阅读说明：本技术 一种动力耦合的八挡变速器及其工作方法 (Power-coupled eight-gear transmission and working method thereof ) 是由 周荣斌 罗南昌 雷作钊 陈培健 于 2020-12-31 设计创作，主要内容包括：本发明涉及一种动力耦合的八挡变速器及其工作方法,包括连接在一起的分动箱壳体和四挡变速箱壳体,分动箱壳体内安装有从前端伸出的动力输入轴,分动箱壳体内还安装有多个均布在动力输入轴周围的前中间轴,分动箱壳体前端安装有多台与前中间轴一一对应同轴连接的高速电机；分动箱壳体和四挡变速箱壳体之间设置有动力过渡轴,四挡变速箱壳体内安装有从后端伸出的动力输出轴；前中间轴和动力输入轴之间设置有离合器KF,前中间轴和动力过渡轴之间设置有离合器K5和离合器K6。采用多台高速电机进行动力的耦合,体积更小,工作更加稳定可靠,并且在其中某台高速电机出现故障时,其余高速电机还可以继续工作来保证变速器的运行；并且能够实现多挡动力输出。(The invention relates to a power-coupled eight-gear transmission and a working method thereof, and the power-coupled eight-gear transmission comprises a transfer case shell and a four-gear transmission shell which are connected together, wherein a power input shaft extending out of the front end is installed in the transfer case shell, a plurality of front intermediate shafts uniformly distributed around the power input shaft are also installed in the transfer case shell, and a plurality of high-speed motors which are coaxially connected with the front intermediate shafts in a one-to-one correspondence manner are installed at the front end of the transfer case shell; a power transition shaft is arranged between the transfer case shell and the four-gear transmission case shell, and a power output shaft extending out of the rear end is installed in the four-gear transmission case shell; a clutch KF is arranged between the front intermediate shaft and the power input shaft, and a clutch K5 and a clutch K6 are arranged between the front intermediate shaft and the power transition shaft. The plurality of high-speed motors are used for coupling power, the size is smaller, the work is more stable and reliable, and when one high-speed motor fails, the rest high-speed motors can continue to work to ensure the operation of the transmission; and multi-stage power output can be achieved.)

1. A power-coupled eight speed transmission characterized by: the transfer case comprises a transfer case shell and a four-gear transmission case shell which are connected together, wherein a power input shaft extending out of the front end is installed in the transfer case shell, a plurality of front intermediate shafts which are uniformly distributed around the power input shaft and are parallel to the power input shaft are also installed in the transfer case shell, and a plurality of high-speed motors which are in one-to-one correspondence coaxial connection with the front intermediate shafts are installed at the front end of the transfer case shell; a power transition shaft is arranged between the transfer case shell and the four-gear transmission case shell, and a power output shaft extending out of the rear end is installed in the four-gear transmission case shell; and a clutch KF is arranged between the front intermediate shaft and the power input shaft, and a clutch K5 and a clutch K6 are arranged between the front intermediate shaft and the power transition shaft.

2. The power-coupled eight speed transmission of claim 1, wherein: the power input shaft and the power transition shaft are coaxially connected together and can rotate relatively, and the power transition shaft and the power output shaft are coaxially connected together and can rotate relatively; a plurality of rear intermediate shafts which are uniformly distributed around the power transition shaft and are parallel to the power transition shaft are arranged in the shell of the four-gear transmission, a clutch K1 and a clutch K2 are arranged between the rear intermediate shafts and the power transition shaft, and a clutch K3 and a clutch K4 are arranged between the rear intermediate shafts and the power output shaft.

3. The power-coupled eight speed transmission of claim 2, wherein: a plurality of temperature sensors A are installed on the side walls of the transfer case shell and the four-gear transmission case shell, the number of the temperature sensors A is the same as that of the clutches, the positions of the temperature sensors A correspond to those of the clutches one by one, and the inward probes of the temperature sensors A extend to the positions close to the corresponding clutches.

4. The power-coupled eight speed transmission of claim 1, wherein: oil pans are arranged at the bottoms of the transfer case shell and the four-gear transmission case shell; an upper layer and a lower layer of serpentine radiating pipes are arranged in the oil pan, and a cooling liquid inlet and a cooling liquid outlet which are respectively connected with two ends of the serpentine radiating pipes are arranged at the side part of the oil pan; the side part of the oil pan is also provided with a temperature sensor B, and a probe of the temperature sensor B extends into the oil pan; a plurality of threaded through holes are formed in the bottom of the oil pan, and magnetic plugs are installed in the threaded through holes.

5. The power-coupled eight speed transmission of claim 4, wherein: an oil outlet and an oil return port are formed in the side part of the oil pan, and an oil liquid heating device is installed at the oil outlet; the oil heating device comprises an oil outlet pipe connected to the oil outlet, a heating rod extending into the oil outlet pipe is installed at one end of the oil outlet pipe facing outwards, an oil suction port is formed in the side portion of the oil outlet pipe, and the oil suction port is communicated with an oil pump inlet.

6. The power-coupled eight speed transmission of claim 5, wherein: the oil pump is characterized in that a filter is arranged above the oil outlet pipe, the inlet end of the filter is connected with an oil suction port of the oil outlet pipe, the outlet end of the filter is connected with an L-shaped joint, and the L-shaped joint is connected with an inlet of the oil pump through a hose.

7. The power-coupled eight speed transmission of claim 1, wherein: the transfer case is characterized in that a reinforcing plate which is vertically arranged and perpendicular to the power input shaft is arranged in front of the transfer case shell, a plurality of connecting supports are connected between the reinforcing plate and the rear end of the transfer case shell, and the front end of the high-speed motor is fixed on the reinforcing plate.

8. A hydraulic control system for the power-coupled eight speed transmission of claim 2, wherein: the hydraulic control system comprises a first control oil path connected with first oil chambers of control clutches K1 and K2, a second control oil path connected with second oil chambers of control clutches K2 and K3, a third control oil path connected with third oil chambers of control clutches K5 and K6, and a fourth control oil path connected with a fourth oil chamber of a control clutch KF, wherein the first control oil path, the second control oil path, the third control oil path and the fourth control oil path are arranged in parallel; the first control oil path, the second control oil path and the third control oil path are respectively provided with a proportional valve and a three-position four-way electromagnetic valve, and A, B interfaces of the three-position four-way electromagnetic valve are respectively connected to two ends of the corresponding oil cavity; a proportional valve is arranged on the fourth control oil path; the balance oil way is used for balancing pressure difference at two ends of the first oil cavity, the second oil cavity and the third oil cavity.

9. The hydraulic control system of claim 8, wherein: the first control oil way, the second control oil way, the third control oil way, the fourth control oil way and the balance oil way are connected to an oil tank through a control main oil way, the oil tank is also connected with a lubricating main oil way, a lubricating branch oil way leading to each lubricating oil way is connected to the lubricating main oil way, a filter core, a one-way valve and a two-position two-way electromagnetic valve are arranged on the lubricating main oil way, and a supplementary oil way leading to the control main oil way is also connected between the one-way valve and the two-position two-way electromagnetic valve in a bypassing manner on the lubricating; the balance oil way is provided with a proportional valve and a normally closed two-position three-way electromagnetic valve, 2 interfaces of the two-position three-way electromagnetic valve are connected to one of the lubricating branch oil ways, 3 interfaces of the two-position three-way electromagnetic valve are connected with the proportional valve on the balance oil way, and 1 interface of the two-position three-way electromagnetic valve is respectively connected to T interfaces of the three-position four-way electromagnetic valve on the first control oil way, the second control oil way and the third control oil way.

10. A method of operating a power-coupled eight speed transmission as set forth in claim 2 wherein: (1) power output mode: the front intermediate shaft driven by the high-speed motor and the power input shaft driven by the engine realize power coupling through a clutch KF, and power is transmitted to the power transition shaft through a clutch K5 or a clutch K6 to realize two-gear speed change; the power transition shaft transmits power to the rear intermediate shaft through the clutch K1 or the clutch K2, the rear intermediate shaft transmits the power to the power output shaft through the clutch K3 or the clutch K4, four-gear speed change is achieved, and eight-gear power output is achieved through the whole transmission; (2) and (3) generating mode: the clutch K5 and the clutch K6 are in a disconnected state, the clutch KF is in an engaged state, and a power input shaft driven by an engine drives a high-speed motor to rotate through a front intermediate shaft, so that power generation is realized.

Technical Field

The invention relates to a power coupling eight-gear transmission and a working method thereof.

Background

The existing heavy truck is mostly driven by a hybrid power system, and the hybrid power system is used for carrying out power coupling by additionally arranging a motor on an engine. The conventional hybrid power system adopts a single high-power common motor and an engine to drive a power input shaft to rotate together; the overall length of the transmission is large due to the large size of a high-power common motor (the general power is 350 KW); and when only one drive motor fails, the electric system cannot work.

Disclosure of Invention

In view of the above, the present invention provides a power-coupled eight-gear transmission with smaller size and more stable and reliable operation, and an operating method thereof, which can realize multi-gear power output.

The invention is realized by adopting the following scheme: a power-coupled eight-gear transmission comprises a transfer case shell and a four-gear transmission shell which are connected together, wherein a power input shaft extending out of the front end is installed in the transfer case shell, a plurality of front intermediate shafts which are uniformly distributed around the power input shaft and are parallel to the power input shaft are also installed in the transfer case shell, and a plurality of high-speed motors which are coaxially connected with the front intermediate shafts in a one-to-one correspondence mode are installed at the front end of the transfer case shell; a power transition shaft is arranged between the transfer case shell and the four-gear transmission case shell, and a power output shaft extending out of the rear end is installed in the four-gear transmission case shell; and a clutch KF is arranged between the front intermediate shaft and the power input shaft, and a clutch K5 and a clutch K6 are arranged between the front intermediate shaft and the power transition shaft.

Further, the power input shaft and the power transition shaft are coaxially connected together and can rotate relatively, and the power transition shaft and the power output shaft are coaxially connected together and can rotate relatively; a plurality of rear intermediate shafts which are uniformly distributed around the power transition shaft and are parallel to the power transition shaft are arranged in the shell of the four-gear transmission, a clutch K1 and a clutch K2 are arranged between the rear intermediate shafts and the power transition shaft, and a clutch K3 and a clutch K4 are arranged between the rear intermediate shafts and the power output shaft.

Furthermore, a plurality of temperature sensors A are installed on the side walls of the transfer case shell and the four-gear transmission case shell, the number of the temperature sensors A is the same as that of the clutches, the positions of the temperature sensors A are in one-to-one correspondence, and the inward probes of the temperature sensors A extend to the positions close to the corresponding clutches.

Further, oil pans are arranged at the bottoms of the transfer case shell and the four-gear transmission case shell; an upper layer and a lower layer of serpentine radiating pipes are arranged in the oil pan, and a cooling liquid inlet and a cooling liquid outlet which are respectively connected with two ends of the serpentine radiating pipes are arranged at the side part of the oil pan; and a temperature sensor B is further installed on the side part of the oil pan, and a probe of the temperature sensor B extends into the oil pan.

Furthermore, a plurality of threaded through holes are formed in the bottom of the oil pan, and magnetic plugs are installed in the threaded through holes.

Further, an oil outlet and an oil return port are formed in the side part of the oil pan, and an oil liquid heating device is mounted at the oil outlet; the oil heating device comprises an oil outlet pipe connected to the oil outlet, a heating rod extending into the oil outlet pipe is installed at one end of the oil outlet pipe facing outwards, an oil suction port is formed in the side portion of the oil outlet pipe, and the oil suction port is communicated with an oil pump inlet.

Furthermore, a filter is arranged above the oil outlet pipe, the inlet end of the filter is connected with an oil suction port of the oil outlet pipe, the outlet end of the filter is connected with an L-shaped joint, and the L-shaped joint is connected with an inlet of the oil pump through a hose.

Furthermore, a reinforcing plate which is vertically arranged and perpendicular to the power input shaft is arranged in front of the transfer case shell, a plurality of connecting supports are connected between the reinforcing plate and the rear end of the transfer case shell, and the front end of the high-speed motor is fixed on the reinforcing plate.

The other technical scheme of the invention is as follows: a hydraulic control system for the power-coupled eight-gear transmission comprises a first control oil path connected with first oil chambers of control clutches K1 and K2, a second control oil path connected with second oil chambers of control clutches K2 and K3, a third control oil path connected with third oil chambers of control clutches K5 and K6 and a fourth control oil path connected with a fourth oil chamber of a control clutch KF, wherein the first control oil path, the second control oil path, the third control oil path and the fourth control oil path are arranged in parallel; the first control oil path, the second control oil path and the third control oil path are respectively provided with a proportional valve and a three-position four-way electromagnetic valve, and A, B interfaces of the three-position four-way electromagnetic valve are respectively connected to two ends of the corresponding oil cavity; a proportional valve is arranged on the fourth control oil path; the balance oil way is used for balancing pressure difference at two ends of the first oil cavity, the second oil cavity and the third oil cavity.

Furthermore, the first control oil path, the second control oil path, the third control oil path, the fourth control oil path and the balance oil path are connected to an oil tank through a control main oil path, the oil tank is also connected with a lubrication main oil path, the lubrication main oil path is connected with a lubrication branch oil path leading to each lubrication oil path, a filter element, a check valve and a two-position two-way electromagnetic valve are arranged on the lubrication main oil path, and a supplementary oil path leading to the control main oil path is also connected between the check valve and the two-position two-way electromagnetic valve in a bypassing manner on the lubrication main oil path; the balance oil way is provided with a proportional valve and a normally closed two-position three-way electromagnetic valve, 2 interfaces of the two-position three-way electromagnetic valve are connected to one of the lubricating branch oil ways, 3 interfaces of the two-position three-way electromagnetic valve are connected with the proportional valve on the balance oil way, and 1 interface of the two-position three-way electromagnetic valve is respectively connected to T interfaces of the three-position four-way electromagnetic valve on the first control oil way, the second control oil way and the third control oil way.

Furthermore, a filter element and a one-way valve are also arranged on the control main oil path; and a pressure relief pipeline returning to the oil tank is connected beside the control main oil way, and the pressure relief pipeline is provided with a normally closed throttle valve and an overflow valve which are arranged in parallel.

Further, a pressure measuring sensor A and a filter are connected to the lubricating main oil path; the oil tank is internally provided with a radiator, and the upper side of the oil tank is provided with a ventilation cap.

Furthermore, a filter and a pressure measuring sensor B are arranged on a pipeline between the three-position four-way electromagnetic valve and the corresponding oil cavity of the first control oil path, the second control oil path and the third control oil path; the fourth control oil passage is also provided with a filter and a load cell B on a pipe between the proportional valve and the fourth oil chamber.

The invention also provides another technical scheme that: a method of operating a power-coupled eight speed transmission as described above, (1) power take-off mode: the front intermediate shaft driven by the high-speed motor and the power input shaft driven by the engine realize power coupling through a clutch KF, and power is transmitted to the power transition shaft through a clutch K5 or a clutch K6 to realize two-gear speed change; the power transition shaft transmits power to the rear intermediate shaft through the clutch K1 or the clutch K2, the rear intermediate shaft transmits the power to the power output shaft through the clutch K3 or the clutch K4, four-gear speed change is achieved, and eight-gear power output is achieved through the whole transmission; (2) and (3) generating mode: the clutch K5 and the clutch K6 are in a disconnected state, the clutch KF is in an engaged state, and a power input shaft driven by an engine drives a high-speed motor to rotate through a front intermediate shaft, so that power generation is realized.

Compared with the prior art, the invention has the following beneficial effects:

(1) the plurality of high-speed motors are used for coupling power, the size is smaller, the work is more stable and reliable, and when one high-speed motor fails, the rest high-speed motors can continue to work to ensure the operation of the transmission; and multi-stage power output can be achieved.

(2) The temperature of the clutch can be detected in real time, the detection result is high in accuracy, and a basis is provided for the working condition adjustment of the whole transmission;

(3) a radiator is arranged by utilizing the space in the oil pan, so that the function of reducing the oil temperature is achieved, and the running stability of the transmission is ensured;

(4) when the oil temperature is low excessively, hydraulic oil can be heated to a certain degree through oil liquid heating decoration, the fluidity of the oil can be improved, the oil is not so hard when a hydraulic pump on the transmission pumps oil, and the normal work of the transmission is ensured.

In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail below with reference to specific embodiments and accompanying drawings.

Drawings

FIG. 1 is a longitudinal cross-sectional view of an eight speed transmission in accordance with an embodiment of the present invention;

FIG. 2 is a left side view of FIG. 1;

FIG. 3 is a perspective view of the transfer case of the embodiment of the present invention with the clutch omitted;

FIG. 4 is a longitudinal cross-sectional view of FIG. 3;

FIG. 5 is a transverse cross-sectional view of a four speed transmission in accordance with an embodiment of the present invention;

FIG. 6 is a side view of an oil pan in an embodiment of the invention;

FIG. 7 is a top view of an oil pan in an embodiment of the present invention;

FIG. 8 is a schematic view of the oil heating apparatus according to an embodiment of the present invention;

FIG. 9 is a left side view of FIG. 8;

FIG. 10 is a schematic view showing the overall configuration of a hydraulic control system according to an embodiment of the present invention;

FIG. 11 is a schematic illustration of the configuration of the hydraulic control system of the embodiment of the present invention at transmission main valve block A;

FIG. 12 is a schematic illustration of the configuration of the hydraulic control system of the embodiment of the present invention at the transmission main valve block B;

FIG. 13 is a partial structural view of the lower half of FIG. 10;

the reference numbers in the figures illustrate: 1-oil tank, 2-radiator, 3-ventilation cap, 4-heater, 5-oil absorption filter, 6-high speed motor, 7-constant delivery pump, 8-transmission auxiliary valve block A, 9-20um filter element, 10-10um filter element, 11-throttle valve, 12-overflow valve, 13-pressure measuring joint, 14-pressure measuring sensor C, 15-one-way valve, 16-transmission main valve block A, 17-supplementary oil circuit, 18-proportional valve, 19-three-position four-way electromagnetic valve, 20-pressure measuring sensor B, 21 filter element, 22-two-position three-way electromagnetic valve, 23-two-position two-way electromagnetic valve, 24-transmission auxiliary valve block B, 25-transmission main valve block B, 26-filter, 27-mechanical platform valve block, 28-sensor A, 29-throttling plug, 30-first oil chamber, 31-second oil chamber, 32-third oil chamber, 33-fourth oil chamber, 34-pressure sensor D, 100-transfer case shell, 110-power input shaft, 120-front intermediate shaft, 121-gear A, 122-gear B, 130-clutch KF, 140-clutch K5, 150-clutch K6, 160-gear ring A, 170-gear ring B, 200-four-gear transmission case shell, 210-power transition shaft, 220-power output shaft, 230-rear intermediate shaft, 240-clutch K1, 250-clutch K2, 260-clutch K3, 270-clutch K4, 280-temperature sensor A, 300-high-speed motor, 400-oil pan, 410-serpentine radiating pipe, 420-cooling liquid inlet, 430-cooling liquid outlet, 440-magnetic plug, 450-oil outlet, 451-oil outlet pipe, 452-heating rod, 453-oil suction port, 460-oil return port, 470-filter, 471-L-shaped joint, 472-filter support, 480-temperature sensor B, 490-upper pressing strip, 500-reinforcing plate and 510-connecting support.

Detailed Description

As shown in fig. 1 to 9, a power-coupled eight-gear transmission comprises a transfer case housing 100 and a four-gear transmission housing 200 which are connected together, wherein a power input shaft 110 extending out of the front end is installed in the transfer case housing 100, a plurality of front intermediate shafts 120 which are uniformly distributed around the power input shaft and are parallel to the power input shaft are also installed in the transfer case housing 110, a plurality of high-speed motors 300 which are coaxially connected with the front intermediate shafts in a one-to-one correspondence manner are installed at the front end of the transfer case housing, and the power of the high-speed motors 800 is about 100 KW; a power transition shaft 210 is arranged between the transfer case shell 100 and the four-gear transmission case shell 200, and a power output shaft 220 extending out of the rear end is installed in the four-gear transmission case shell; a clutch KF is arranged between the front intermediate shaft 120 and the power input shaft 110, and a clutch K5 and a clutch K6 are arranged between the front intermediate shaft and the power transition shaft; the front intermediate shaft driven by a high-speed motor and the power input shaft driven by an engine realize power coupling through a clutch KF, then the power is transmitted to the power transition shaft 210 through a clutch K1 or K2, the power transition shaft 210 is transmitted to the rear intermediate shaft through a clutch K1 or K2, the rear intermediate shaft transmits the power to the power output shaft through a clutch K3 or K4, the transfer case realizes two-gear speed change through clutches K5 and K6, the four-gear speed change case realizes four-gear speed change through clutches K1, K2, K3 and K4, the whole speed changer realizes eight-gear speed change, a plurality of high-speed motors with smaller specifications are adopted for auxiliary driving, compared with the traditional high-speed motor driving with large specifications, the whole length of the speed changer is shorter, the volume is smaller, the work is more stable and reliable, and when one high-speed motor fails, the rest high-speed motors can also continue to work to ensure the operation of the speed changer, ensuring the vehicle to continue running; meanwhile, when the clutches K1 and K2 are both disconnected, the engine can drive the high-speed motor to rotate to generate electricity by engaging the clutch KF.

In the embodiment, the power input shaft 110 and the power transition shaft 210 are coaxially connected together and can rotate relatively, and the power transition shaft 210 and the power output shaft 220 are coaxially connected together and can rotate relatively; a plurality of rear intermediate shafts 230 which are uniformly distributed around the power transition shaft and are parallel to the power transition shaft are installed in the four-gear transmission shell, a clutch K1 and a clutch K2 are arranged between the rear intermediate shafts 230 and the power transition shaft 210, and a clutch K3 and a clutch K4 are arranged between the rear intermediate shafts and the power output shaft.

In this embodiment, all clutches adopt a multi-plate friction clutch, which belongs to the prior art, and the structure and the working principle thereof are not specifically explained herein; the clutch K2 and the clutch outer ring of the clutch K3 are connected into a whole and meshed with a gear C on the rear intermediate shaft through a peripheral gear ring C, the clutch outer ring of the clutch K1 is meshed with the gear D on the rear intermediate shaft through the gear ring D, the clutch outer ring of the clutch K4 is meshed with the gear E on the rear intermediate shaft through the gear ring E, a first oil cavity and a first double-head piston pressing plate controlled by a piston in the first oil cavity are arranged between the clutch K1 and the clutch K2, the first double-head piston pressing plate is used for controlling the clutch K1 or the clutch K2 to be closed, a second oil cavity and a second double-head piston pressing plate controlled by a piston in the second oil cavity to move are arranged between the clutch K3 and the clutch K4, and the second double-head piston pressing plate is used for controlling the clutch K3 or the clutch K4 to be closed.

The clutch KF and the clutch outer ring of the clutch K5 are connected into a whole and meshed with a gear A121 on the front intermediate shaft through a peripheral gear ring A160, a fourth oil cavity and a piston pressing plate controlled by a piston in the fourth oil cavity to move are arranged on the front side of the clutch KF, and the piston pressing plate is used for controlling the clutch KF to be closed; the outer ring of the clutch K6 is meshed with the gear B122 on the front intermediate shaft through the peripheral gear ring B170; and a third oil chamber and a third double-head piston pressing plate controlled by a piston in the third oil chamber are arranged between the clutch K5 and the clutch K6, and the third double-head piston pressing plate is used for controlling the closing of the clutch K5 or the clutch K6.

In the embodiment, a plurality of temperature sensors A280 are mounted on the side walls of the transfer case shell 100 and the four-gear transmission case shell 200, the number of the temperature sensors A is the same as that of the clutches, the positions of the temperature sensors A correspond to those of the clutches one by one, and probes of the temperature sensors A extend to the positions near the corresponding clutches at the inward ends; the probe of the temperature sensor A is extended to the vicinity of the clutch, oil thrown out from the clutch along the radial direction can immediately contact the probe of the temperature sensor, the temperature of the oil cannot be excessively lost, the oil temperature detected by the temperature sensor is ensured to be closest to the temperature of the clutch, the structure is simple, the detection result is high in accuracy, and a basis is provided for adjusting the working condition of the whole transmission.

In the embodiment, the inward end of the probe of the temperature sensor A is close to the piston top pressure plate of the corresponding clutch; the inside lubricated and cooling friction disc's of clutch oil can be thrown out from temperature sensor A's probe side (being piston top pressure disk position), and the fluid of throwing out just contacts temperature sensor A's probe, and temperature sensor A just can detect the oil temperature this moment, and the oil temperature this moment is nearest with clutch temperature itself, temperature sensor A is towards the distance between interior one end and the piston top pressure disk and is 2~5 mm.

In the present embodiment, oil pans 400 are arranged at the bottoms of the transfer case shell and the four-gear transmission case shell; an upper layer and a lower layer of serpentine radiating pipes 410 are arranged in the oil pan 400, and the radiating pipes are copper pipes; the side part of the oil pan is provided with a cooling liquid inlet 420 and a cooling liquid outlet 430 which are respectively connected with the two ends of the serpentine heat dissipation pipe 410; a temperature sensor B480 is further installed on the side of the oil pan, and a probe of the temperature sensor B extends into the oil pan; the radiator is arranged in the space in the oil pan, the structure is simple and compact, the design of the main shell of the transmission is not influenced, the design is reasonable, the cooling liquid is introduced into the radiating tubes, and the heat of the hydraulic oil can be taken away by the cooling liquid through the radiating tubes, so that the oil temperature is reduced, and the operation stability of the transmission is ensured; the temperature sensor B can detect the oil temperature in real time.

In this embodiment, the bottom of the oil pan 400 is provided with a plurality of threaded through holes, and magnetic plugs 440 are installed in the threaded through holes; the magnetic plug 440 can adsorb iron powder or scrap iron in oil, prevent the filter from being blocked by the impurities, and simultaneously avoid gear abrasion during lubrication.

In this embodiment, be provided with the bottom suspension fagging that supports lower floor's snakelike cooling tube in the oil pan, the bottom suspension fagging upside is provided with the intermediate support strip that supports upper snakelike cooling tube, the intermediate support strip upside is provided with upper press strip 490, lower support strip, intermediate support strip and upper press strip pass through bolted connection and be in the same place, and the semicircular groove that the position corresponds is seted up to lower suspension fagging upside and intermediate support strip downside, and the semicircular groove that the position corresponds is also seted up to intermediate support strip upside and upper press strip downside, and two semicircular groove formation round holes that correspond are gone up and down pass for the cooling tube, and lower floor's cooling tube is cliied in bottom suspension fagging.

In this embodiment, an oil outlet 450 and an oil return port 460 are formed in the side of the oil pan 400, and an oil heating device is installed at the oil outlet; the oil heating device comprises an oil outlet pipe 451 connected to an oil outlet, a heating rod 452 extending into the oil outlet pipe is mounted at one end of the oil outlet pipe 451 facing outwards, an oil suction port 453 is formed in the side part of the oil outlet pipe, the oil suction port is communicated with an inlet of an oil pump (not shown in the figure), an outlet of the oil pump is connected to a hydraulic system of the transmission, and hydraulic oil completing work returns to the oil return port; the hydraulic oil in the transmission is pumped out from the oil outlet, the heating rod heats the oil passing through the oil outlet pipe, the heated oil is pumped to a hydraulic system of the transmission through the oil pump, and the fluidity of the oil can be improved by heating the hydraulic oil to a certain degree, so that a hydraulic pump on the transmission is not too hard to pump oil, and the normal work of the transmission is ensured; and adopt instant heating's mode, can promote the oil temperature more fast.

In this embodiment, a filter 470 is disposed above the oil outlet pipe, an inlet end of the filter is connected to an oil suction port of the oil outlet pipe, an outlet end of the filter is connected to an L-shaped joint 471, the L-shaped joint is connected to an inlet of an oil pump through a hose, and an outlet of the oil pump is connected to a hydraulic system of the transmission through a hose; the filter can filter out impurities in the oil.

In this embodiment, in order to make the filter mounting more secure, the filter 470 is fixed to the casing of the transmission (i.e., the transfer case casing 100 or the four-speed transmission case casing 200) by an arcuate filter bracket 472, the filter 470 and the filter bracket 472 are connected by screws, and the filter bracket 472 is connected to the outside of the casing of the transmission by screws.

In this embodiment, in order to ensure the stability of the high-speed motor, a reinforcing plate 500 is vertically arranged in front of the transfer case shell 100 and is perpendicular to the power input shaft, a plurality of connecting brackets 510 are connected between the reinforcing plate 500 and the rear end of the transfer case shell, and the front end of the high-speed motor is fixed on the reinforcing plate.

A method of operating a power-coupled eight speed transmission as described above, (1) power take-off mode: the front intermediate shaft driven by the high-speed motor and the power input shaft driven by the engine realize power coupling through a clutch KF, and power is transmitted to the power transition shaft through a clutch K5 or a clutch K6 to realize two-gear speed change; the power transition shaft transmits power to the rear intermediate shaft through the clutch K1 or the clutch K2, the rear intermediate shaft transmits the power to the power output shaft through the clutch K3 or the clutch K4, four-gear speed change is achieved, and eight-gear power output is achieved through the whole transmission; (2) and (3) generating mode: the clutch K5 and the clutch K6 are in a disconnected state, the clutch KF is in an engaged state, and a power input shaft driven by an engine drives a high-speed motor to rotate through a front intermediate shaft, so that power generation is realized.

As shown in fig. 10 to 13, a hydraulic control system for the power-coupled eight-speed transmission includes a first control oil path connected to first oil chambers of control clutches K1 and K2, a second control oil path connected to second oil chambers of control clutches K2 and K3, a third control oil path connected to third oil chambers of control clutches K5 and K6, and a fourth control oil path connected to a fourth oil chamber of control clutch KF, where the first control oil path, the second control oil path, the third control oil path, and the fourth control oil path are arranged in parallel; the first control oil path, the second control oil path and the third control oil path are all provided with a proportional valve 18 and a three-position four-way electromagnetic valve 19, and A, B interfaces of the three-position four-way electromagnetic valve 19 are respectively connected to two ends of a corresponding oil cavity; a proportional valve 18 is arranged on the fourth control oil path; the balance oil way is used for balancing pressure difference at two ends of the first oil cavity, the second oil cavity and the third oil cavity; the balance oil way is used for switching the pressure difference between two ends of the balance oil cavity, so that the piston in the oil cavity can move slowly, the clutch can be engaged slowly, the gear shifting process is ensured to be stable, and the problem of shifting in the speed changing process due to the fact that the piston moves quickly because the oil pressure difference between two ends of the oil cavity is too large is solved.

In this embodiment, the first control oil path, the second control oil path, the third control oil path, the fourth control oil path and the balance oil path are connected to the oil tank 1 through a control main oil path, the oil tank 1 is further connected with a lubrication main oil path, the lubrication main oil path is connected with a lubrication branch oil path leading to each lubrication oil path, the lubrication main oil path is provided with two filter elements, a one-way valve 15 and a two-position two-way electromagnetic valve 23, the two filter elements are respectively a 10um filter element 10 with a filtering precision of 10um and a 20um filter element 9 with a filtering precision of 20um, and the lubrication main oil path is further connected with a supplementary oil path 17 leading to the control main oil path between the one-way valve and the two-position; when two clutches need to be controlled to act, the control main oil circuit may have insufficient oil quantity or insufficient oil pressure, at the moment, the two-position two-way electromagnetic valve acts to cut off oil communicated to each lubricating branch oil circuit, so that the original oil for lubrication is supplemented into the control main oil circuit to control the action of the clutches.

In this embodiment, a proportional valve 18 and a normally closed two-position three-way electromagnetic valve 22 are arranged on the balance oil path, 2 interfaces of the two-position three-way electromagnetic valve 22 are connected to one of the lubricating branch oil paths, 3 interfaces of the two-position three-way electromagnetic valve are connected with the proportional valve on the balance oil path, and 1 interface of the two-position three-way electromagnetic valve is respectively connected to T interfaces of the three-position four-way electromagnetic valve on the first control oil path, the second control oil path and the third control oil path; the proportional valve on the control oil way controls the pressure at the oil inlet end of the oil cavity, and the proportional valve on the balance oil way controls the pressure at the oil outlet end of the oil cavity to ensure that the oil pressure difference at the two ends is not too large when the first oil cavity, the second oil cavity and the third oil cavity act; meanwhile, a part of oil in the lubricating oil way is used for filling the control oil way, so that the control oil way is full of oil, when the clutch needs to be controlled to act to switch gears, the control main oil way does not need to provide excessive oil, and only the oil quantity of the piston needs to be provided, so that the response speed can be increased.

In this embodiment, the control main oil path is also provided with two filter elements, namely a 10um filter element 10 with a filtering precision of 10um and a 20um filter element 9 with a filtering precision of 20 um; and a pressure relief pipeline returning to the oil tank is further connected by the control main oil circuit, and the pressure relief pipeline is provided with a normally closed throttle valve 11 and an overflow valve 12 which are arranged in parallel, so that pressure can be manually relieved by opening the throttle valve, and when the transmission is maintained, the hydraulic system is prevented from being failed to cause incomplete pressure relief.

In this embodiment, the main lubrication oil path is further connected to a pressure sensor C28 and a filter, the rated pressure of the pressure sensor C28 is 8MPa, and the filter is also arranged on the pipeline connecting the 2 ports of the two-position three-way solenoid valve 22 to the branch lubrication oil path; the constant delivery pump 7 driven by a high-speed motor 6 is installed on the lubricating main oil way and the control main oil way, a heater 4 and an oil absorption filter 5 are installed on a connecting pipeline between the oil tank 1 and the control main oil way and the lubricating main oil way, a radiator 2 is installed in the oil tank 1, and a ventilation cap 3 is arranged on the upper side of the oil tank.

In the embodiment, the first control oil path, the second control oil path and the third control oil path are provided with a filter and a pressure measuring sensor B20 on a pipeline between the three-position four-way electromagnetic valve and the corresponding oil chamber, and the rated pressure of the pressure measuring sensor B is 6 MPa; the fourth control oil passage is also provided with a filter and a load cell B on a pipe between the proportional valve and the fourth oil chamber.

In this embodiment, the control main oil circuit is provided with a pressure sensor C, the rated pressure of the pressure sensor C is 8MPa, the lubrication branch oil circuit is provided with a pressure sensor D, and the rated pressure of the pressure sensor D is 0.5 MPa.

In this embodiment, the first control oil path and the second control oil path are provided in a transmission main valve block a for controlling the actuation and lubrication of the clutch in the four-speed transmission, and the third control oil path and the fourth control oil path are provided in a transmission main valve block B for controlling the actuation and lubrication of the clutch in the transfer case (i.e., the two-speed transmission); the filter element, the one-way valve, the filter, the pressure measuring sensor A, the two-position two-way electromagnetic valve and other components on the main control oil way are arranged on the auxiliary transmission valve block A; one of the main lubricating oil paths is connected to a main transmission valve block A and then is divided into a plurality of oil paths for lubricating a four-gear box clutch, the other main lubricating oil path of the main lubricating oil paths is connected to a main transmission valve block B and then is divided into a plurality of oil paths for lubricating a transfer case clutch, and the third main lubricating oil path of the main lubricating oil paths is connected to a mechanical platform valve block and then is divided into a plurality of oil paths for lubricating a mechanical platform.

The control method of the hydraulic control system comprises the following steps:

(1) in an initial state, all the proportional valves and the electromagnetic valves are not powered;

(2) when gear shifting is started, all the proportional valves apply a specified voltage, the controller enables the oil supply pressure of the proportional valves (namely YA1, YA2 and YA4 in the figure 1) of the first control oil path, the second control oil path and the third control oil path to be slightly larger than the oil supply pressure of the proportional valves (namely YA3 in the figure 1) on the balance oil path, the three-position four-way electromagnetic valves of the first control oil path, the second control oil path and the third control oil path are respectively electrified, and the two-position three-way electromagnetic valve are electrified; at this time, the first control oil path, the second control oil path and the third control oil path respectively supply oil to one end of the first oil chamber, one end of the second oil chamber and one end of the third oil chamber, one of the clutches K1 and K2 is closed, one of the clutches K3 and K4 is closed, and one of the clutches K5 and K6 is closed; the proportional valve (YA 3 in figure 1) on the balance oil path supplies oil to the other ends of the first oil chamber, the second oil chamber and the third oil chamber respectively through a two-position three-way electromagnetic valve, and meanwhile, the proportional valve (YA 4 in figure 1) on the fourth control oil path supplies electricity according to a preset curve to supply oil to the fourth oil chamber;

(3) in the closing process of the clutch, the controller continuously adjusts the voltages of the proportional valves (namely YA1, YA2, YA3 and YA4 in the figure 1) of the first control oil path, the second control oil path, the third control oil path and the balance oil path, so that the pressure difference between two ends of the first oil chamber, the second oil chamber and the third oil chamber is increased, and finally, a required pressure difference is achieved to completely close the clutch; then the proportional valve (YA 3 in FIG. 1), the two-position three-way solenoid valve and the two-position three-way solenoid valve on the balance oil way are electrified to complete a gear shifting process.

The first gear requires the clutches K1, K4 and K6 to be closed; the second gear needs the closing of K1, K4 and K5 clutches; the third gear requires the K2, K4 and K6 clutches to be closed; the fourth gear requires the K2, K4 and K5 clutches to be closed; fifth gear requires the K1, K3 and K6 clutches to be closed; the sixth gear requires the K1, K3 and K5 clutches to be closed; the seven gears require the K2, K3 and K6 clutches to be closed; eight gears require the K2, K3 and K5 clutches to be closed; the KF clutch needs to be in the closed state when hybrid drive is selected.

Any embodiment disclosed herein above is meant to disclose, unless otherwise indicated, all numerical ranges disclosed as being preferred, and any person skilled in the art would understand that: the preferred ranges are merely those values which are obvious or representative of the technical effect which can be achieved. Since the numerical values are too numerous to be exhaustive, some of the numerical values are disclosed in the present invention to illustrate the technical solutions of the present invention, and the above-mentioned numerical values should not be construed as limiting the scope of the present invention.

If the invention discloses or relates to parts or structures which are fixedly connected to each other, the fixedly connected parts can be understood as follows, unless otherwise stated: a detachable fixed connection (for example using bolts or screws) is also understood as: non-detachable fixed connections (e.g. riveting, welding), but of course, fixed connections to each other may also be replaced by one-piece structures (e.g. manufactured integrally using a casting process) (unless it is obviously impossible to use an integral forming process).

In addition, terms used in any technical solutions disclosed in the present invention to indicate positional relationships or shapes include approximate, similar or approximate states or shapes unless otherwise stated.

Any part provided by the invention can be assembled by a plurality of independent components or can be manufactured by an integral forming process.

Finally, it should be noted that the above examples are only used to illustrate the technical solutions of the present invention and not to limit the same; although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art will understand that: modifications to the specific embodiments of the invention or equivalent substitutions for parts of the technical features may be made; without departing from the spirit of the present invention, it is intended to cover all aspects of the invention as defined by the appended claims.