CN112594338B

CN112594338B - Eight-gear transmission with power coupling function and working method thereof

Info

Publication number: CN112594338B
Application number: CN202011618872.6A
Authority: CN
Inventors: 周荣斌; 罗南昌; 雷作钊; 陈培健
Original assignee: Fujian Zhongwei Power Technology Co Ltd
Current assignee: Fujian Zhongwei Power Technology Co Ltd
Priority date: 2020-12-31
Filing date: 2020-12-31
Publication date: 2024-07-26
Anticipated expiration: 2040-12-31
Also published as: CN112594338A

Abstract

The invention relates to a power-coupled eight-gear transmission and a working method thereof, comprising a transfer case shell and a four-gear transmission shell which are connected together, wherein a power input shaft extending from the front end is arranged in the transfer case shell; a power transition shaft is arranged between the transfer case shell and the four-gear gearbox shell, and a power output shaft extending from the rear end is arranged in the four-gear gearbox 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 power coupling is performed by adopting a plurality of high-speed motors, the size is smaller, the operation is more stable and reliable, and when one of the high-speed motors fails, the other high-speed motors can still continue to operate to ensure the operation of the transmission; and a multi-gear power output can be achieved.

Description

Eight-gear transmission with power coupling function and working method thereof

Technical Field

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

Background

The existing heavy truck is mostly driven by adopting a hybrid power system, and the hybrid power system is used for power coupling by adding a motor to an engine. At present, a hybrid power system adopts a single high-power common motor and an engine to jointly drive a power input shaft to rotate; the whole length of the transmission is larger because of the larger size of a high-power common motor (the common power is 350 KW); and when a single driving motor fails, the electric system cannot work.

Disclosure of Invention

In view of the above, the invention aims to provide an eight-gear transmission with smaller volume and more stable and reliable power coupling in operation and a working method thereof, which can realize multi-gear power output.

The invention is realized by adopting the following scheme: the eight-gear transmission with power coupling 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 arranged 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 arranged 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 arranged at the front end of the transfer case shell; a power transition shaft is arranged between the transfer case shell and the four-gear gearbox shell, and a power output shaft extending from the rear end is arranged in the four-gear gearbox 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.

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 parallel to the power transition shaft are arranged in the four-gear gearbox shell, a clutch K1 and a clutch K2 are arranged between the rear intermediate shaft and the power transition shaft, and a clutch K3 and a clutch K4 are arranged between the rear intermediate shaft and the power output shaft.

Further, a plurality of temperature sensors A are mounted on the side walls of the transfer case shell and the four-speed gearbox shell, the number of the temperature sensors A is the same as that of the clutches and the positions of the temperature sensors A are in one-to-one correspondence, and probes of the temperature sensors A extend to the vicinity of the corresponding clutches at the inward end of the temperature sensors A.

Further, oil pans are arranged at the bottoms of the transfer case shell and the four-gear transmission case shell; two layers of upper and lower snake-shaped 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 snake-shaped radiating pipes are arranged on 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.

Further, 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 heating device is arranged 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 arranged at one end of the oil outlet pipe 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.

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

Further, the transfer case shell is provided with a reinforcing plate which is vertically arranged along the vertical direction and is perpendicular to the power input shaft, a plurality of connecting brackets 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 invention adopts another technical scheme that: a hydraulic control system for the eight speed transmission power-coupled as described above, including a first control oil passage connected with a first oil chamber of the control clutches K1, K2, a second control oil passage connected with a second oil chamber of the control clutches K2, K3, a third control oil passage connected with a third oil chamber of the control clutches K5, K6, and a fourth control oil passage connected with a fourth oil chamber of the control clutch KF, the first control oil passage, the second control oil passage, the third control oil passage, and the fourth control oil passage being provided in parallel; the first control oil way, the second control oil way and the third control oil way 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 differences at two ends of the first oil cavity, the second oil cavity and the third oil cavity.

Further, 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 lubrication main oil way, a lubrication branch oil way leading to each lubrication oil way is connected to the lubrication main oil way, a filter element, a one-way valve and a two-position two-way electromagnetic valve are arranged on the lubrication main oil way, and a supplement 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 by-pass of the lubrication main oil way; the balance oil way is provided with a proportional valve and a normally closed two-position three-way electromagnetic valve, the 2 interface of the two-position three-way electromagnetic valve is connected to one of the lubricating branch oil ways, the 3 interface of the two-position three-way electromagnetic valve is connected with the proportional valve on the balance oil way, and the 1 interface of the two-position three-way electromagnetic valve is respectively connected to the 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.

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

Further, the main lubrication oil path is also connected with a pressure measuring sensor A and a filter; and the lubricating main oil way and the control main oil way are respectively provided with a constant delivery pump driven by a high-speed motor, a heater and an oil absorption filter are arranged on a connecting pipeline between the oil tank and the control main oil way as well as between the oil tank and the lubricating main oil way, a radiator is arranged in the oil tank, and an air permeable cap is arranged on the upper side of the oil tank.

Further, a filter and a pressure measuring sensor B are arranged on the pipeline between the three-position four-way electromagnetic valve and the corresponding oil cavity; and a filter and a pressure measuring sensor B are also arranged on the fourth control oil way on the pipeline between the proportional valve and the fourth oil cavity.

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

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

(1) The power coupling is performed by adopting a plurality of high-speed motors, the size is smaller, the operation is more stable and reliable, and when one of the high-speed motors fails, the other high-speed motors can still continue to operate to ensure the operation of the transmission; and a multi-gear power output can be achieved.

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

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

(4) When the oil temperature is too low, hydraulic oil can be heated to a certain degree through oil heating decoration, the fluidity of the oil can be improved, so that the hydraulic pump on the transmission is not too hard during oil pumping, and the transmission is ensured to work normally.

The present invention will be further described in detail below with reference to specific embodiments and associated drawings for the purpose of making the objects, technical solutions and advantages of the present invention more apparent.

Drawings

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

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

FIG. 3 is a perspective view of an embodiment of the transfer case 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 according to 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 invention;

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

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

FIG. 10 is a schematic view of the overall construction 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 at a transmission main valve block A according to an embodiment of the present invention;

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

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

The reference numerals in the figures illustrate: 1-tank, 2-radiator, 3-breather cap, 4-heater, 5-oil suction filter, 6-high speed motor, 7-fixed displacement pump, 8-transmission sub-valve block A, 9-20um cartridge, 10-10um cartridge, 11-throttle valve, 12-relief valve, 13-pressure tap, 14-pressure sensor C, 15-check valve, 16-transmission main valve block A, 17-make-up oil circuit, 18-proportional valve, 19-three-way solenoid valve, 20-pressure sensor B, 21 cartridge, 22-two-position three-way solenoid valve, 23-two-position two-way solenoid valve, 24-transmission sub-valve block B, 25-transmission main valve block B, 26-filter, 27-mechanical platform valve block, 28-pressure sensor A, 29-throttle plug, 30-first oil chamber, 31-second oil chamber, 32-third oil chamber, 33-fourth oil chamber, 34-pressure sensor D, 100-transfer case housing, 110-power input shaft, 120-front countershaft, 121-gear A, 122-gear B, 122-gear K, 130-gear K, 140-6-speed bump, 250K, 150-bump carrier K, 250-250K, 400-bump carrier K, 400, 250-K, 400-pad K, 400-250-K, 400-speed clutch 400, 250-K, 150-K, and one-speed clutch 400, 400-speed clutch 400, and one-well, 400-ring gear K, and one-speed clutch 400, and one-way clutch 400, 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 bracket, 480-temperature sensor B, 490-upper trim strip, 500-reinforcing plate and 510-connecting bracket.

Detailed Description

As shown in fig. 1-9, the power-coupled eight-speed transmission comprises a transfer case housing 100 and a four-speed transmission housing 200 which are connected together, wherein a power input shaft 110 extending from the front end is installed in the transfer case housing 100, a plurality of front intermediate shafts 120 uniformly distributed around the power input shaft and 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 housing 100 and a four-speed gearbox housing 200, and a power output shaft 220 extending from the rear end is arranged in the four-speed gearbox housing; 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 the high-speed motor and the power input shaft driven by the engine realize power coupling through a clutch KF, then 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 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 box realizes four-gear speed change through clutches K1, K2, K3 and K4, the whole speed change box realizes eight-gear speed change, a plurality of high-speed motors with smaller specifications are adopted for auxiliary driving, compared with the traditional driving with a large-size high-speed motor, the whole length of the speed change box is shorter, the size is smaller, the operation is more stable and reliable, and when a certain high-speed motor fails, the rest high-speed motors can continue to work to ensure the continuous running of the vehicle; meanwhile, when the clutches K1 and K2 are disconnected, the engine can drive the high-speed motor to rotate to generate electricity through engaging the clutch KF.

In the present 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 parallel to the power transition shaft are arranged in the four-speed gearbox housing, 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 the clutches are multi-plate friction clutches, which belong to the prior art, and the structure and working principle thereof are not specifically described herein; the clutch K2 and the clutch K3 are connected into a whole, the clutch outer ring is meshed with a gear C on a rear intermediate shaft through a peripheral gear ring C, the clutch outer ring of the clutch K1 is meshed with a gear D on the rear intermediate shaft through a gear ring D, the clutch outer ring of the clutch K4 is meshed with a gear E on the rear intermediate shaft through a gear ring E, a first oil cavity and a first double-headed piston top pressure plate which is controlled to move by a piston in the first oil cavity are arranged between the clutch K1 and the clutch K2, the first double-headed piston top pressure plate is used for controlling the clutch K1 or the clutch K2 to be closed, a second oil cavity and a second double-headed piston top pressure plate which is controlled to move by a piston in the second oil cavity are arranged between the clutch K3 and the clutch K4, and the second double-headed piston top pressure 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 a front intermediate shaft through a peripheral gear ring A160, a fourth oil cavity and a piston top pressure plate controlled to move by a piston in the fourth oil cavity are arranged on the front side of the clutch KF, and the piston top pressure plate is used for controlling the clutch KF to be closed; the clutch outer ring of the clutch K6 is meshed with a gear B122 on the front intermediate shaft through a peripheral gear ring B170; a third oil cavity and a third double-headed piston top pressing plate which is controlled to move by a piston in the third oil cavity are arranged between the clutch K5 and the clutch K6, and the third double-headed piston top pressing plate is used for controlling the clutch K5 or the clutch K6 to be closed.

In this embodiment, the transfer case housing 100 and the four-speed gearbox housing 200 are provided with a plurality of temperature sensors a280 on the side walls, the number of the temperature sensors a is the same as that of the clutches and the positions of the temperature sensors a are in one-to-one correspondence, and the probes of the temperature sensors a extend to the vicinity of the corresponding clutches toward one inward end; according to the invention, the probe of the temperature sensor A is extended to the vicinity of the clutch, so that oil thrown out by the clutch along the radial direction can be immediately contacted with the probe of the temperature sensor, the temperature of the oil can not be excessively lost, the temperature of the oil detected by the temperature sensor is ensured to be closest to the temperature of the clutch, the structure is simple, the accuracy of the detection result is high, and a basis is provided for the working condition adjustment of the whole transmission.

In this embodiment, the inward end of the probe of the temperature sensor a is close to the piston top pressure plate of the corresponding clutch; oil for lubricating and cooling friction plates in the clutch can be thrown out from the side (namely the position of a piston top pressure plate) of a probe of a temperature sensor A, the thrown oil just contacts with the probe of the temperature sensor A, the temperature sensor A can detect the oil temperature at the moment, the temperature of the oil at the moment is the temperature of the clutch recently, and the distance between the inward end of the temperature sensor A and the piston top pressure plate is 2-5 mm.

In the embodiment, the bottoms of the transfer case shell and the four-speed gearbox shell are respectively provided with an oil pan 400; an upper layer and a lower layer of snakelike radiating pipes 410 are arranged in the oil pan 400, and copper pipes are adopted as the radiating pipes; the side of the oil pan is provided with a cooling liquid inlet 420 and a cooling liquid outlet 430 respectively connected with both ends of the serpentine radiating pipe 410; the side part of the oil pan is also provided with a temperature sensor B480, and a probe of the temperature sensor B extends into the oil pan; the radiator is arranged in the oil pan by utilizing the space, the structure is simple and compact, the design of the main shell of the transmission is not influenced, the design is reasonable, cooling liquid is introduced into the radiating pipe, and the cooling liquid can take away the heat of hydraulic oil through the radiating pipe, so that the effect of reducing the oil temperature is achieved, and the running stability of the transmission is ensured; the temperature sensor B may detect the oil temperature in real time.

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

In this embodiment, be provided with the lower support bar that supports lower floor's snakelike cooling tube in the oil pan, the lower support bar upside is provided with the medial support bar that supports upper strata snakelike cooling tube, the medial support bar upside is provided with upper batten 490, lower support bar, medial support bar and upper batten pass through bolted connection together, and the semicircular groove that the position corresponds has been seted up to lower support bar upside and medial support bar downside, and the semicircular groove that the position corresponds has also been seted up to medial support bar upside and upper batten downside, and upper and lower two semicircular grooves that correspond form the round hole and supply the cooling tube to pass, and lower support bar and medial support bar cooperation clamp lower floor cooling tube, medial support bar and upper batten cooperation clamp upper strata cooling tube.

In this embodiment, an oil outlet 450 and an oil return port 460 are provided on 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 the oil outlet, a heating rod 452 extending into the oil outlet pipe is arranged at one outward end of the oil outlet pipe 451, an oil suction port 453 is arranged at 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 after finishing 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 the hydraulic pump on the transmission is not too hard when pumping oil, and the transmission is ensured to work normally; and the oil temperature can be raised faster by adopting an instant heating mode.

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 connector 471, the L-shaped connector is connected to an inlet of an oil pump via a hose, and an outlet of the oil pump is connected to a hydraulic system of the transmission via a hose; the filter can filter out impurities in the oil.

In this embodiment, to make the filter installation more secure, the filter 470 is fixed to the transmission housing (i.e., the transfer case housing 100 or the four-speed transmission housing 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 transmission housing by screws.

In this embodiment, in order to ensure that the high-speed motor is firmly and stably fixed, the transfer case housing 100 has a reinforcing plate 500 vertically disposed in front of the transfer case housing and perpendicular to the power input shaft, and a plurality of connection brackets 510 are connected between the reinforcing plate 500 and the rear end of the transfer case housing, and the front end of the high-speed motor is fixed on the reinforcing plate.

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

As shown in fig. 10 to 13, a hydraulic control system for the eight-speed transmission for power coupling as described above includes a first control oil passage connected with a first oil chamber of a control clutch K1, K2, a second control oil passage connected with a second oil chamber of a control clutch K2, K3, a third control oil passage connected with a third oil chamber of a control clutch K5, K6, and a fourth control oil passage connected with a fourth oil chamber of a control clutch KF, the first control oil passage, the second control oil passage, the third control oil passage, and the fourth control oil passage being arranged in parallel; the first control oil way, the second control oil way and the third control oil way are respectively 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 the corresponding oil cavity; the fourth control oil circuit is provided with a proportional valve 18; the balance oil way is used for balancing pressure differences at two ends of the first oil cavity, the second oil cavity and the third oil cavity; the balance oil way is used for cutting the gear shift position and is used for balancing the pressure difference at two ends of the oil cavity, so that a piston in the oil cavity can slowly move, a clutch can be slowly connected, the gear shift process is ensured to be stable, and the problem that the piston moves rapidly due to the fact that the oil pressure difference at two ends of the oil cavity is too large, and then the shifting process is caused 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, a lubrication branch oil path leading to each lubrication oil path is connected to the lubrication main oil path, a filter element, a one-way valve 15 and a two-position two-way electromagnetic valve 23 are arranged on the lubrication main oil path, the two filter elements are respectively a 10um filter element 10 with the filtering precision of 10um and a 20um filter element 9 with the filtering precision of 20um, and a supplement oil path 17 leading to the control main oil path is also connected between the one-way valve and the two-position two-way electromagnetic valve by-pass; when two clutches are required to be controlled to operate, the oil quantity of the control main oil way may be insufficient or the oil pressure is insufficient, at the moment, the two-position two-way solenoid valve operates to cut off the oil to each lubricating branch oil way, so that the oil originally used for lubricating is supplemented into the control main oil way to control the clutch to operate.

In this embodiment, the balance oil path is provided with a proportional valve 18 and a normally closed two-position three-way electromagnetic valve 22, the 2 interface of the two-position three-way electromagnetic valve 22 is connected to one of the two-position three-way electromagnetic valve and the 3 interface of the two-position three-way electromagnetic valve is connected with the proportional valve on the balance oil path, and the 1 interface of the two-position three-way electromagnetic valve is connected to the 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 respectively; the proportional valve on the control oil path controls the pressure of the oil inlet end of the oil cavity, and the proportional valve on the balance oil path controls the pressure of 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, part of oil in the lubricating oil way is used for filling the control oil way, so that the control oil way is filled with oil, and when the clutch is required to be controlled to move to switch gear positions, the control main oil way is not required to provide excessive oil, and only the oil quantity of the piston is required 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; the control main oil way is also connected with a pressure relief pipeline which returns to the oil tank, the pressure relief pipeline is provided with a normally closed throttle valve 11 and an overflow valve 12 which are arranged in parallel, and the pressure relief can be manually carried out by opening the throttle valve, so that the hydraulic system is prevented from being broken down and not completely carried out when the transmission is maintained.

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 disposed on the 2-port connection of the two-position three-way electromagnetic valve 22 to the pipe path of the branch lubrication oil path; the oil tank 1 is internally provided with a radiator 2, and the upper side of the oil tank is provided with a ventilation cap 3.

In the embodiment, a filter and a pressure measuring sensor B20 are arranged on a pipeline between the three-position four-way electromagnetic valve and the corresponding oil cavity, and the rated pressure of the pressure measuring sensor B is 6MPa; and a filter and a pressure measuring sensor B are also arranged on the fourth control oil way on the pipeline between the proportional valve and the fourth oil cavity.

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

In this embodiment, the first control oil path and the second control oil path are disposed on the main transmission valve block a and are used for controlling the movement and lubrication of the clutch in the fourth-gear transmission, and the third control oil path and the fourth control oil path are disposed on the main transmission valve block B and are used for controlling the movement and lubrication of the clutch in the transfer case (i.e., the two-gear case); the components such as a filter element, a one-way valve, a pressure measuring sensor C, a throttle valve, an overflow valve and the like on the control main oil circuit are arranged on the transmission auxiliary valve block A, and the components such as the filter element, the one-way valve, the filter, the pressure measuring sensor A, the two-position two-way electromagnetic valve and the like of the lubrication main oil circuit are arranged on the transmission auxiliary valve block B; one of the main lubricating oil ways is connected to the main valve block A of the transmission and is subdivided into a plurality of oil ways for lubrication of the four-gear box clutch, the other main lubricating oil way is connected to the main valve block B of the transmission and is subdivided into a plurality of oil ways for lubrication of the transfer box clutch, and the third main lubricating oil way is connected to the valve block of the mechanical platform and is subdivided into a plurality of oil ways for lubrication of the mechanical platform.

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

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

(2) Starting gear shifting, wherein all proportional valves supply a specified voltage, oil supply pressures of proportional valves (namely YA1, YA2 and YA4 in figure 1) of a first control oil way, a second control oil way and a third control oil way are slightly larger than oil supply pressures of proportional valves (namely YA3 in figure 1) on a balance oil way through a controller, and three-position four-way electromagnetic valves of the first control oil way, the second control oil way and the third control oil way are respectively powered, and a two-position three-way electromagnetic valve are powered; at this time, the first control oil path, the second control oil path and the third control oil path supply oil to one ends of the first oil chamber, the second oil chamber and the third oil chamber respectively, 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 cavity, the second oil cavity and the third oil cavity respectively through two-position three-way electromagnetic valves, 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 cavity;

(3) The voltage of proportional valves (namely YA1, YA2, YA3 and YA4 in figure 1) of the first control oil way, the second control oil way, the third control oil way and the balance oil way is continuously regulated by a controller in the closing process of the clutch, so that the pressure difference between the two ends of the first oil cavity, the second oil cavity and the third oil cavity is increased, and finally, the required pressure difference is reached to enable the clutch to be completely closed; the proportional valve (i.e., YA3 in FIG. 1), the two-position three-way solenoid valve and the two-position three-way solenoid valve on the balance oil path are then energized to complete a shift process.

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

Any of the above-described embodiments of the present invention disclosed herein, unless otherwise stated, if they disclose a numerical range, then the disclosed numerical range is the preferred numerical range, as will be appreciated by those of skill in the art: the preferred numerical ranges are merely those of the many possible numerical values where technical effects are more pronounced or representative. Since the numerical values are more and cannot be exhausted, only a part of the numerical values are disclosed to illustrate the technical scheme of the invention, and the numerical values listed above should not limit the protection scope of the invention.

If the invention discloses or relates to components or structures fixedly connected with each other, then unless otherwise stated, the fixed connection is understood as: detachably fixed connection (e.g. using bolts or screws) can also be understood as: the non-detachable fixed connection (e.g. riveting, welding), of course, the mutual fixed connection may also be replaced by an integral structure (e.g. integrally formed using a casting process) (except for obviously being unable to use an integral forming process).

In addition, terms used in any of the above-described aspects of the present disclosure to express positional relationship or shape have meanings including a state or shape similar to, similar to or approaching thereto 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-mentioned embodiments are only for illustrating the technical scheme of the present invention and are not limiting; while the invention has been described in detail with reference to the preferred embodiments, those skilled in the art will appreciate that: modifications may be made to the specific embodiments of the present invention or equivalents may be substituted for part of the technical features thereof; without departing from the spirit of the invention, it is intended to cover the scope of the invention as claimed.

Claims

1. A power-coupled eight speed transmission, characterized by: the transfer case comprises a transfer case shell and a four-gear transmission shell which are connected together, wherein a power input shaft extending from the front end is arranged 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 arranged 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 arranged at the front end of the transfer case shell; a power transition shaft is arranged between the transfer case shell and the four-gear gearbox shell, and a power output shaft extending from the rear end is arranged in the four-gear gearbox 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 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 parallel to the power transition shaft are arranged in the four-gear gearbox shell, a clutch K1 and a clutch K2 are arranged between the rear intermediate shaft and the power transition shaft, and a clutch K3 and a clutch K4 are arranged between the rear intermediate shaft and the power output shaft.

2. The power-coupled eight speed transmission of claim 1, wherein: the transfer case shell and the four-speed gearbox shell are provided with a plurality of temperature sensors A on the side walls, the number of the temperature sensors A is the same as that of the clutches and the positions of the temperature sensors A are in one-to-one correspondence, and probes of the temperature sensors A extend to the vicinity of the corresponding clutches towards the inner end of the probes.

3. The power-coupled eight speed transmission of claim 1, wherein: the bottoms of the transfer case shell and the four-gear gearbox shell are respectively provided with an oil pan; two layers of upper and lower snake-shaped 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 snake-shaped radiating pipes are arranged on 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.

4. A power-coupled eight speed transmission according to claim 3, wherein: an oil outlet and an oil return port are formed in the side part of the oil pan, and an oil heating device is arranged 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 arranged at one end of the oil outlet pipe 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.

5. The power-coupled eight speed transmission of claim 4, wherein: the oil outlet pipe top is provided with the filter, the entry end of filter is connected with the oil suction port of oil outlet pipe, the exit end of filter is connected with L shape and connects, L shape connects and is connected with the oil pump entry through the hose.

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

7. A hydraulic control system for the power-coupled eight speed transmission of claim 1, wherein: the hydraulic control system comprises a first control oil circuit connected with a first oil cavity of a control clutch K1 and a first oil cavity of a control clutch K2, a second control oil circuit connected with a second oil cavity of the control clutch K2 and a second oil cavity of a control clutch K3, a third control oil circuit connected with a third oil cavity of the control clutch K5 and a third oil cavity of a control clutch K6 and a fourth control oil circuit connected with a fourth oil cavity of a control clutch KF, wherein the first control oil circuit, the second control oil circuit, the third control oil circuit and the fourth control oil circuit are arranged in parallel; the first control oil way, the second control oil way and the third control oil way 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 differences at two ends of the first oil cavity, the second oil cavity and the third oil cavity.

8. The hydraulic control system of claim 7, 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 the oil tank through a control main oil way, the oil tank is also connected with a lubrication main oil way, the lubrication main oil way is connected with a lubrication branch oil way leading to each lubrication oil way, the lubrication main oil way is provided with a filter element, a one-way valve and a two-position two-way electromagnetic valve, and a supplement 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 by-pass of the lubrication main oil way; the balance oil way is provided with a proportional valve and a normally closed two-position three-way electromagnetic valve, the 2 interface of the two-position three-way electromagnetic valve is connected to one of the lubricating branch oil ways, the 3 interface of the two-position three-way electromagnetic valve is connected with the proportional valve on the balance oil way, and the 1 interface of the two-position three-way electromagnetic valve is respectively connected to the 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.

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