CN106678326B - Hydraulic speed variator for light vehicle - Google Patents
Hydraulic speed variator for light vehicle Download PDFInfo
- Publication number
- CN106678326B CN106678326B CN201710083190.1A CN201710083190A CN106678326B CN 106678326 B CN106678326 B CN 106678326B CN 201710083190 A CN201710083190 A CN 201710083190A CN 106678326 B CN106678326 B CN 106678326B
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- gear
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- 230000005540 biological transmission Effects 0.000 claims abstract description 54
- 230000007935 neutral effect Effects 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 3
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 230000007547 defect Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009347 mechanical transmission Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/065—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the friction or endless flexible member type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
Abstract
The invention relates to a hydraulic transmission for a light vehicle, wherein an oil pump driving sleeve and a supporting shaft are arranged on a box body, an oil pump arranged in the box body is connected with the oil pump driving sleeve, a power taking window is arranged at the horizontal part of an input shaft of the box body, and a connecting gear which is empty sleeved on a guide wheel seat is meshed with an oil pump connecting gear on the pump driving sleeve through two power taking gear wheels on the supporting shaft; the first shaft and the second shaft are respectively provided with a wet clutch and a corresponding driving gear, driven gears arranged on the first shaft and the second shaft are respectively meshed with two input gears of the input shaft, the driving gears on the first shaft and the second shaft are respectively correspondingly meshed with an output shaft gear, a high-gear output gear and a low-gear output gear on the output shaft, a reverse clutch Kr and a reverse driving gear on the reverse shaft are respectively meshed with the wet clutch and the low-gear output gear on the first shaft and are matched with a locking clutch, and six forward gears and one reverse output are realized. The invention has novel and compact structure, flexible operation and multiple gears and can adapt to different working conditions of the light vehicle.
Description
Technical Field
The invention relates to a hydraulic transmission for a light vehicle, belonging to the technical field of hydraulic transmissions for light vehicles.
Background
The transmission of a general automobile mainly comprises a mechanical transmission and a hydromechanical transmission. The mechanical speed changer is complex in operation, for automobiles needing frequent stopping, starting and accelerating, a driver has to frequently shift gears, the labor intensity is high, the mechanical speed changer is a rigid transmission with step speed change, the vibration and the impact are large in the driving process, and the riding comfort is poor. The wet-type multi-plate clutch is controlled and operated by the electrohydraulic valve to realize gear conversion, and the hydromechanical transmission adopts the external meshing gear to carry out gear shifting transmission, so that the hydraulic mechanical transmission has the advantages of good manufacturing process and high transmission efficiency. The hydromechanical transmission is a planetary gear type transmission, can obtain a proper number of gears through a small number of planetary rows, has the advantages of compact structure and light weight, but has the defects of complex manufacturability, high manufacturing cost and the like. The application range of the hydraulic transmission for the light vehicle is special, the total weight of the vehicle is less than 7 tons, and the total length of the vehicle body is less than 7 meters. An automatic transmission of a passenger car cannot be installed due to insufficient power; the automatic transmission of a large heavy-duty car is unsuitable in power range and large in size and cannot be installed. Moreover, the existing similar hydraulic transmission is generally insensitive to control, so that the hydraulic transmission is difficult to use when different working conditions are switched, and the labor intensity is high.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provide the hydraulic transmission for the light vehicle, which has the advantages of novel and compact structure, convenient assembly, flexible operation, multiple gears, capability of adapting to different working conditions of the light vehicle and adjustable power take-off speed ratio.
The technical scheme for achieving the purpose is as follows: the hydraulic transmission for the light vehicle comprises a hydraulic torque converter and a transmission, wherein the hydraulic torque converter comprises a driving disc, a locking clutch, a turbine, a guide wheel, a pump wheel, a guide wheel seat and an input shaft, the driving disc is connected with the pump wheel through the locking clutch, the guide wheel is fixed on the guide wheel seat through an overrunning clutch, the guide wheel seat fixedly connected on a box body is sleeved on the input shaft, and the turbine is fixedly connected on the input shaft through the turbine seat; the method is characterized in that:
the box body is provided with an oil pump driving sleeve and a supporting shaft, an oil pump connecting gear is fixed on the oil pump driving sleeve, an oil pump arranged in the box body is connected with the oil pump driving sleeve, a power taking window is arranged at the horizontal part of an input shaft of the box body, the supporting shaft fixed on the box body corresponds to the power taking window, a first power takeoff gear and a second power takeoff gear with different tooth diameters are sleeved on the supporting shaft in an empty mode, a connecting gear sleeved on a guide wheel seat shaft section is connected with the pump wheel, the connecting gear is in constant mesh with the first power takeoff gear with a large diameter, and the oil pump connecting gear is in constant mesh with the first power takeoff gear or the second power takeoff gear;
the transmission comprises an I shaft, a II shaft, an output shaft and a reverse gear shaft which are supported on a box body through bearings, wherein an output shaft gear, a high-gear output gear, a low-gear output gear and an output flange are sequentially arranged on the output shaft along the axial direction, an input shaft with a first input gear and a second input gear which are different in tooth diameter is coaxially connected with the output shaft through the bearings, a wet clutch K1 and a wet clutch K2 are connected to the I shaft and are connected with a first driving gear and a second driving gear which are respectively corresponding to the I shaft in a sleeved mode, an I shaft driven gear on the input side of the I shaft is in constant engagement with a second input gear with a small diameter, the first driving gear is in constant engagement with the low-gear output gear, and the second driving gear is in constant engagement with the output shaft gear, so that second forward power output is realized;
the wet clutch K3 and the wet clutch K4 are connected to the II shaft and are connected with a third driving gear and a fourth driving gear which are respectively corresponding to the II shaft in a hollow mode, a II shaft driven gear at the input side of the II shaft is normally meshed with a first input gear with a large diameter, the third driving gear is normally meshed with an output shaft gear, and the fourth driving gear is normally meshed with a high-gear output gear and is matched with a locking clutch to realize four-gear forward power output;
the reverse gear shaft is provided with a reverse gear clutch Kr, an external gear of the reverse gear clutch Kr is normally meshed with an external gear of the wet clutch K1 or an external gear of the wet clutch K2, the reverse gear clutch Kr is connected with a reverse gear driving gear sleeved on the reverse gear shaft, and the reverse gear driving gear is normally meshed with a low gear output gear, so that reverse gear power output is realized.
The hydraulic transmission has two input gears with different tooth diameters on the input shaft, the input gears are meshed with the driven gears on the I shaft and the II shaft, the I shaft, the II shaft and the reverse gear shaft are respectively provided with a wet clutch for controlling gear, the electrohydraulic valve is used for controlling the operation of the corresponding wet clutches on the I shaft, the II shaft and the reverse gear shaft, so that the first driving gear and the second driving gear which are sleeved on the I shaft, the third driving gear and the fourth driving gear which are sleeved on the II shaft are meshed with the output shaft gear, the low gear output gear and the high gear output gear on the output shaft to output power, and the input shafts respectively drive the I shaft and the II shaft through the input gears, thereby reducing power transmission loss, improving transmission efficiency and reducing fuel consumption. The hydraulic transmission provided by the invention adopts the input shaft, the I shaft, the II shaft, the reverse gear shaft and the output shaft, and the input shaft is coaxially connected with the output shaft of the transmission, so that the hydraulic transmission is convenient to install, simple, compact and reasonable in structure, small in size, convenient to manufacture, easy to ensure the assembly precision, convenient to maintain, and capable of meeting the light requirements on the internal structure of the transmission. According to the invention, a small amount of transmission shafts and gears are matched with the wet clutch, the wet clutch is controlled and operated through the electrohydraulic valve to realize automatic gear shifting, six forward gears and one reverse gear are realized, the power range is suitable for a light vehicle, and different working conditions of the light vehicle can be met. The box body is provided with the force taking port, the torque of the engine can be transmitted out through the force taking gear, the force taking window is positioned at the horizontal position of the input shaft of the gearbox, and the speed ratio of the force taking port is adjustable, so that different operation requirements are met.
Drawings
Embodiments of the present invention are described in further detail below with reference to the accompanying drawings.
Fig. 1 is a schematic structural view of a hydraulic transmission for a light vehicle according to the present invention.
Fig. 2 is a schematic side view of the structure of fig. 1.
FIG. 3 is a schematic cross-sectional expanded configuration of A-A and B-B of FIG. 1.
Fig. 4 is a transmission schematic of the present invention.
Wherein: 1-driving disk, 2-guide wheel seat, 3-guide wheel, 4-locking clutch, 5-turbine, 6-pump wheel, 7-connecting gear, 8-first power takeoff gear, 9-supporting shaft, 10-oil pump driving sleeve, 11-oil pump connecting gear, 12-second power takeoff gear, 13-oil pump, 14-input shaft, 15-first input gear, 16-I shaft driven gear, 17-second driving gear, 18-reverse gear shaft, 19-reverse gear driving gear, 20-I shaft, 21-first driving gear, 22-low gear output gear, 23-output shaft, 24-output flange, 25-high gear output gear, 26-fourth driving gear, 27-II shaft, 28-box, 28-1-power taking window, 28-2-front box, 28-21-middle wallboard, 28-22-rear wallboard, 28-3-rear box, 28-31-front wallboard, 28-32-rear wallboard, 28-33-first middle baffle, 28-34-second middle baffle, 28-4-box cover, 29-electrohydraulic valve, 30-third driving gear, 31-output shaft gear, 32-second input gear, 33-II shaft driven gear, 34-overrunning clutch, 35-turbine seat, 36-I shaft bearing cover, 37-II shaft bearing cover, 38-reverse gear bearing cover and 39-output shaft bearing cover.
Detailed Description
As shown in fig. 1 to 3, the hydrodynamic transmission for a light vehicle of the present invention includes a hydrodynamic torque converter and a transmission. The hydraulic torque converter comprises a driving disc 1, a locking clutch 4, a turbine 5, a guide wheel 3, a pump wheel 6, a guide wheel seat 2 and an input shaft 14, wherein the driving disc 1 is connected with the pump wheel 6 through the locking clutch 4, the guide wheel 3 is fixed on the guide wheel seat 2 through an overrunning clutch 34, the guide wheel seat 2 fixedly connected on a box 28 is sleeved on the input shaft 14, and the turbine 5 is fixedly connected on the input shaft 14 through a turbine seat 35.
As shown in fig. 1 and 3, an oil pump driving sleeve 10 and a supporting shaft 9 are installed on a box body 28, the oil pump driving sleeve 10 is connected to the box body 28 through a bearing, an oil pump connecting gear 11 is fixed on the oil pump driving sleeve 10, the oil pump connecting gear 11 and the oil pump driving sleeve 10 can be made into an integrated structure, an oil pump 13 arranged in the box body 28 is connected with the oil pump driving sleeve 10, the volume of a hydraulic torque converter can be further reduced through the oil pump 13 built in the box body 28, and when a driving disc 1 drives a pump wheel 6 to rotate, oil is supplied to oil channels on a turbine 5 and the box body 28 and oil channels in an I shaft 20, an II shaft 27 and a reverse gear shaft 18 respectively through the oil pump 13, so that gear conversion and lubrication are realized; meanwhile, the oil drives the turbine 5 to rotate, and drives the input shaft 14 to rotate through the turbine seat 35, so that power is output through the output shaft 23 after passing through each shaft.
As shown in fig. 1 and 2, a power take-off window 28-1 is arranged at the horizontal position of an input shaft 14, a supporting shaft 9 fixed on the box 28 corresponds to the power take-off window 28-1, the supporting shaft 9 adopts a T-shaped shaft and is installed on the box 28 through a fastener for supporting two power take-off gears, a first power take-off gear 8 and a second power take-off gear 12 with different tooth diameters are sleeved on the supporting shaft 9 in an empty mode, the first power take-off gear 8 and the second power take-off gear 12 are different in tooth diameters, so that the speed ratio power take-off can be conveniently adjusted, the power take-off range is enlarged, a connecting gear 7 which is sleeved on the shaft section of a guide wheel seat 2 is connected with a pump wheel 6, the connecting gear 7 is meshed with the first power take-off gear 8 with a large diameter, an oil pump connecting gear 11 is meshed with the first power take-off gear 8 or the second power take-off gear 12, the input power is transmitted through a power take-off gear to meet the operation requirements of vehicles with different working conditions, and the oil pump 13 ensures the pressure and lubrication of the transmission.
As shown in fig. 3, the second power takeoff gear 12 of the present invention is mounted on the supporting shaft 9 through a bearing, the first power takeoff gear 8 is detachably connected to the second power takeoff gear 12, and the tooth thickness of the first power takeoff gear 8 is smaller than the tooth thickness of the second power takeoff gear 12, so that the present invention is convenient for processing and assembly.
As shown in fig. 1 and 3, the transmission of the present invention includes an i shaft 20, a ii shaft 27, an output shaft 23 and a reverse gear shaft 18 supported on a housing 28 through bearings, the output shaft 23 is provided with an output shaft gear 31, a high gear output gear 25, a low gear output gear 22 and an output flange 24 in sequence along the axial direction, the output shaft gear 31 and the output shaft 23 can be made into an integral structure, the high gear output gear 25, the low gear output gear 22 and the output flange 24 are connected to the output shaft 23 to output different rotational speeds respectively, and the input shaft 14 having a first input gear 15 and a second input gear 32 with two different tooth diameters is coaxially connected with the output shaft 23 through bearings, so that the hydraulic transmission has a simple, compact and reasonable structure and is convenient to manufacture.
In order to facilitate the installation, as shown in fig. 3, the input shaft 14 is provided with an outer shaft diameter section and an inner shaft diameter section on both sides of the first input gear 15 and the second input gear 32, the bearings mounted on the inner shaft diameter section of the input shaft 14 are connected to the box 28, the bearings mounted on the outer shaft diameter section of the input shaft 14 are disposed in the mounting holes on the inner side of the output shaft 23, and the outer side of the output shaft 23 is mounted on the box 28 through the bearings.
As shown in fig. 3, the wet clutch K1 and the wet clutch K2 of the present invention are connected to the i-shaft 20 and connected to the first driving gear 21 and the second driving gear 17 which are respectively corresponding to the i-shaft 20, the i-shaft driven gear 16 on the input side of the i-shaft 20 is in constant mesh with the second input gear 32 of small diameter, the power on the input shaft 14 is transmitted to the i-shaft 20, the first driving gear 21 is in constant mesh with the low gear output gear 22, the second driving gear 17 is in constant mesh with the output shaft gear 31 and the constant mesh, the wet clutch K1 and the wet clutch K2 are respectively controlled by the electro-hydraulic valve 29 installed on the box 28, and the power is transmitted to the output shaft 23 through the first driving gear 21 or the second driving gear 17, thereby realizing the two-gear forward power output.
As shown in FIG. 3, the wet clutch K1 and the wet clutch K2 are arranged on the I shaft 20 back to back, the friction pair of the wet clutch K1 is 1.3-1.8 times, such as 1.4 or 1.6 or 1.7 times, of the friction pair of the wet clutch K2, and the friction pair of the wet clutch K1 is more than the friction pair of the wet clutch K2, so that the relative rotating speed of the friction pair of the low-speed forward gear clutch is smaller, the power transmission loss is reduced, and the transmission efficiency is improved. As shown in fig. 3, the wet clutch K1 and the wet clutch K2 of the present invention are provided with external gears on the same housing, and a first driving gear 21 and a second driving gear 17 mounted on the i-shaft 20 through needle bearings are located at both sides of the wet clutch K1 and the wet clutch K2.
As shown in fig. 3, the wet clutch K3 and the wet clutch K4 of the present invention are connected to the ii shaft 27 and connected to the third driving gear 30 and the fourth driving gear 26 which are respectively corresponding to the ii shaft 27, the ii shaft driven gear 33 on the input side of the ii shaft 27 is normally engaged with the first input gear 15 having a large diameter, the power on the input shaft 14 is transmitted to the ii shaft 27, the third driving gear 30 is normally engaged with the output shaft gear 31, the fourth driving gear 26 is normally engaged with the high gear output gear 25, the wet clutch K3 and the wet clutch K4 are respectively controlled through the electro-hydraulic valve 29, the power is transmitted to the output shaft 23 through the third driving gear 30 or the fourth driving gear 26, and the fourth forward power output is realized in combination with the lock clutch 4.
As shown in fig. 3, the wet clutch K3 and the wet clutch K4 of the present invention are mounted back-to-back on the ii shaft 27, and the friction pair of the wet clutch K3 is identical to the friction pair of the wet clutch K4, and the third driving gear 30 and the fourth driving gear 26 mounted on the ii shaft 27 through needle bearings are located at both sides of the wet clutch K3 and the wet clutch K4, and the friction pair of the wet clutch K3 and the wet clutch K4 is identical to the friction pair of the wet clutch K2, thereby facilitating the installation.
Referring to fig. 3, a reverse clutch Kr is mounted on a reverse shaft 18, an external gear of the reverse clutch Kr is normally meshed with an external gear of a wet clutch K1 or an external gear of a wet clutch K2, power transmitted to an i shaft 20 is transmitted to the reverse clutch Kr through the wet clutch, the reverse clutch Kr is connected with a reverse driving gear 19 sleeved on the reverse shaft 18, the reverse driving gear 19 is normally meshed with a low gear output gear 22, and the reverse clutch Kr is controlled through an electrohydraulic valve 29 to realize reverse power output.
As shown in fig. 1 to 3, the case 28 of the present invention includes a front case 28-2 for mounting a torque converter, a rear case 28-3 for mounting a transmission, and a cover 28-4 mounted on a rear wall plate 28-32 of the rear case 28-3, and the front case 28-2, the rear case 28-3, and the cover 28-4 are positioned by positioning pins and connected with fasteners for easy processing, mounting, and maintenance.
As shown in FIG. 3, the front box 28-2 of the present invention comprises an open cavity box, a middle wallboard 28-21 and a rear wallboard 28-22, wherein the driving disc 1, the locking clutch 4, the turbine 5, the guide wheel 3 and the pump wheel 6 are all arranged in the cavity box, two sides of the oil pump driving sleeve 10 are arranged on the middle wallboard 28-21 and the rear wallboard 28-22 of the front box 28-2 through bearings, the front side of the supporting shaft 9 is supported on the middle wallboard 28-21, the rear side is arranged on the rear wallboard 28-22 through fasteners, the connecting gear 7 is connected on the middle wallboard 28-21 and the rear wallboard 28-22 of the front box 28-2 through bearings, and the input shaft 14 is supported on the guide wheel seat 2 through bearings.
Referring to fig. 1 to 3, the rear case 28-3 of the present invention is provided with a front wall plate 28-31, a rear wall plate 28-32, and first and second intermediate baffles 28-33 and 28-34 located in the rear case 28-3, a case cover 28-4 is provided with bearing holes corresponding to respective shafts, the front wall plate 28-31 of the rear case 28-3 is connected to the rear wall plate 28-22 of the front case 28-2 by positioning pins and fasteners, the rear wall plate 28-32 of the rear case 28-3 is connected to the case cover 28-4 by positioning pins and fasteners, an i shaft 20 is mounted on the first intermediate baffle 28-33 and the case cover 28-4 of the rear case 28-3 by bearings, a reverse gear shaft 18 is mounted on the second intermediate baffle 28-34 and the case cover 28-4 of the rear case 28-3 by bearings, an ii shaft 27 is mounted on the front wall plate 28-31 and the case cover 28-4 of the rear case 28-3 by bearings, the rear side of the output shaft 23 is supported on the case cover 28-4 by bearings, and an i shaft cover 36, an ii shaft cover 37 and a bearing cover 39 corresponding to the respective shafts and a bearing cover 39 are mounted on the output shaft cover 28-4.
As shown in fig. 3 and 4, the transmission route of the present invention is as follows: advancing to I gear: input shaft 14→second input gear 32→i-shaft driven gear 16→wet clutch K1→first driving gear 21→low gear output gear 22→output shaft 23; forward ii gear: input shaft 14→second input gear 32→i-shaft driven gear 16→wet clutch k2→second drive gear 17→output shaft gear 31→output shaft 23; advancing III gear: input shaft 14→first input gear 15→second shaft driven gear 33→wet clutch k3→third driving gear 30→output shaft gear 31→output shaft 23; advancing IV gear: input shaft 14→first input gear 15→second shaft driven gear 33→wet clutch k4→fourth driving gear 26→high gear output gear 25→output shaft 23; when the locking clutch 4 is connected with the driving disc 1 and combined with the forward III gear and the forward IV gear, the forward V gear and the forward VI gear are formed; reverse gear transmission: the input shaft 14, the second input gear 32, the I-shaft driven gear 16, the external gear of the wet clutch K1 or the wet clutch K2, the external gear of the reverse clutch, the reverse clutch Kr, the reverse driving gear 19, the low-gear output gear 22 and the output shaft 23, when the wet clutches K1, K2, K3 and K4 on the I shaft 20 and the II shaft and the reverse clutch Kr on the reverse shaft 18 are all disengaged, no power is output, and the gearbox is in idle load operation, namely in neutral gear, so that a multi-gear structure of six forward gears and one reverse gear can be formed.
When the engine is started, the pump impeller 6 is driven to rotate through the driving disc 1 and the locking clutch 4, and then the pump impeller 6 rotates together through the guide wheel 3, the turbine 5 and the input shaft 14; the operation locking clutch 4 is separated from the pump wheel 6, the turbine 5 and the input shaft 14 are driven to rotate together through the locking clutch 4 by the driving disc 1 to realize high-gear power output, the second input gear 32 on the input shaft 14 drives the I-shaft driven gear 16, the first input gear 15 drives the II-shaft driven gear 33, meanwhile, the external gear of the wet clutch on the I shaft 20 drives the external gear of the reverse gear clutch Kr to transmit power into the gearbox, and when the wet clutches K1 and K2 of the I shaft 20 and the wet clutches K3 and K4 on the II shaft 27 and the reverse gear clutch Kr on the reverse gear shaft 18 are all separated, no power is output, and the gearbox is in idle load operation, namely in neutral gear. When any one of the reverse gear, the high gear or the low gear is engaged, the corresponding wet clutch is engaged, and then the wet clutch is output through the output shaft 23 by the high gear output gear 25 or the low gear output gear 22, at this time, a proper moment is generated to drive the automobile to run under the action of the guide wheel 3 according to the size of the driving load, and the lockup clutch 4 is combined at a certain speed, so that the transmission efficiency of the hydraulic transmission is highest, and the oil consumption is reduced, so as to form multi-gear conversion.
When the engine is started, the pump wheel 6 is driven to rotate by the driving disc 1, and then the connecting gear 7 connected to the pump wheel 6 is always meshed with the first power takeoff gear 8 or the second power takeoff gear 12, the input power can be transmitted through the power takeoff, and the power takeoff can be meshed with the first power takeoff gear 8 or the second power takeoff gear 12 so as to adjust the speed ratio power takeoff. Meanwhile, the power takeoff gear is in constant engagement with the oil pump connecting gear 11, and the oil pump 13 is driven to work through the oil pump driving sleeve 10, so that gear shifting pressure and lubrication of the transmission are ensured.
Claims (4)
1. The hydraulic transmission for the light vehicle comprises a hydraulic torque converter and a transmission, wherein the hydraulic torque converter comprises a driving disc (1), a locking clutch (4), a turbine (5), a guide wheel (3), a pump wheel (6), a guide wheel seat (2) and an input shaft (14), the driving disc (1) is connected with the pump wheel (6) through the locking clutch (4), the guide wheel (3) is fixed on the guide wheel seat (2) through an overrunning clutch (34), the guide wheel seat (2) fixedly connected on a box body (28) is sleeved on the input shaft (14), and the turbine (5) is fixedly connected on the input shaft (14) through a turbine seat (35); the method is characterized in that:
the oil pump driving device is characterized in that an oil pump driving sleeve (10) and a supporting shaft (9) are arranged on a box body (28), an oil pump connecting gear (11) is fixed on the oil pump driving sleeve (10), an oil pump (13) arranged in the box body (28) is connected with the oil pump driving sleeve (10), a force taking window (28-1) is arranged at the horizontal position of an input shaft (14) of the box body (28), the supporting shaft (9) fixed on the box body (28) corresponds to the force taking window (28-1), a first power takeoff gear (8) and a second power takeoff gear (12) with different tooth diameters are sleeved on the supporting shaft (9) in an empty mode, a connecting gear (7) sleeved on a shaft section of a guide wheel seat (2) is connected with a pump wheel (6), the connecting gear (7) is normally meshed with a first power takeoff gear (8) with a large diameter, and the oil pump connecting gear (11) is normally meshed with the first power takeoff gear (8) or the second power takeoff gear (12);
the transmission comprises an I shaft (20), an II shaft (27), an output shaft (23) and a reverse gear shaft (18) which are supported on a box body (28) through bearings, wherein the output shaft (23) is sequentially provided with an output shaft gear (31), a high-gear output gear (25), a low-gear output gear (22) and an output flange (24) along the axial direction, an input shaft (14) with a first input gear (15) and a second input gear (32) which are different in tooth diameter is coaxially connected with the output shaft (23) through bearings, the two sides of the first input gear (15) and the second input gear (32) of the input shaft (14) are provided with an outer shaft diameter section and an inner shaft diameter section, the bearings arranged on the inner shaft diameter section of the input shaft (14) are connected on the box body (28), the bearings arranged on the outer shaft diameter section of the input shaft (14) are arranged in mounting holes on the inner side of the output shaft (23), and the outer side of the output shaft (23) is arranged on the box body (28) through bearings; the wet clutch K1 and the wet clutch K2 are connected to the I shaft (20) and are connected with a first driving gear (21) and a second driving gear (17) which are sleeved on the I shaft (20) and correspond to each other, an I shaft driven gear (16) at the input side of the I shaft (20) is normally meshed with a second input gear (32) with a small diameter, the first driving gear (21) is normally meshed with a low-gear output gear (22), and the second driving gear (17) is normally meshed with an output shaft gear (31), so that first-gear and second-gear forward power output is realized;
the wet clutch K3 and the wet clutch K4 are connected to the II shaft (27) and are connected with a third driving gear (30) and a fourth driving gear (26) which are respectively sleeved on the II shaft (27), a II shaft driven gear (33) at the input side of the II shaft (27) is normally meshed with a first input gear (15) with a large diameter, the third driving gear (30) is normally meshed with an output shaft gear (31), the fourth driving gear (26) is normally meshed with a high-gear output gear (25) to realize three-gear and four-gear forward power output and is matched with a locking clutch (4), and when the locking clutch (4) is connected with a driving disc (1) and is respectively combined with three-gear forward power and four-gear forward power, five-gear forward power output and six-gear forward power output are realized;
the reverse gear shaft (18) is provided with a reverse gear clutch Kr, an external gear of the reverse gear clutch Kr is normally meshed with an external gear of the wet clutch K1 or an external gear of the wet clutch K2, the reverse gear clutch Kr is connected with a reverse gear driving gear (19) sleeved on the reverse gear shaft (18), and the reverse gear driving gear (19) is normally meshed with a low gear output gear (22) to realize reverse gear power output;
the specific transmission route is as follows: advancing to I gear: an input shaft (14), a second input gear (32), an I-shaft driven gear (16), a wet clutch K1, a first drive gear (21), a low-gear output gear (22), and an output shaft (23); forward ii gear: an input shaft (14), a second input gear (32), an I-shaft driven gear (16), a wet clutch K2, a second drive gear (17), an output shaft gear (31), and an output shaft (23); advancing III gear: an input shaft (14), a first input gear (15), a second driven gear (33), a wet clutch K3, a third drive gear (30), an output shaft gear (31), and an output shaft (23); advancing IV gear: an input shaft (14), a first input gear (15), a second shaft driven gear (33), a wet clutch K4, a fourth driving gear (26), a high-speed output gear (25), and an output shaft (23); when the locking clutch (4) is connected with the driving disc (1), the locking clutch is combined with the forward III gear and the forward IV gear to form forward V gear and forward VI gear; reverse gear transmission: the transmission comprises an input shaft (14), a second input gear (32), an I-shaft driven gear (16), an external gear of a wet clutch K1 or a wet clutch K2, an external gear of a reverse clutch, a reverse clutch Kr, a reverse driving gear (19), a low-gear output gear (22) and an output shaft (23), wherein when the wet clutches K1, K2, K3 and K4 on an I shaft (20) and an II shaft (27) and the reverse clutch Kr on a reverse shaft (18) are all disengaged, no power is output, and the transmission is in a neutral operation, namely a neutral gear, so that a multi-gear structure of six forward gears and one reverse gear can be formed;
the second power takeoff gear (12) is arranged on the supporting shaft (9) through a bearing, the first power takeoff gear (8) is detachably connected to the second power takeoff gear (12), and the tooth thickness of the first power takeoff gear (8) is smaller than that of the second power takeoff gear (12);
the wet clutch K1 and the wet clutch K2 are arranged on the I shaft (20) back to back, an external gear is arranged on the same shell of the wet clutch K1 and the wet clutch K2, and a first driving gear (21) and a second driving gear (17) which are arranged on the I shaft (20) through needle bearings are positioned on two sides of the wet clutch K1 and the wet clutch K2;
the wet clutch K3 and the wet clutch K4 are arranged on the II shaft (27) back to back, the friction pair of the wet clutch K3 is the same as the friction pair of the wet clutch K4, and a third driving gear (30) and a fourth driving gear (26) which are arranged on the II shaft (27) through needle bearings are arranged on two sides of the wet clutch K3 and the wet clutch K4.
2. The hydraulic transmission for a light vehicle according to claim 1, wherein: the box body (28) comprises a front box body (28-2) for installing the hydraulic torque converter, a rear box body (28-3) for installing the transmission and a box cover (28-4) arranged on a rear wall plate (28-32) of the rear box body (28-3), and the front box body (28-2), the rear box body (28-3) and the box cover (28-4) are connected through fasteners after being positioned through positioning pins.
3. The hydraulic transmission for a light vehicle according to claim 2, characterized in that: the front box body (28-2) comprises an open cavity box body, a middle wallboard (28-21) and a rear wallboard (28-22), the driving disc (1), the locking clutch (4), the turbine (5), the guide wheel (3) and the pump wheel (6) are all arranged in the cavity box body, two sides of the oil pump driving sleeve (10) are arranged on the middle wallboard (28-21) and the rear wallboard (28-22) of the front box body (28-2) through bearings, the front side of the supporting shaft (9) is supported on the middle wallboard (28-21), the rear side is arranged on the rear wallboard (28-22) through fasteners, the connecting gear (7) is arranged on the middle wallboard (28-21) and the rear wallboard (28-22) of the front box body (28-2) through bearings, and the input shaft (14) is supported on the guide wheel seat (2) through bearings.
4. The hydraulic transmission for a light vehicle according to claim 2, characterized in that: the rear box body (28-3) is provided with a front wall plate (28-31), a rear wall plate (28-32) and a first middle baffle plate (28-33) and a second middle baffle plate (28-34) which are positioned in the rear box body (28-3), the box cover (28-4) is provided with bearing holes corresponding to shafts, the I shaft (20) is arranged on the first middle baffle plate (28-33) and the box cover (28-4) of the rear box body (28-3) through bearings, the reverse gear shaft (18) is arranged on the second middle baffle plate (28-34) and the box cover (28-4) of the rear box body (28-3) through bearings, the II shaft (27) is arranged on the front wall plate (28-31) and the box cover (28-4) of the rear box body (28-3) through bearings, and the rear side of the output shaft (23) is arranged on the box cover (28-4) through bearings, and the I shaft bearing cover (36), the II shaft bearing cover (37), the reverse bearing cover (38) and the output shaft cover (39) are arranged on the box cover (28-4) correspondingly.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710083190.1A CN106678326B (en) | 2017-02-16 | 2017-02-16 | Hydraulic speed variator for light vehicle |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710083190.1A CN106678326B (en) | 2017-02-16 | 2017-02-16 | Hydraulic speed variator for light vehicle |
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| CN106678326A CN106678326A (en) | 2017-05-17 |
| CN106678326B true CN106678326B (en) | 2024-01-26 |
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| CN201710083190.1A Active CN106678326B (en) | 2017-02-16 | 2017-02-16 | Hydraulic speed variator for light vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109296725B (en) * | 2018-11-22 | 2024-02-20 | 浙江金道科技股份有限公司 | Double-speed gearbox for small-tonnage forklift |
| CN110805689B (en) * | 2019-11-28 | 2023-05-09 | 重庆清平机械有限责任公司 | High-power density motor gear box mechanism for electric automobile |
| CN114811034A (en) * | 2022-05-06 | 2022-07-29 | 中国北方车辆研究所 | Wire control automatic gear shifting device for wheel type combat vehicle |
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| EP0412069A1 (en) * | 1989-08-01 | 1991-02-06 | IVECO FIAT S.p.A. | Hydromechanical power-shift transmission for motor vehicles, particularly for commercial vehicles |
| JPH07301302A (en) * | 1994-04-28 | 1995-11-14 | Aisin Aw Co Ltd | Power transmission device for vehicle |
| CN1851293A (en) * | 2006-05-18 | 2006-10-25 | 邓亚民 | Automobile ordinary geartrain hydraulic speed transmission |
| CN102182795A (en) * | 2011-03-30 | 2011-09-14 | 浙江万里扬变速器股份有限公司 | Transmission with three shafts and two clutches |
| CN102606708A (en) * | 2012-03-30 | 2012-07-25 | 杭州前进齿轮箱集团股份有限公司 | Multi-gear hydrodynamic transmission applicable to various working conditions |
| CN203214807U (en) * | 2012-02-23 | 2013-09-25 | 株式会社久保田 | Transmission of working vehicle |
| CN106369133A (en) * | 2016-09-09 | 2017-02-01 | 广西柳工机械股份有限公司 | Multi-gear hydrodynamic transmission |
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- 2017-02-16 CN CN201710083190.1A patent/CN106678326B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0412069A1 (en) * | 1989-08-01 | 1991-02-06 | IVECO FIAT S.p.A. | Hydromechanical power-shift transmission for motor vehicles, particularly for commercial vehicles |
| JPH07301302A (en) * | 1994-04-28 | 1995-11-14 | Aisin Aw Co Ltd | Power transmission device for vehicle |
| CN1851293A (en) * | 2006-05-18 | 2006-10-25 | 邓亚民 | Automobile ordinary geartrain hydraulic speed transmission |
| CN102182795A (en) * | 2011-03-30 | 2011-09-14 | 浙江万里扬变速器股份有限公司 | Transmission with three shafts and two clutches |
| CN203214807U (en) * | 2012-02-23 | 2013-09-25 | 株式会社久保田 | Transmission of working vehicle |
| CN102606708A (en) * | 2012-03-30 | 2012-07-25 | 杭州前进齿轮箱集团股份有限公司 | Multi-gear hydrodynamic transmission applicable to various working conditions |
| CN106369133A (en) * | 2016-09-09 | 2017-02-01 | 广西柳工机械股份有限公司 | Multi-gear hydrodynamic transmission |
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| CN106678326A (en) | 2017-05-17 |
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Effective date of registration: 20190618 Address after: 210001 Room 703, 4 Blocks, Amber Lane, Qinhuai District, Nanjing City, Jiangsu Province Applicant after: Deng Yamin Address before: 214181 Yaojiami 7, Zhetangbang, Qianzhou Street, Huishan District, Wuxi City, Jiangsu Province Applicant before: Chen Yunzhu |
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