 'transfer function' of the low-gear transfer FD1 is realized; when an oil discharge port of the low gear transfer case FD1 is cut off, the low gear transfer case FD1 can generate rotation blocking, the low gear driving end IM1 and the low gear driven end DM1 rotate synchronously, the low gear transfer case FD1 loses the transfer function, and the power input by the low gear driving end IM1 is completely transmitted to the low gear driven end DM1, and the state is equivalent to the 'engagement' working condition of the clutch. As can be seen, the low range transfer FD1 has three functions, clutch disengaged, transfer, and clutch engaged. Similarly, the high range divider FD2 also has the same function as the low range divider FD1. The principles and structures of the low-gear transfer case FD1 and the high-gear transfer case FD2 can be seen in a power splitter in Chinese patent CN 106838196A.

2. In the above scheme, referring to fig. 1, the overrunning clutch SC in the motor output transmission module has the characteristic of unidirectional transmission of the rotation speed and the torque. According to the invention, the driving end of the overrunning clutch SC is in transmission connection with the motor shaft MZ, the driven end is fixedly arranged on the motor driving gear Cm1, when the hydraulic motor HM outputs the rotating speed through the motor shaft MZ and the output rotating speed has the trend of exceeding the rotating speed of the motor driving gear Cm1, the overrunning clutch SC is combined, and the motor shaft MZ transmits the power of the hydraulic motor HM to the motor driving gear Cm 1; when the rotation speed of the motor shaft MZ is lower than the rotation speed of the motor driving gear Cm1, the overrunning clutch SC is disengaged and interrupts the motor shaft MZ from transmitting power to the motor driving gear Cm1, so that power circulation and transmission loss caused by reverse transmission of mechanical power to the hydraulic transmission module can be avoided. Furthermore, when the low range transfer FD1 or the high range transfer FD2 are in the transfer state, the magnitude of the hydraulic power and the mechanical power of the transfer output is proportional to the magnitude of the hydraulic pressure supplied to the hydraulic motor HM, which is proportional to the magnitude of the resistive torque experienced at the hydraulic motor shaft MZ, at a certain flow rate. When the transmission device works, when the working resistance on the output shaft OZ changes within a certain range, the one-way transmission characteristic of the overrunning clutch SC can always automatically adjust the oil pressure on the hydraulic transmission path through the self system to keep the output rotating speed No unchanged, so the setting of the overrunning clutch SC ensures that the double-flow transmission device has the characteristic of self-adaptive pressure adjustment.

3. In the scheme, as shown in fig. 1, the low-gear transfer case FD1 and the high-gear transfer case FD2 adopt fixed displacement pumps, and the hydraulic motor HM adopts a displacement variable motor, so that when the system works in a double-flow transmission state, the hydraulic transmission ratio of the low-gear transfer case FD1 or the high-gear transfer case FD2 to the hydraulic motor HM can be changed by continuously adjusting the displacement of the hydraulic motor HM, and the total transmission ratio of the double-flow transmission device can be continuously adjusted within a certain range.

4. In the foregoing solution, referring to fig. 1, the low range throttle valve VD1 is used to control the operating pressure of the low range transfer FD1, and at the same time, to adjust the low range transfer oil supply flow rate Qd1 branched to the hydraulic motor HM at the low range split point f1 and the low range transfer return flow rate Qh1 returned to the low range transfer oil inlet a1. Under the condition that the low-gear driving end IM1 has power input and the low-gear driving end IM1 and the low-gear driven end DM1 have a rotation speed difference, when a low-gear throttle valve VD1 is fully opened, a low-gear transfer case oil outlet b1 is completely communicated with a low-gear transfer case oil inlet a1, the liquid flow resistance can be regarded as 0, oil liquid discharged from the low-gear transfer case oil outlet b1 completely flows back to the low-gear transfer case oil inlet a1, and the low-gear transfer case FD1 cannot establish oil pressure inside the low-gear transfer case FD1, so that transmission cannot be realized and is in a state similar to clutch separation. During the adjustment process of the low-gear throttle valve VD1 from full opening to full closing, the gradually increased throttling effect causes the oil pressure at the low-gear splitting point f1 and the oil pressure in the low-gear transfer FD1 to synchronously rise and enables the low-gear check valve VS3 to be opened, after the oil discharged by the low-gear transfer FD1 reaches the low-gear splitting point f1, one part of the oil flows back to a low gear transmission oil inlet a1 by a low gear transmission return flow rate Qh1, the other part of the oil flows is transmitted to a hydraulic motor HM by a low gear transmission oil supply flow rate Qd1 through a low gear check valve VS3, while driving the rotor of the hydraulic motor HM to rotate and outputting the motor shaft rotation speed Nm and the motor shaft torque Mm through the motor shaft MZ, at the same time, the low range driven end DM1 also outputs the low range driven shaft rotation speed No1 and the low range driven shaft torque Mo1 through the low range driven shaft DZ1, and therefore the low range transfer return flow Qh1 is not 0 in this process, so that the low range transfer FD1 is in a state similar to clutch "half-engaged". When the low range throttle VD1 reaches "full close", the low range transfer return flow rate Qh1 is 0, and the low range transfer oil supply flow rate Qd1 to the hydraulic motor HM reaches the maximum, and the low range transfer FD1 is in "full split" state. In the "full transfer" state of the low range transfer FD1, the low range switch valve VC1 is shifted from its right position to its left position, which causes the low range transfer FD1 to stall, lose transfer function and be in a state similar to the "engaged" state of the clutch. Similarly, when the high-gear driving end IM2 has power input and the high-gear driving end IM2 and the high-gear driven end DM2 have a difference in rotational speed, the high-gear throttle valve VD2 is "fully opened", and when the high-gear throttle valve is adjusted from "fully opened" to "fully closed" and "fully closed", the high-gear transfer case FD2 can be in "disengaged", "half-coupled" and "fully-split" states, respectively, and the high-gear switching valve VC2 is shifted from its right position to its left position in the "fully-split" state of the high-gear transfer case FD2, so that the high-gear transfer case FD2 can be in an "engaged" state, and the high-gear driven end DM2 correspondingly outputs the high-gear driven shaft rotational speed No2 and the high-gear driven shaft torque Mo2 through the high-gear driven shaft DZ2.

5. In the above scheme, referring to fig. 1, when the low range transfer FD1 is in the "full transfer" state and pressure oil is supplied to the hydraulic motor HM, the motor displacement is gradually reduced to increase the motor shaft rotation speed Nm and reduce the motor shaft torque Mm, but when the motor displacement is adjusted to 0, the pressure oil cannot pass through the hydraulic motor HM, so that the motor shaft rotation speed Nm and the motor shaft torque Mm are both 0, and at the same time, the low range transfer FD1 forms a stall due to the inability to output oil, loses the transfer function, and enters the "engaged" state. Similarly, when the high range transfer FD2 is in the "full transfer" state and pressurized oil is being supplied to the hydraulic motor HM, the motor displacement is adjusted to 0 and the high range transfer FD2 is also brought to the "engaged" state.

6. In the above-described embodiment, referring to fig. 1, when the low gear is shifted to the high gear, the power is transferred to the high gear by the high gear clutch FD 72, when the low gear is in the direct transmission state when the low gear FD1 is in the "engaged" state, the low gear clutch SS1 is "engaged", the low gear switching valve VC1 is "off", the low gear throttle VD1 is "fully closed", the low gear FD1 is blocked, the overrunning clutch SC is disengaged, the power input by the input shaft IZ (i.e., the input rotation speed Ni and the input torque Mi) is transferred to the high gear by the input gear Ci, the low gear input gear C11, the low gear clutch FD1, the low gear input shaft IZ1, the low gear separator FD1, the low gear driven shaft DZ1, the low gear drive gear C1, the low gear drive gear 1, the power transfer ratio is increased by the high gear input hydraulic pressure input shaft VC No of the high gear FD clutch FD1, the high gear clutch FD is increased when the high gear FD is switched to the high gear input shaft FD1, the high gear FD, the high gear input hydraulic power transfer mode is performed by the high gear FD clutch FD1, the high gear input shaft FD clutch FD1, the high gear input hydraulic pressure is increased, the high gear driving mode 1, the high gear driving power transfer mode 1 is increased, the high gear driving mode 1, the high gear driving mode 36driving mode is increased, the high gear input shaft 3675 is increased, the high gear FD1, the high gear driving mode 36driving mode 3675 is increased, the high gear stage 36driving mode is increased, the high gear stage 36driving mode is increased, the high gear stage 36driving mode is increased by the high gear stage 36driving mode is increased, the high gear stage 36driving mode is increased by the high gear stage 36driving mode 1, the high gear stage 36driving mode is increased by the high gear stage 36driving mode is increased by the high gear stage 36driving mode high gear stage FD 36driving mode high gear stage FD 36.

In the above-described aspect, when the high-gear shift is performed to the low-gear shift, when the high-gear shift FD2 is operated in the double-flow transmission state, after engaging the low-gear meshing sleeve SS1, the displacement of the hydraulic motor HM and the opening of the high-gear throttle VD2 are simultaneously increased to decrease the rotational speed of the output shaft OZ until the rotational speed of the low-gear driven end DM1 becomes No1 ═ No2 × i1 ÷ i2, the low-gear switching valve VC1 is "blocked" to start the establishment of oil pressure inside the low-gear shift FD1, a part of the power input from the input shaft IZ is transmitted to the output shaft OZ in a direct transmission manner through the low-gear shift FD1, the internal oil pressure of the low-gear shift FD1 is increased as the opening of the high-gear throttle VD2 is continuously increased, the ratio of the power transmitted through the low-gear shift FD1 is also increased, the ratio of the power transmitted through the high-gear shift FD2 is reduced, when the opening of the high-gear throttle 2 reaches the full-gear shift, the FD2, and the high-gear shift transmission path is completely interrupted by the high-gear shift transmission system 3642, and the high-gear shift is transmitted to the high-gear shift notch 2.

Due to the adoption of the technical scheme, the beneficial technical effects of the invention are embodied in the following aspects:

1. the combined type double-flow variable-speed transmission device provided by the invention combines two sets of hydraulic-mechanical double-flow transmission systems into one system by using the principle of a double-clutch transmission, can realize uninterrupted power shifting, is favorable for ensuring the transmission continuity and the shifting smoothness in the shifting process, and improves the shifting quality.

2. The invention relates to a combined double-flow variable-speed transmission device, which adopts a positive displacement hydraulic pump capable of rotating integrally relative to a system shell as a transfer case, has the characteristics of simple structure, convenience in transmission system arrangement and the like relative to a transfer case formed by combining the conventional hydraulic pump and a planetary mechanism, and is beneficial to reducing the manufacturing cost of the system.

3. The combined double-flow variable-speed transmission device can realize the functions of interrupting transmission, starting, accelerating, shifting and the like of the variable-speed transmission device by performing different controls on the displacement of each meshing sleeve, each switching valve, each throttle valve and each hydraulic motor.

In a word, the combined type double-flow variable speed transmission device has the gear shifting function of the double clutches, can transmit power in three transmission modes of hydraulic transmission, hydraulic-mechanical double-flow transmission and mechanical transmission, has the characteristics of stepless speed regulation of hydraulic transmission and high efficiency of mechanical transmission in the transmission process, and can better meet the requirements of vehicles, particularly engineering machinery, agricultural machinery and other complex and changeable use conditions of driving conditions.

Drawings

Fig. 1 is a schematic structural diagram of a compound double-flow variable transmission device according to the present invention.

Reference numerals: a1. an oil inlet of the low-gear transfer case; a2. an oil inlet of the high-gear transfer case; ac1, a low-gear switch valve inlet; ac2, a high-gear switch valve inlet; ad1, a low range throttle inlet; ad2, a high-range throttle valve inlet; as3, inlet of a low-gear check valve; as4, an inlet of a high-grade check valve; b1. an oil discharge port of the low-gear transfer case; b2. an oil discharge port of the high-gear transfer case; bc1, a low-gear switch valve outlet; bc2, high-gear switch valve outlet; bd1, low range throttle outlet; bd2. high range throttle valve outlet; bs3. low range check valve outlet; bs4. high check valve outlet; ci. input gear; C11. a low range input gear; C12. a low range drive gear; c13, a low-gear driven gear; C21. a high-gear input gear; C22. a high gear drive gear; C23. a high-gear driven gear; cm1. motor drive gear; cm2. motor driven gear; DM1, low-gear driven end; DM2. high-gear driven end; DZ1. low range driven shaft; DZ2. high-gear driven shaft; FD1, low range transfer case; FD2. high range transfer case; f1. low range split point; f2. a high gear split point; HM. a hydraulic motor; IZ. an input shaft; IM1, a low-gear driving end; IM2. a high-gear driving end; IZ1, a low-gear input shaft; IZ2. a high-gear input shaft; i1. a low gear transmission ratio; i2. a high gear transmission ratio; im. motor output gear ratio; j1. a low-gear inlet confluence point; j2. a high-gear inlet confluence point; KT. a housing; mi. input torque; mo1. low gear driven shaft torque; mo2. high gear driven shaft torque; MZ. a motor shaft; mm. motor shaft torque; mo, output torque; ni. input speed; no1. low gear driven shaft speed; no2. high gear driven shaft speed; nm. motor shaft speed; no. output rotation speed; OZ. an output shaft; p. a confluence point; qd1, oil supply flow of the low-gear transfer case; qd2, oil supply flow of the high-gear transfer case; qh1. low range transfer case reflux; qh2. high-gear transfer case reflux amount; sa1, sealing the low gear oil inlet; sa2, sealing the high-gear oil inlet; sb1, low-gear oil drainage sealing; sb2, high-gear oil drainage sealing; SC. an overrunning clutch; SS1. low range sleeve; SS2. high gear engaging sleeve; vc1, a low range switching valve; vc2. high range switching valve; vd1 low range throttle; VD2. high range throttle valve; vs1, low-range check valve; VS2, high-gear check valve; vs3, low-range check valve; vs4, high-stop check valve; and T, an oil tank.

Detailed Description

The invention will now be further described, by way of example, with reference to the accompanying drawings in which:

example (b): combined double-flow variable-speed transmission device

As described with reference to fig. 1, the device is mainly composed of an input transmission module, a low range transfer FD1, a low range hydraulic transmission module, a low range mechanical transmission module, a high range transfer FD2, a high range hydraulic transmission module, a high range mechanical transmission module, a hydraulic motor HM, a motor output transmission module, and an output shaft OZ.

The input transmission module consists of an input shaft IZ, an input gear Ci, a low-gear input gear C11, a low-gear input shaft IZ1, a low-gear meshing sleeve SS1, a high-gear input gear C21, a high-gear input shaft IZ2 and a high-gear meshing sleeve SS2.

The input shaft IZ is pivotally supported on the casing KT of the transmission, and the input gear Ci is fixedly arranged at one end of the input shaft IZ and is simultaneously meshed with the low-gear input gear C11 and the high-gear input gear C21.

The low-gear input gear C11 has a central axis and is rotatably supported on the casing KT with its central axis; the low-gear input shaft IZ1 is coaxially arranged with the low-gear input gear C11, the low-gear engaging sleeve SS1 is sleeved at one end of the low-gear input shaft IZ1 and can axially slide along the low-gear input shaft IZ1, when the low-gear engaging sleeve SS1 slides to one side of the low-gear input gear C11 and is combined with the low-gear input gear C11, the low-gear input gear C11 is in transmission connection with the low-gear input shaft IZ1, and when the low-gear engaging sleeve SS1 slides to the other side, the low-gear input gear C11 is disconnected from the low-gear input shaft IZ1.

The high-gear input gear C21 has a central shaft and is rotatably supported on the casing KT by the central shaft; the high-gear input shaft IZ2 and the high-gear input gear C21 are coaxially arranged, the high-gear engaging sleeve SS2 is sleeved at one end of the high-gear input shaft IZ2 and can axially slide along the high-gear input shaft IZ2, when the high-gear engaging sleeve SS2 slides to one side of the high-gear input gear C21 and is combined with the high-gear input gear C21, the high-gear input gear C21 is in transmission connection with the high-gear input shaft IZ2, and when the high-gear engaging sleeve SS2 slides to the other side, the high-gear input gear C21 is disconnected from the high-gear input shaft IZ2.

The low-gear transfer case FD1 mainly comprises a low-gear displacement pump, a low-gear oil inlet seal Sa1 and a low-gear oil outlet seal Sb1, wherein a rotor of the low-gear displacement pump is used as a low-gear driving end IM1 of the low-gear transfer case FD1 and is in transmission connection with a low-gear input shaft IZ1, and a stator of the low-gear displacement pump is used as a low-gear driven end DM1 of the low-gear transfer case FD1 and is in rotary support relative to a casing KT; the low-gear oil inlet seal Sa1 is a rotary seal channel for the low-gear displacement pump to feed oil, the rotary seal channel is provided with a low-gear oil inlet fixed port and a low-gear oil inlet rotary port, the low-gear oil inlet rotary port is connected with an oil inlet of the low-gear displacement pump and communicated with a low-pressure cavity of the low-gear displacement pump, and the low-gear oil inlet fixed port is used as an oil inlet a1 of a low-gear transfer case; the low-gear oil discharge seal Sb1 is a rotary seal channel for discharging oil from the low-gear displacement pump, and the rotary seal channel has a low-gear oil discharge fixed port and a low-gear oil discharge rotary port, the low-gear oil discharge rotary port is connected with the oil discharge port of the low-gear displacement pump and communicated with a high-pressure cavity of the low-gear displacement pump, and the low-gear oil discharge fixed port is used as a low-gear transfer case oil discharge port b1.

The low-range hydraulic transmission module comprises a low-range one-way valve VS1, a low-range switching valve VC1, a low-range throttle valve VD1 and a low-range check valve VS3.

The low-gear one-way valve VS1 is communicated with an oil path from the oil tank T to the direction of the oil inlet a1 of the low-gear transfer case in a one-way mode, and a low-gear inlet confluence point j1 is arranged between the low-gear one-way valve VS1 and the oil inlet a1 of the low-gear transfer case.

The low-gear switch valve VC1 is a two-position two-way switch valve and has a low-gear switch valve inlet ac1 and a low-gear switch valve outlet bc1, a low-gear splitter oil outlet b1 extends outward to form an oil discharge line, the oil discharge line is sequentially provided with a low-gear splitting point f1 and a confluence point p, a low-gear switch valve VC1 is connected in series to the oil discharge line between the low-gear splitter oil outlet b1 and the low-gear splitting point f1, the low-gear switch valve inlet ac1 is communicated with the low-gear splitter oil outlet b1, the low-gear switch valve outlet bc1 is communicated with the low-gear splitting point f1, when the low-gear switch valve VC1 is in the left position, the oil path from the low-gear splitter oil outlet b1 to the low-gear splitting point f1 is cut off, and when the low-gear switch valve VC1 is in the right position, the oil path from the low-gear splitter oil outlet b1 to the low-gear splitting point f1 is communicated with the low-gear splitting point VC1.

The low-range throttle valve VD1 is an adjustable throttle valve, the opening adjustment range of which is "fully closed" to "fully open", the low-range throttle valve VD1 has a low-range throttle valve inlet ad1 and a low-range throttle valve outlet bd1, the low-range throttle valve inlet ad1 communicates with the low-range branch point f1, the low-range throttle valve outlet bd1 communicates with the low-range inlet confluence point j1, when the low-range throttle valve VD1 is "fully closed", the oil path from the low-range branch point f1 to the low-range inlet confluence point j1 is cut off, when the low-range throttle valve VD1 is "fully open", the oil path from the low-range branch point f1 to the low-range inlet confluence point j1 is fully conducted, when the low-range throttle valve VD1 is partially opened, the oil path from the low-range branch point f1 to the low-range inlet confluence point j1 is partially conducted, and the conduction degree of the low-range throttle valve VD 35 1 increases as.

The low-range check valve VS3 is a check valve and has a low-range check valve inlet as3 and a low-range check valve outlet bs3, the low-range check valve VS3 communicates with the oil passage in the direction from the low-range branch point f1 to the confluence point p in a one-way manner, the low-range check valve inlet as3 communicates with the low-range branch point f1, and the low-range check valve outlet bs3 communicates with the confluence point p.

The low-gear mechanical transmission module comprises a low-gear driven shaft DZ1, a low-gear driving gear C12 and a low-gear driven gear C13; low fender driven shaft DZ1 slewing bearing is on casing KT, and low fender driven shaft DZ1 one end is connected with the low fender driven end DM1 transmission of low fender transfer case FD1, and the other end is connected with low fender driving gear C12 transmission, and low fender driving gear C12 meshes with low fender driven gear C13 mutually, and low fender driving gear C12 is i1 to low fender drive ratio of low fender driven gear C13, low fender driven gear C13 with output shaft OZ transmission is connected.

The high-gear transfer case FD2 mainly comprises a high-gear displacement pump, a high-gear oil inlet seal Sa2 and a high-gear oil outlet seal Sb2, wherein a rotor of the high-gear displacement pump is in transmission connection with a high-gear input shaft IZ2 as a high-gear driving end IM2 of the high-gear transfer case FD2, and a stator of the high-gear displacement pump is in rotary support relative to a casing KT as a high-gear driven end DM2 of the high-gear transfer case FD 2; the high-gear oil inlet seal Sa2 is a rotary seal channel for oil inlet of the high-gear positive displacement pump, the rotary seal channel is provided with a high-gear oil inlet fixed port and a high-gear oil inlet rotary port, the high-gear oil inlet rotary port is connected with an oil inlet of the high-gear positive displacement pump and communicated with a low-pressure cavity of the high-gear positive displacement pump, and the high-gear oil inlet fixed port is used as an oil inlet a2 of a high-gear transfer case; the high-gear oil discharge seal Sb2 is a rotary seal channel for discharging oil of the high-gear displacement pump, the rotary seal channel is provided with a high-gear oil discharge fixed port and a high-gear oil discharge rotary port, the high-gear oil discharge rotary port is connected with an oil discharge port of the high-gear displacement pump and communicated with a high-pressure cavity of the high-gear displacement pump, and the high-gear oil discharge fixed port is used as a high-gear transfer case oil discharge port b2.

The high-gear hydraulic transmission module comprises a high-gear one-way valve VS2, a high-gear switch valve VC2, a high-gear throttle valve VD2 and a high-gear check valve VS4.

The high-gear one-way valve VS2 is communicated with an oil path from the oil tank T to the direction of the oil inlet a2 of the high-gear transfer case in a one-way mode, and a high-gear inlet confluence point j2 is arranged between the high-gear one-way valve VS2 and the oil inlet a2 of the high-gear transfer case.

The high-gear switch valve VC2 is a two-position two-way switch valve and is provided with a high-gear switch valve inlet ac2 and a high-gear switch valve outlet bc2, an oil discharge oil way extends outwards from a high-gear splitter oil discharge port b2, a high-gear splitting point f2 is arranged on the oil discharge oil way, the high-gear switch valve VC2 is connected in series to the oil discharge oil way between a high-gear splitter oil discharge port b2 and a high-gear splitting point f2, the high-gear switch valve inlet ac2 is communicated with a high-gear splitter oil discharge port b2, the high-gear switch valve outlet bc2 is communicated with a high-gear splitting point f2, when the high-gear switch valve VC2 is in the left position, the oil way from the high-gear splitter oil discharge port b2 to the high-gear splitting point f2 is cut off, when the high-gear switch valve VC2 is in the right position, the oil way from the high-gear splitter oil discharge port b2 to the high-gear splitting point f2 is communicated, and the initial position of the high-gear switch.

The high-gear throttle valve VD2 is an adjustable throttle valve, the opening adjusting range of the adjustable throttle valve is from full close to full open, the high-gear throttle valve VD2 is provided with a high-gear throttle valve inlet ad2 and a high-gear throttle valve outlet bd2, the high-gear throttle valve inlet ad2 is communicated with a high-gear diversion point f2, the high-gear throttle valve outlet bd2 is communicated with a high-gear inlet confluence point j2, when the high-gear throttle valve VD2 is in full close, an oil path from the high-gear diversion point f2 to the high-gear inlet confluence point j2 is cut off, when the high-gear throttle valve VD2 is in full open, an oil path from the high-gear diversion point f2 to the high-gear inlet confluence point j2 is completely communicated, when the high-gear throttle valve 2 is partially open, an oil path from the high-gear diversion point f2 to the high-gear inlet confluence point j2 9 is partially communicated, and the communication degree of the adjustable throttle valve VD is increased along.

The high-level check valve VS4 is a one-way valve and has a high-level check valve inlet as4 and a high-level check valve outlet bs4, the high-level check valve VS4 is communicated with the oil path from the high-level diversion point f2 to the confluence point p in a one-way mode, the high-level check valve inlet as4 is communicated with the high-level diversion point f2, and the high-level check valve outlet bs4 is communicated with the confluence point p.

The high-gear mechanical transmission module comprises a high-gear driven shaft DZ2, a high-gear driving gear C22 and a high-gear driven gear C23; high fender driven shaft DZ2 slewing bearing is on casing KT, and high fender driven shaft DZ2 one end is connected with the high fender driven end DM2 transmission of high fender transfer case FD2, and the other end is connected with high fender driving gear C22 transmission, and high fender driving gear C22 meshes with high fender driven gear C23 mutually, and high fender driving gear C22 is i2 to the high fender drive ratio of high fender driven gear C23, high fender driven gear C23 with output shaft OZ transmission is connected.

The hydraulic motor HM is a positive displacement variable displacement hydraulic motor, a stator of the hydraulic motor HM is fixedly arranged on the casing KT, the hydraulic motor HM is provided with an oil inlet and an oil outlet, the confluence point p is communicated with the oil inlet of the hydraulic motor HM, and the oil outlet of the hydraulic motor HM is communicated with the oil tank T.

The motor output transmission module includes an overrunning clutch SC, a motor shaft MZ, a motor drive gear Cm1, and a motor driven gear Cm2.

The overrunning clutch SC has the characteristic of unidirectional power transmission and is provided with a driving end and a driven end, the driving end of the overrunning clutch SC is in transmission connection with a motor shaft MZ, the motor shaft MZ is rotatably supported on a shell KT, the motor shaft MZ is in transmission connection with a rotor of a hydraulic motor HM, the driven end of the overrunning clutch SC is fixedly arranged on a motor driving gear Cm1, when the hydraulic motor HM outputs rotating speed through the motor shaft MZ and the output rotating speed has a trend of exceeding the rotating speed of the motor driving gear Cm1, the overrunning clutch SC is combined, the power of the hydraulic motor HM is transmitted to the motor driving gear Cm1, and when the rotating speed of the motor shaft MZ is lower than the rotating speed of the motor driving gear Cm1, the overrunning clutch SC is separated and interrupts the motor shaft MZ to transmit power to the motor driving gear Cm 1; the motor driving gear Cm1 is meshed with the motor driven gear Cm2, the motor driving gear Cm1 is im in the transmission ratio of motor output to the motor driven gear Cm2, the motor driven gear Cm2 is in transmission connection with the output shaft OZ, and the output shaft OZ is rotatably supported on the shell KT.

The working principle of the embodiment is as follows:

referring to fig. 1, the initial state of a compound dual flow variable transmission of the present invention is: the low gear meshing sleeve SS1 and the high gear meshing sleeve SS2 are both separated, the low gear switch valve VC1 and the high gear switch valve VC2 are both conducted, the low gear throttle valve VD1 and the high gear throttle valve VD2 are both fully opened, and the displacement of the hydraulic motor HM is adjusted to be maximum. When the invention is applied to a vehicle transmission system, the specific process of controlling the power transmission is as follows:

1. neutral gear of vehicle

However, in order to facilitate the subsequent vehicle starting operation, the low gear sleeve SS1 may be engaged first, allowing the power input from the input shaft IZ to be transmitted to the low gear active end IM1 through the input gear Ci, the low gear input gear C11, the low gear sleeve SS1 and the low gear input shaft IZ1, and the low gear transfer FD1 sucks and discharges oil, and since the low gear switch valve VC1 is "on" and the low gear throttle VD1 is "fully opened" at this time, all the oil discharged from the low gear transfer FD1 flows back to the low gear transfer oil inlet port 63a 1 through the low gear switch valve VC1 and the low gear throttle VD1, and since the low gear transfer FD1 cannot establish oil pressure therein and is in the "disengaged" state, power is not transmitted, and a neutral gear is formed.

2. Vehicle launch

Normally, when the vehicle is started in a low gear, under the conditions of "engagement" of the low gear meshing sleeve SS1 and suction and discharge of oil from the low gear shift FD1, the opening degree of the low gear throttle valve VD1 is gradually reduced, oil pressure is gradually built up inside the low gear shift FD1 and pressure oil is supplied to the low gear split point f1, when the oil pressure reaches the opening pressure of the low gear check valve VS3, the low gear check valve VS3 is turned on, pressure oil output from the low gear shift FD1 is split by the low gear split point f1, a part of the pressure oil still flows back to the low gear shift inlet 685a 1 through the low gear throttle valve VD1, another part of the pressure oil is supplied to the hydraulic motor HM through the low gear check valve VS3, and the motor shaft MZ is driven to form the motor shaft torque Mm and the rotation trend, at this time, the rotation speeds of the motor driving gear Cm1, the motor driven gear Cm2 and the output shaft MZ are all 0, the motor driving gear Cm is "engaged", the motor over-shaft clutch SC "m" and the motor driving gear Cm "84, The motor driven gear Cm2 and the overrunning clutch SC are transmitted to the output shaft OZ, at the same time, under the action of the internal pressure oil of the low-gear transfer FD1, the low-gear driven end DM1 transmits the low-gear driven shaft torque Mo1 formed by the low-gear driven shaft DZ1 to enable the low-gear driven shaft DZ1 to generate a rotation trend, after the low-gear driven shaft torque Mo1 is transmitted to the output shaft OZ through the low-gear driving gear C12 and the low-gear driven gear C13, the low-gear driven shaft torque Mo converges with the torque output by the hydraulic motor HM to form an output torque Mo for the output shaft OZ, the output torque Mo continuously increases along with the reduction of the opening degree of the low-gear throttle valve VD1, when the output torque Mo increases enough to overcome the vehicle starting resistance, and the low-gear throttle valve 1 reaches "full-close", the vehicle starts, and the variable speed transmission device is in.

3. Acceleration of vehicle

After the vehicle is started, the speed change transmission device is in a hydraulic-mechanical double-flow transmission state, and the vehicle can be accelerated by the following methods: the method comprises the steps that firstly, the displacement of a hydraulic motor HM is kept unchanged, and power input is continuously increased; the second method is that the power input is continuously increased, and the displacement of the hydraulic motor HM is reduced; and the third method is to keep the power input unchanged and continuously reduce the displacement of the hydraulic motor HM.

In the second and third methods, since the motor shaft rotation speed Nm of the motor shaft MZ is the ratio of the low range transfer oil supply flow rate Qd1 to the displacement of the hydraulic motor HM (that is, Nm is Qd 1/displacement of the hydraulic motor), the overrunning clutch SC can be ensured to be always "engaged" as long as the displacement of the hydraulic motor HM is reduced and Nm is always maintained to be equal to or greater than Nm No × im, and the output rotation speed No of the variable speed transmission in the hydraulic-mechanical dual flow transmission state is continuously increased to accelerate the vehicle, regardless of whether the low range transfer oil supply flow rate Qd1 supplied to the hydraulic motor HM by the low range transfer FD1 is changed.

In the hydro-mechanical two-flow transmission regime, when the displacement of the hydraulic motor HM is adjusted to 0, the low range divider FD1 is "engaged" due to stalling, and the variable speed drive is put into a direct drive regime, in which the vehicle can only be accelerated by increasing the power input.

4. Low gear shift into high gear

When the low gear is in the direct drive state, the low gear mesh sleeve SS1 is engaged, the low gear switch valve VC1 is turned off, the low gear throttle valve VD1 is fully closed, the low gear separator FD1 is locked, the overrunning clutch SC is disengaged, the power input by the input shaft IZ is transmitted to the output shaft OZ through the input gear Ci, the low gear input gear C1, the low gear mesh sleeve SS1, the low gear input shaft IZ1, the low gear separator FD1, the low gear driven shaft d1, the low gear drive gear VC1, the high gear throttle valve VD1 is turned on, the hydraulic motor 1 is adjusted to the maximum value, the high gear mesh sleeve 1 is engaged, the power input by the input gear IZ is engaged, the high gear drive gear FD, the power input gear Ci, the low gear driven gear C1 is engaged, the high gear mesh ratio of the high gear 1, the high gear drive gear 1 is increased, the high gear mesh ratio of the high gear mesh clutch 1, the high gear mesh ratio of the high gear drive gear 1 is increased, the high gear mesh ratio of the high gear 1, the high gear mesh clutch 1, the high gear drive gear 1 is increased, the high gear mesh ratio of the high gear mesh clutch 1, the high gear mesh ratio of the high gear drive gear 1 is increased by the high gear mesh clutch 1, the high gear mesh clutch 1 is increased by the high gear mesh clutch 1, the high gear mesh clutch 1, the high gear mesh 1 is increased by the high gear mesh clutch 1, the high gear mesh clutch 1, the high gear mesh 1 is increased by the high gear mesh 1, the high gear mesh 36mesh 1, the high gear mesh 1 is increased by the high gear mesh 1, the high gear mesh clutch 1, the high gear mesh 1, the high gear mesh 1 is increased by the high gear mesh 1, the high gear mesh 1 is increased by the high gear mesh 1, the high gear mesh.

After the transmission is shifted to the high gear, the transmission operates in the dual-flow transmission state, and in order to accelerate the vehicle, the control process is similar to that of the second method and the third method in the above-mentioned 3, which is not described herein again.

When the displacement of the hydraulic motor HM is adjusted to 0, the high range divider FD1 is "engaged" due to stalling, and the transmission is shifted into a direct drive state, in which the vehicle can only be accelerated in a manner that increases the power input, as in the case of a transmission operating in low range.

5. High gear shifting into low gear

When the high gear is in a double-flow transmission state, the low gear mesh sleeve SS1 is engaged, then the displacement of a hydraulic motor HM and the opening degree of a high gear throttle VD2 are simultaneously increased, the rotating speed of an output shaft OZ is reduced until the rotating speed of a low gear driven end DM1 is No 1-No 2 × i1 ÷ i2, a low gear switch valve VC1 is cut off, oil pressure is built inside a low gear transfer FD1, part of power input by an input shaft IZ is transmitted to the output shaft OZ in a direct transmission mode through a low gear transfer FD1, the oil pressure inside a low gear transfer FD 48 is continuously increased along with the continuous opening degree of a high gear throttle VD2, the FD ratio of power transmission through the low gear transfer FD1 is also continuously increased, the ratio of power transmission through the high gear transfer FD2 is continuously reduced, when the opening degree of a high gear throttle VD2 reaches a full opening degree, the FD ratio of power transmission through the low gear transfer FD 635826 is continuously increased, and the high gear transfer is completely disconnected from the high gear mesh sleeve FD 23, and the high gear transfer is completed by the high gear transfer route FD 638.

The above example only shows a typical embodiment of the present invention, and in fact, there are other variations and extensions of the present invention, and the following is described for the variations and extensions that may occur in the present invention:

1. in the above embodiment, the compound hydro-mechanical dual flow transmission has two gears, i.e. high and low gears, but it cannot be determined that the invention has only two gears. If a pair of gear pairs can be added between the low-gear driven shaft DZ1 and the output shaft OZ, and the gear shifting can be realized by adding synchronizers and other structures with the low-gear driving and driven gear pairs C12 and C13. Therefore, in claim 1 of the present invention, the connection relationship between the low gear drive gear C12 and the low gear driven gear C13 and the connection relationship between the high gear drive gear C22 and the high gear driven gear C23 are defined as "transmission connection". It follows that a variable speed drive output of more than two gears can be achieved based on the basic principles of the present invention, as will be appreciated by those skilled in the art.

2. In the above embodiments, the compound hydraulic-mechanical double flow transmission device does not describe the reverse gear condition, and the reverse gear can be additionally installed according to the vehicle running requirement. The reverse gear may be implemented in various forms, for example, by adding a corresponding reverse gear pair to the motor shaft MZ of the hydraulic motor HM, by adding a corresponding gear pair to the low-gear driven shaft DZ1 and the high-gear driven shaft DZ2, or by connecting the low-gear drive gear C12 and the high-gear driven gear C23 through gears. Of course, the reverse gear can be arranged within the solution according to the invention or outside the transmission system according to the invention, so that a reverse gear is not necessary for the invention, and is therefore not further defined in claim 1 of the present invention. As will be readily understood by those skilled in the art.

3. In the above embodiments, the transmission control of the combined hydraulic-mechanical dual-flow transmission device is implemented by a hydraulic control system, and the hydraulic control system has various forms, and may be simple or complex, so that only the basic principle and implementation process of the present invention are described in the above description of examples, and the hydraulic control system can implement the control of the variable speed transmission device of the present invention as long as it meets the control requirements of the present invention.

4. In the above embodiments, the low range divider FD1 and the high range divider FD2 are vane-type fixed displacement pumps, crescent gear pumps, gerotor pumps, or axial plunger fixed displacement pumps.

5. In the above embodiments, the hydraulic motor HM is a single-acting vane type variable displacement motor, or an axial plunger type variable displacement motor.

6. In the above embodiments, the overrunning clutch SC is a roller type overrunning clutch, or a ball type overrunning clutch, or a ratchet and pawl type overrunning clutch, or a wedge type overrunning clutch.

The above embodiments are merely illustrative of the technical ideas and features of the present invention, and the purpose thereof is to enable those skilled in the art to understand the contents of the present invention and implement the present invention, and not to limit the protection scope of the present invention. All equivalent changes and modifications made according to the spirit of the present invention should be covered within the protection scope of the present invention.

Claims (4)

1. A compound dual flow variable speed drive, characterized by: the hydraulic transmission device mainly comprises an input transmission module, a low-gear transfer case (FD 1), a low-gear hydraulic transmission module, a low-gear mechanical transmission module, a high-gear transfer case (FD 2), a high-gear hydraulic transmission module, a high-gear mechanical transmission module, a Hydraulic Motor (HM), a motor output transmission module and an output shaft (OZ);

the input transmission module consists of an input shaft (IZ), an input gear (Ci), a low-gear input gear (C11), a low-gear input shaft (IZ 1), a low-gear meshing sleeve (SS 1), a high-gear input gear (C21), a high-gear input shaft (IZ 2) and a high-gear meshing sleeve (SS 2);

the input shaft (IZ) is rotatably supported on a shell (KT) of the transmission device, and the input gear (Ci) is fixedly arranged on the input shaft (IZ) and is simultaneously meshed with the low-gear input gear (C11) and the high-gear input gear (C21);

the low-gear input gear (C11) is provided with a central shaft and is rotatably supported on the shell (KT) by the central shaft; the low-gear input shaft (IZ 1) and the low-gear input gear (C11) are coaxially arranged, the low-gear meshing sleeve (SS 1) is sleeved at one end of the low-gear input shaft (IZ 1) and can axially slide along the low-gear input shaft (IZ 1), when the low-gear meshing sleeve (SS 1) slides to one side of the low-gear input gear (C11) and is combined with the low-gear input gear (C11), the low-gear input gear (C11) and the low-gear input shaft (IZ 1) form transmission connection, and when the low-gear meshing sleeve (SS 1) slides to the other side, the low-gear input gear (C11) and the low-gear input shaft (IZ 1) are disconnected;

the high-gear input gear (C21) is provided with a central shaft and is rotatably supported on the shell (KT) by the central shaft; the high-gear input shaft (IZ 2) and the high-gear input gear (C21) are coaxially arranged, the high-gear meshing sleeve (SS 2) is sleeved at one end of the high-gear input shaft (IZ 2) and can axially slide along the high-gear input shaft (IZ 2), when the high-gear meshing sleeve (SS 2) slides to one side of the high-gear input gear (C21) and is combined with the high-gear input gear (C21), the high-gear input gear (C21) and the high-gear input shaft (IZ 2) form transmission connection, and when the high-gear meshing sleeve (SS 2) slides to the other side, the high-gear input gear (C21) and the high-gear input shaft (IZ 2) are disconnected;

the low-gear transfer case (FD 1) mainly comprises a low-gear displacement pump, a low-gear oil inlet seal (Sa 1) and a low-gear oil outlet seal (Sb 1), wherein a rotor of the low-gear displacement pump is used as a low-gear driving end (IM 1) of the low-gear transfer case (FD 1) and is in transmission connection with a low-gear input shaft (IZ 1), and a stator of the low-gear displacement pump is used as a low-gear driven end (DM 1) of the low-gear transfer case (FD 1) and is in rotary support relative to a shell (KT); the low-gear oil inlet seal (Sa 1) is a rotary seal channel for low-gear displacement pump oil inlet, the rotary seal channel is provided with a low-gear oil inlet fixed port and a low-gear oil inlet rotary port, the low-gear oil inlet rotary port is connected with the oil inlet of the low-gear displacement pump and communicated with a low-pressure cavity of the low-gear displacement pump, and the low-gear oil inlet fixed port is used as the oil inlet (a 1) of the low-gear transfer case; the low-gear oil drainage seal (Sb 1) is a rotary seal channel for discharging oil of the low-gear displacement pump, the rotary seal channel is provided with a low-gear oil drainage fixed port and a low-gear oil drainage rotary port, the low-gear oil drainage rotary port is connected with an oil drainage port of the low-gear displacement pump and communicated with a high-pressure cavity of the low-gear displacement pump, and the low-gear oil drainage fixed port is used as an oil drainage port (b 1) of the low-gear transfer case;

the low-gear hydraulic transmission module comprises a low-gear one-way valve (VS 1), a low-gear switch valve (VC 1), a low-gear throttle valve (VD 1) and a low-gear check valve (VS 3);

the low-gear one-way valve (VS 1) is communicated with an oil path from an oil tank (T) to the direction of an oil inlet (a 1) of the low-gear transfer case in a one-way mode, and a low-gear inlet confluence point (j 1) is arranged between the low-gear one-way valve (VS 1) and the oil inlet (a 1) of the low-gear transfer case;

the low-gear switch valve (VC 1) is a two-position two-way switch valve and is provided with a low-gear switch valve inlet (ac 1) and a low-gear switch valve outlet (bc 1), a low-gear transfer case oil discharge port (b 1) extends outwards to form an oil discharge oil path, a low-gear splitting point (f 1) and a merging point (p) are sequentially arranged on the oil discharge oil path in sequence, the low-gear switch valve (VC 1) is connected in series on the oil discharge oil path between the low-gear transfer case oil discharge port (b 1) and the low-gear splitting point (f 1), the low-gear switch valve inlet (ac 1) is communicated with the low-gear transfer case oil discharge port (b 1), the low-gear switch valve outlet (bc 1) is communicated with the low-gear splitting point (f 1), when the low-gear switch valve (VC 1) is in the left position, the oil path from the low-gear transfer case oil discharge port (b 1) to the low-gear splitting point (f 1) is cut off, when the low-gear switch valve (VC 1) is in the right position, the low-gear splitting point (VC 1 9) is communicated with the low-gear splitting point (VC, the initial position of the low-gear switch valve (VC 1) is 'on';

the low-gear throttle valve (VD 1) is an adjustable throttle valve, the opening degree adjusting range is from full close to full open, the low-gear throttle valve (VD 1) is provided with a low-gear throttle valve inlet (ad 1) and a low-gear throttle valve outlet (bd 1), the low-gear throttle valve inlet (ad 1) is communicated with a low-gear diversion point (f 1), the low-gear throttle valve outlet (bd 1) is communicated with a low-gear inlet confluence point (j 1), when the low-gear throttle valve (VD 1) is completely closed, the oil path from the low-gear splitting point (f 1) to the low-gear inlet confluence point (j 1) is cut off, when the low gear throttle valve (VD 1) is fully opened, the oil path from the low gear splitting point (f 1) to the low gear inlet confluence point (j 1) is completely communicated, when the low-range throttle valve (VD 1) is partially opened, the oil path from the low-range splitting point (f 1) to the low-range inlet confluence point (j 1) is partially communicated, and the communication degree of the oil path is increased along with the increase of the opening degree of the low-range throttle valve (VD 1);

the low-gear check valve (VS 3) is a one-way valve and is provided with a low-gear check valve inlet (as 3) and a low-gear check valve outlet (bs 3), the low-gear check valve (VS 3) is communicated with an oil path from the low-gear splitting point (f 1) to the confluence point (p) in a one-way mode, the low-gear check valve inlet (as 3) is communicated with the low-gear splitting point (f 1), and the low-gear check valve outlet (bs 3) is communicated with the confluence point (p);

the low-gear mechanical transmission module comprises a low-gear driven shaft (DZ 1), a low-gear driving gear (C12) and a low-gear driven gear (C13); the low-gear driven shaft (DZ 1) is rotatably supported on the shell (KT), one end of the low-gear driven shaft (DZ 1) is in transmission connection with a low-gear driven end (DM 1) of a low-gear transfer case (FD 1), the other end of the low-gear driven shaft is in transmission connection with a low-gear driving gear (C12), a low-gear driving gear (C12) is in transmission connection with a low-gear driven gear (C13), and the low-gear driven gear (C13) is in transmission connection with the output shaft (OZ);

the high-gear transfer case (FD 2) mainly comprises a high-gear displacement pump, a high-gear oil inlet seal (Sa 2) and a high-gear oil outlet seal (Sb 2), wherein a rotor of the high-gear displacement pump is used as a high-gear driving end (IM 2) of the high-gear transfer case (FD 2) and is in transmission connection with a high-gear input shaft (IZ 2), and a stator of the high-gear displacement pump is used as a high-gear driven end (DM 2) of the high-gear transfer case (FD 2) and is in rotary support relative to a shell (KT); the high-gear oil inlet seal (Sa 2) is a rotary seal channel for high-gear displacement pump oil inlet, the rotary seal channel is provided with a high-gear oil inlet fixed port and a high-gear oil inlet rotary port, the high-gear oil inlet rotary port is connected with the oil inlet of the high-gear displacement pump and communicated with a low-pressure cavity of the high-gear displacement pump, and the high-gear oil inlet fixed port is used as the oil inlet (a 2) of the high-gear transfer case; the high-gear oil drainage seal (Sb 2) is a rotary seal channel for the oil drainage of the high-gear displacement pump, the rotary seal channel is provided with a high-gear oil drainage fixed port and a high-gear oil drainage rotary port, the high-gear oil drainage rotary port is connected with the oil drainage port of the high-gear displacement pump and communicated with a high-pressure cavity of the high-gear displacement pump, and the high-gear oil drainage fixed port is used as an oil drainage port (b 2) of the high-gear transfer case;

the high-gear hydraulic transmission module comprises a high-gear one-way valve (VS 2), a high-gear switch valve (VC 2), a high-gear throttle valve (VD 2) and a high-gear check valve (VS 4);

the high-gear one-way valve (VS 2) is communicated with an oil path from an oil tank (T) to the direction of an oil inlet (a 2) of the high-gear transfer case in a one-way mode, and a high-gear inlet confluence point (j 2) is arranged between the high-gear one-way valve (VS 2) and the oil inlet (a 2) of the high-gear transfer case;

the high-gear switch valve (VC 2) is a two-position two-way switch valve and is provided with a high-gear switch valve inlet (ac 2) and a high-gear switch valve outlet (bc 2), an oil discharge oil path is arranged on the oil discharge port (b 2) of the high-gear transfer case in an outward extending mode, a high-gear diversion point (f 2) is arranged on the oil discharge oil path, a high-gear switch valve (VC 2) is connected in series on the oil discharge oil path between an oil discharge port (b 2) of the high-gear transfer case and the high-gear diversion point (f 2), an inlet (ac 2) of the high-gear switch valve is communicated with an oil discharge port (b 2) of the high-gear transfer case, an outlet (bc 2) of the high-gear switch valve is communicated with the high-gear diversion point (f 2), when the high-gear switch valve (VC 2) is in the left position, the oil path from the oil outlet (b 2) of the high-gear transfer case to the high-gear diversion point (f 2) is cut off, when the high-gear switch valve (VC 2) is in the right position, the oil path from the oil outlet (b 2) of the high-gear transfer case to the high-gear diversion point (f 2) is conducted, and the initial position of the high-gear switch valve (VC 2) is conducted;

the high-gear throttle valve (VD 2) is an adjustable throttle valve, the opening degree adjusting range is from full close to full open, the high-gear throttle valve (VD 2) is provided with a high-gear throttle valve inlet (ad 2) and a high-gear throttle valve outlet (bd 2), the high-gear throttle valve inlet (ad 2) is communicated with a high-gear diversion point (f 2), the high-gear throttle valve outlet (bd 2) is communicated with a high-gear inlet confluence point (j 2), when the high-gear throttle valve (VD 2) is completely closed, the oil path from the high-gear splitting point (f 2) to the high-gear inlet confluence point (j 2) is cut off, when the high-gear throttle valve (VD 2) is fully opened, the oil path from the high-gear splitting point (f 2) to the high-gear inlet confluence point (j 2) is completely communicated, when the high-gear throttle valve (VD 2) is partially opened, the oil path from the high-gear splitting point (f 2) to the high-gear inlet confluence point (j 2) is partially communicated, and the communication degree of the oil path is increased along with the increase of the opening degree of the high-gear throttle valve (VD 2);

the high-gear check valve (VS 4) is a one-way valve and is provided with a high-gear check valve inlet (as 4) and a high-gear check valve outlet (bs 4), the high-gear check valve (VS 4) is communicated with an oil way from a high-gear splitting point (f 2) to a confluence point (p) in a one-way mode, the high-gear check valve inlet (as 4) is communicated with a high-gear splitting point (f 2), and the high-gear check valve outlet (bs 4) is communicated with the confluence point (p);

the high-gear mechanical transmission module comprises a high-gear driven shaft (DZ 2), a high-gear driving gear (C22) and a high-gear driven gear (C23); the high-gear driven shaft (DZ 2) is rotatably supported on the shell (KT), one end of the high-gear driven shaft (DZ 2) is in transmission connection with a high-gear driven end (DM 2) of a high-gear transfer case (FD 2), the other end of the high-gear driven shaft is in transmission connection with a high-gear driving gear (C22), a high-gear driving gear (C22) is in transmission connection with a high-gear driven gear (C23), and the high-gear driven gear (C23) is in transmission connection with the output shaft (OZ);

the Hydraulic Motor (HM) is a positive displacement variable displacement hydraulic motor, a stator of the Hydraulic Motor (HM) is fixedly arranged on the shell (KT), the Hydraulic Motor (HM) is provided with an oil inlet and an oil outlet, the confluence point (p) is communicated with the oil inlet of the Hydraulic Motor (HM), and the oil outlet of the Hydraulic Motor (HM) is communicated with the oil tank (T);

the motor output transmission module comprises an overrunning clutch (SC), a motor shaft (MZ), a motor drive gear (Cm 1) and a motor driven gear (Cm 2);

the overrunning clutch (SC) has the characteristic of unidirectional power transmission and is provided with a driving end and a driven end, the driving end of the overrunning clutch (SC) is in transmission connection with a motor shaft (MZ), the motor shaft (MZ) is rotatably supported on a shell (KT), the motor shaft (MZ) is in transmission connection with a rotor of a Hydraulic Motor (HM), the driven end of the overrunning clutch (SC) is fixedly arranged on a motor driving gear (Cm 1), when the Hydraulic Motor (HM) outputs a rotational speed through the motor shaft (MZ) that has a tendency to exceed the rotational speed of the motor drive gear (Cm 1), the overrunning clutch (SC) is combined, the power of the Hydraulic Motor (HM) is transmitted to the motor driving gear (Cm 1), when the rotation speed of the motor shaft (MZ) is lower than the rotation speed of the motor driving gear (Cm 1), the overrunning clutch (SC) is separated and interrupts the power transmission of the motor shaft (MZ) to the motor driving gear (Cm 1); the motor driving gear (Cm 1) is meshed with a motor driven gear (Cm 2), the motor driven gear (Cm 2) is in transmission connection with the output shaft (OZ), and the output shaft (OZ) is rotatably supported on a shell (KT).

2. The composite dual flow variable transmission of claim 1, wherein: the low-gear transfer case (FD 1) and the high-gear transfer case (FD 2) are vane type fixed displacement pumps, or internal gear pumps, or cycloid rotor pumps, or axial plunger fixed displacement pumps.

3. The composite dual flow variable transmission of claim 1, wherein: the Hydraulic Motor (HM) is a single-acting vane variable displacement motor or an axial plunger variable displacement motor.

4. The composite dual flow variable transmission of claim 1, wherein: the overrunning clutch (SC) is a roller type overrunning clutch, or a ball type overrunning clutch, or a ratchet pawl type overrunning clutch, or a wedge type overrunning clutch.

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