CN105793607A - Speed change mechanism with gears overlap - Google Patents
Speed change mechanism with gears overlap Download PDFInfo
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- CN105793607A CN105793607A CN201580000487.6A CN201580000487A CN105793607A CN 105793607 A CN105793607 A CN 105793607A CN 201580000487 A CN201580000487 A CN 201580000487A CN 105793607 A CN105793607 A CN 105793607A
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- clutch
- gear
- speed
- driven pulley
- driving wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A speed change mechanism with gears overlap comprises a power input shaft (1), a power output shaft (3) and multiple parallel drive speed change units (2). The power input shaft (1), the multiple speed change units (2) and the power output shaft (3) are tandem driven sequentially. The speed change unit (2) includes a transmission (20), a clutch (24) and an overrunning clutch (23). The transmission (20) comprises a drive wheel (21) and a driven wheel (22). The transmission (20), the overrunning clutch (23) and the clutch (24) are tandem driven in any order. When the speed change mechanism works to transfer torque, none of the gears is interfered, the interference friction among the gears is small and the gears can overlap. When starting and upshifting, a variety of clutches can work simultaneously to make the starting and upshifting smooth and increase the transfer torque at the same time. When upshifting, the engaged low speed clutch does not need to be disconnected. When downshifting, the clutch only needs to be disconnected from high gears to low gears one by one to achieve downshifting. It has high degree of shift comfort, fast speed, large transmission torque, simple structure, simple control, fast slide, fuel economy and environment protection.
Description
The present invention relates to a kind of speed change gear, more particularly to a kind of overlapping speed change gear of gear, belong to machine driving speed change and become torsion technical field.
Speed changer is that, for changing the rotating speed from engine and the mechanism of torque, it can be fixed or stepping changes output shaft and input shaft gearratio, also known as gearbox.Speed changer generally comprises variable transmission mechanism and operating mechanism.Transmission mechanism uses greatly ordinary gear transmission, and what is also had uses Planetary Gear Transmission.
Speed changer is divided into manual, automatic two kinds, and manual transmission is mainly made up of gear and axle, and variable-speed torque-converting is produced by different gear combinations；And automatic transmission AT is made up of hydraulic torque converter, planetary gear and hydraulic control system, variable-speed torque-converting is reached by way of fluid power transmission and gear combination.The major function of speed changer is as follows：Change gearratio；In the case of hand engine rotation is constant, automobile is set to fall back traveling；Using neutral gear, power transmission is interrupted, starting, idling is enabled the engine to, be easy to shifting of transmission or carry out power output.
Automatic transmission AT is made up of hydraulic torque converter, planetary gear and hydraulic control system, and variable-speed torque-converting is reached by way of fluid power transmission and gear combination.Wherein hydraulic torque converter is the part of AT most features, and it is made up of components such as pump impeller, turbine and guide wheels, directly inputs engine power transmission moment of torsion and clutch action.Conventional speed changer has following several types：Hydraulic automatic speed variator, hydraulic drive automatic transmission, Electric Drive automatic transmission, stepped mechanical automatic transmission and stepless automatic speed changer for machine etc..Wherein, most commonly hydraulic automatic speed variator.Hydraulic automatic speed variator is mainly made up of the variable-speed gear system of hydraulic control, mainly includes automatic clutch and automatic transmission two large divisions, and it can automatically carry out gear shift according to the change of the aperture and speed of throttle.
Common automatic transmission is divided into CVT bunchers, AT automatic transmission, DCT double-clutch speed changers, parallel shaft transmission and AMT formula automatic transmission by taking automobile as an example.Above speed changer is when converting gear, and the quantity of executive component is more, gear interference friction is big, handoff procedure complexity between each gear, control program is more, the complicated cumbersome fault rate of maintenance is high, the problems such as gear shift overlying interference between each gear, influence shift quality are also easy to produce in gearshift procedure.As AMT shifting of transmission smoothes out difference slowly；CVT speed changer load is small, anxious to accelerate easily to skid；DCT speed changer cost height is complicated, and buty shifting fault rate is high, it is impossible to odd or even number trip stop, and dry clutch easily produces too many heat, and wet clutch frictional force is again inadequate；AT automatic transmission reacts slow to velocity variations, the problems such as complicated oil consumption is high.
The content of the invention
The problem to be solved in the present invention is how to allow the gear shifting quality of gearbox more comfortable, and switching speed faster, is passed
Dynamic torque is bigger, and structure is simpler, controls easier, fuel-saving environmental protection.
To realize above-mentioned goal of the invention, the invention provides a kind of overlapping speed change gear of gear.
Multiple driving wheels are housed, each driving wheel is corresponding with a gear on a kind of overlapping speed change gear of gear, including power input shaft, power output shaft, power input shaft, multiple driven pulleys are accordingly housed on power output shaft, each driven pulley is corresponding with a gear；
Selector shaft is provided with power input shaft, one end of selector shaft is fixed with piston, and the outside of piston is the first oil pressure chamber for controlling gear shift；One-way clutch and clutch are provided with each driving wheel, clutch can be in bonding state by the oil pressure cntrol of the first oil pressure chamber, power input shaft drives the working end of driving wheel to rotate by clutch, and the working end of driving wheel is engaged with the driven pulley on power output shaft.
Wherein more preferably, one-way clutch is on power input shaft, and clutch is located at the outside of one-way clutch；Clutch oil pocket and clutch plunger are provided with driving wheel, clutch oil pocket can be connected with the first oil pressure chamber, clutch plunger can make clutch be in bonding state by oil pressure actuated.
A kind of overlapping speed change gear of gear, including power input shaft, power output shaft, multiple driving wheels are housed on power input shaft, each driving wheel is corresponding with a gear, multiple driven pulleys are accordingly housed, each driven pulley is corresponding with a gear on power output shaft, selector shaft is provided with power output shaft, one end of selector shaft is fixed with piston, and the lateral compartments of piston are the 3rd oil pressure chamber for controlling gear shift；One-way clutch and clutch are provided with each driven pulley, clutch can be in bonding state by the oil pressure cntrol of the 3rd oil pressure chamber, and driven pulley drives power output shaft to rotate by clutch.
Wherein more preferably, the one-way clutch in driven pulley is on power output shaft, and clutch is located at the outside of one-way clutch；Clutch oil pocket and clutch plunger are additionally provided with driven pulley, clutch oil pocket can be connected with the 3rd oil pressure chamber, clutch plunger can make clutch be in bonding state by oil pressure actuated.
A kind of overlapping speed change gear of gear, including power input shaft, power output shaft, at least seven driving wheels are housed on power input shaft, each driving wheel is corresponding with a gear, at least seven driven pulleys are accordingly housed on power output shaft, each driven pulley is corresponding with a gear, the power input shaft is provided with first grade of driving wheel, second gear driving wheel, third gear driving wheel, fourth speed driving wheel, fifth speed driving wheel, sixth speed driving wheel and seventh speed driving wheel, the power output shaft is provided with first grade of driven pulley, second gear driven pulley, third gear driven pulley, fourth speed driven pulley, fifth speed driven pulley, sixth speed driven pulley and seventh speed driven pulley, clutch and freewheel clutch are provided with the outside of each driven pulley or driving wheel, clutch is by gear shift oil pressure cntrol, power output shaft drives the working end of driven pulley to rotate by clutch and freewheel clutch, engaged with the driving wheel on power input shaft the working end of driven pulley, or power input shaft drives the working end of driving wheel to rotate by clutch and freewheel clutch, engaged with the driven pulley on power output shaft the working end of driving wheel.
Wherein more preferably, clutch and freewheel clutch are provided with the outside of each driven pulley, clutch is by gear shift oil pressure cntrol, power output shaft drives the working end of driven pulley to rotate by clutch and freewheel clutch, engaged with the driving wheel on power input shaft the working end of driven pulley, wherein, first grade of driven pulley with this
Two grades of driven pulleys are clutch type connection altogether；The third gear driven pulley is that super-clutch type is connected altogether with the fourth speed driven pulley；The fifth speed driven pulley, the sixth speed driven pulley are connected with power output shaft by clutch connecting shaft delivery type respectively, and the seventh speed driven pulley is connected with power output shaft by freewheel clutch connecting shaft delivery type.
Wherein more preferably, clutch and freewheel clutch are provided with the outside of each driving wheel, clutch is by gear shift oil pressure cntrol, power input shaft drives the working end of driving wheel to rotate by clutch and freewheel clutch, engaged with the driven pulley on power output shaft the working end of driving wheel, wherein, first grade of driving wheel is that clutch type is connected altogether with the second gear driving wheel；The third gear driving wheel is that super-clutch type is connected altogether with the fourth speed driving wheel；The fifth speed driving wheel, the sixth speed driving wheel are connected with power input shaft by clutch connecting shaft delivery type respectively, and the seventh speed driven pulley is connected with power input shaft by freewheel clutch connecting shaft delivery type.
A kind of overlapping speed change gear of gear, including：The variable-speed unit of power input shaft, power output shaft and multiple parallel connection transmissions, the power input shaft, multiple variable-speed units, the power output shaft sequentially tandem sequence；
The variable-speed unit includes transmission device, clutch and freewheel clutch, and the transmission device includes driving wheel and driven pulley；
The transmission device and the clutch, freewheel clutch tandem sequence in any order.
Wherein more preferably, the transmission device, the clutch and the freewheel clutch sequentially tandem sequence.
Wherein more preferably, the clutch, the transmission device and the freewheel clutch sequentially tandem sequence.
Wherein more preferably, the transmission device, the freewheel clutch and the clutch sequentially tandem sequence.
Wherein more preferably, the freewheel clutch, the transmission device and the clutch sequentially tandem sequence.
Wherein more preferably, the clutch, the freewheel clutch and the transmission device sequentially tandem sequence.
Wherein more preferably, the freewheel clutch, the clutch and the transmission device sequentially tandem sequence.
Wherein more preferably, the variable-speed unit also includes engine braking clutch, the engine braking clutch and the freewheel clutch and/or clutch Parallel Control engine braking.
Wherein more preferably, in addition to by the power on the power input shaft transmit to the high-speed drive unit on the power output shaft, the high-speed drive unit includes transmission device and clutch；
The transmission device and the clutch tandem sequence.
Wherein more preferably, it is characterised in that using hub arrangement of clutch transmission altogether between the adjacent variable-speed unit.
Wherein more preferably, the hub arrangement of clutch altogether is arranged on power input shaft or power output shaft.
Wherein more preferably, the common hub of at least adjacent two grades of clutches and/or the freewheel clutch.
Wherein more preferably, in addition to brake, the brake is arranged on power output shaft or between power output shaft and differential mechanism.
Wherein more preferably, the power input shaft and/or power output sectional parallel are set.
Wherein more preferably, the power input shaft is segmented transfer of torque in parallel with the power output shaft；Or
The power output shaft subsection setup transmission moment of torsion in parallel with the power input shaft.
The overlapping speed change gear of gear that the present invention is provided, does not have interference friction between gear interference, each shelves small, gear can be with overlapping, and in starting and upshift, multiple clutches, which are simultaneously operable, makes starting in work transmission moment of torsion
Steadily increase transmission moment of torsion simultaneously with gear shift, the low or first gear clutch engaged need not be separated during upshift, during downshift, only need to cut-off clutch realizes downshift one by one from high tap position to low-grade location, shift procedure is simply various；Gear shift smooth-going is quick, and output torque is big, slides fast, switching speed is fast, fuel-saving environmental protection.
Fig. 1 is the overlapping speed change gear overall structure diagram of the gear of the invention provided；
Fig. 2 is the variable-speed unit structural representation of the embodiment of the present invention 1；
Fig. 3 is the variable-speed unit structural representation of the embodiment of the present invention 2；
Fig. 4 is the variable-speed unit structural representation of the embodiment of the present invention 3；
Fig. 5 is the variable-speed unit structural representation of the embodiment of the present invention 4；
Fig. 6 is the variable-speed unit structural representation of the embodiment of the present invention 5；
Fig. 7 is the variable-speed unit structural representation of the embodiment of the present invention 6；
Fig. 8-Figure 10 is that the embodiment of the present invention 7 increases the variable-speed unit structural representation of engine braking clutch；
Figure 11-Figure 12 is that the embodiment of the present invention 8 increases the variable-speed unit structural representation of high-speed cells；
Figure 13 is the variable-speed unit structural representation of the common hub of the freewheel clutch of the embodiment of the present invention 9；
Figure 14 is the variable-speed unit structural representation of the common hub of the clutch of the embodiment of the present invention 9；
Figure 15 is the variable-speed unit structural representation of the clutch of the embodiment of the present invention 9 and the common hub of engine braking clutch；
Figure 16 is that hub arrangement of clutch is arranged on the variable-speed unit structural representation on power input shaft to the embodiment of the present invention 9 altogether；
Figure 17-Figure 18 is the overlapping speed change gear structural representation of gear of multiple variable-speed units of the invention hub altogether；
Figure 19-21 is the overlapping speed change gear overall structure diagram of the multiple identical variable-speed unit gears of the present invention；
Figure 22-23 is the overlapping speed change gear overall structure diagram of the multiple different variable-speed unit gears of the present invention；
Figure 24-25 is the overlapping speed change gear structural representation of the gear of the embodiment of the present invention 10；
Figure 26 is the overlapping speed change gear structural representation of the gear of the embodiment of the present invention 11.
With reference to the accompanying drawings and examples, the embodiment to the present invention is described in further detail.Following examples are used to illustrate the present invention, but are not limited to the scope of the present invention.
As shown in figure 1, the present invention provides a kind of gear overlapping speed change gear, the overlapping speed change gear of the gear includes：The variable-speed unit 2 of power input shaft 1, power output shaft 3 and multiple parallel connection transmissions, power input shaft 1, multiple variable-speed units 2, the sequentially tandem sequence of power output shaft 3；Variable-speed unit 2 includes transmission device 20, freewheel clutch 23 and clutch 24, and transmission device 20 includes driving wheel 21, driven pulley 22；Driving wheel 21 and driven pulley 22 and freewheel clutch 23, the tandem sequence in any order of clutch 24.The speed change gear overlapping to the gear of the invention provided deploys to be described in detail below.
As shown in figure 1, the overlapping speed change gear of the gear of the invention provided, sets corresponding shelves according to actual needs
Position, one variable-speed unit 2 of each gear correspondence.As shown in Figures 2 to 7, in the corresponding variable-speed unit 2 of each gear of the invention, driving wheel 21 and driven pulley 22 can respectively be illustrated to the scheme that different order is driven respectively with multiple single embodiments (embodiment 1- embodiments 12) below with freewheel clutch 23, clutch 24 with a variety of sequential transmissions.
Embodiment 1
As shown in Fig. 2 in the present embodiment, driving wheel 21, driven pulley 22, clutch 24 and the sequentially tandem sequence of freewheel clutch 23.When being driven using the scheme of the present embodiment, driven pulley 22 is engaged with clutch 24, clutch 24 is engaged with freewheel clutch 23.Power is sequentially by the incoming driving wheel 21 of power input shaft 1, and driving wheel 21, driven pulley 22, clutch 24 and freewheel clutch 23 are sequentially driven, and are spread out of by freewheel clutch 23 to power output shaft 3.
Embodiment 2
As shown in figure 3, in the present embodiment, clutch 24, driving wheel 21, driven pulley 22 and the sequentially tandem sequence of freewheel clutch 23.When being driven using the scheme of the present embodiment, clutch 24 is engaged with driving wheel 21, and driven pulley 22 is engaged with freewheel clutch 23.Power is sequentially by the incoming clutch 24 of power input shaft 1, and driving wheel 21, driven pulley 22 and freewheel clutch 23 are sequentially driven, and power is spread out of to power output shaft 3 by freewheel clutch 23.
Embodiment 3
As shown in figure 4, in the present embodiment, driving wheel 21, driven pulley 22, freewheel clutch 23 and the sequentially tandem sequence of clutch 24.When being driven using the scheme of the present embodiment, driven pulley 22 is engaged with freewheel clutch 23, and freewheel clutch 23 is engaged with clutch 24.Power is sequentially by the incoming driving wheel 21 of power input shaft 1, and driving wheel 21, driven pulley 22, freewheel clutch 23 and clutch 24 are sequentially driven, and are spread out of by clutch 24 to power output shaft 3.
Embodiment 4
As shown in figure 5, freewheel clutch 23, driving wheel 21, driven pulley 22 and the sequentially tandem sequence of clutch 24.When being driven using the scheme of the present embodiment, freewheel clutch 23 is engaged with driving wheel 21, and driven pulley 22 is engaged with clutch 24.Power is sequentially by the incoming freewheel clutch 23 of power input shaft 1, and freewheel clutch 23, driving wheel 21, driven pulley 22 and the sequentially tandem sequence of clutch 24 are spread out of to power output shaft 3 by clutch 24.
Embodiment 5
As shown in fig. 6, in the present embodiment, clutch 24, freewheel clutch 23, driving wheel 21 and the sequentially tandem sequence of driven pulley 22.When being driven using the scheme of the present embodiment, clutch 24 is engaged with freewheel clutch 23, and freewheel clutch 23 is engaged with driving wheel 21.Power is sequentially by the incoming clutch 24 of power input shaft 1, and clutch 24, freewheel clutch 23, driving wheel 21 and the sequentially tandem sequence of driven pulley 22 are spread out of to power output shaft 3 by driven pulley 22.
Embodiment 6
As shown in fig. 7, in the present embodiment, freewheel clutch 23, clutch 24, driving wheel 21 and the sequentially tandem sequence of driven pulley 22.When being driven using the scheme of the present embodiment, freewheel clutch 23 is engaged with clutch 24, and clutch 24 is engaged with driving wheel 21.Power is sequentially by the incoming freewheel clutch 23 of power input shaft 1, and freewheel clutch 23, clutch 24, driving wheel 21 and the sequentially tandem sequence of driven pulley 22 are spread out of to power output shaft 3 by driven pulley 22.
Embodiment 7
The overlapping speed change gear of gear that the present invention is provided, can set corresponding engine braking clutch 25 in corresponding variable-speed unit 2 according to actual needs.The variable-speed unit 2 for needing to set engine braking clutch 25 can be any one variable-speed unit 2 of embodiment 1 into embodiment 6.Engine braking clutch 25 can with the parallel connection of freewheel clutch 23 can also with connect after freewheel clutch 23 and clutch 24 it is in parallel, engine braking clutch 25 can be arranged as required to, in the side of driving wheel 21, the side of driven pulley 22 can also be arranged on certainly.Choose below by taking variable-speed unit 2 of the embodiment 1 into embodiment 6 as an example, set the embodiment of engine braking clutch 25 to illustrate to the present invention.As shown in figure 8, the variable-speed unit 2 in embodiment 1 also includes engine braking clutch 25, engine braking clutch 25 and the freewheel clutch 23 and the Parallel Control engine braking of clutch 24 that are in series.As shown in figure 9, the variable-speed unit 2 in embodiment 3 also includes engine braking clutch 25, engine braking clutch 25 and the Parallel Control engine braking of freewheel clutch 23.As shown in Figure 10, the variable-speed unit 2 in embodiment 2 also includes engine braking clutch 25, the braking in parallel with freewheel clutch 23 of engine braking clutch 25.Variable-speed unit 2 in other embodiments still can set corresponding engine braking clutch 25, can also realize the function with above-mentioned example, will not enumerate repeat herein.Can be without engine braking clutch 25 when generator is braked to vehicle if be converted into oil and electricity hybrid vehicle using motor.
Embodiment 8
As shown in figure 1, the overlapping speed change gear of the gear of the invention provided, in addition to the power on power input shaft 1 is transmitted to the high-speed drive unit 4 on power output shaft 3.In order to reduce abrasion, the life-span of speed changer is improved, as shown in figure 11, high-speed drive unit includes driving wheel 21, driven pulley 22 and clutch 24；Driving wheel 21, driven pulley 22 and the tandem sequence in any order of clutch 24.When being driven using the scheme of the present embodiment, clutch 24 is engaged with driven pulley 22.Power is sequentially by the incoming driving wheel 21 of power input shaft 1, driving wheel 21, driven pulley 22 and the sequentially tandem sequence of clutch 24, by being spread out of from clutch 24 to power output shaft 3.Of course it is to be understood that the present invention is not limited only to this, as shown in figure 12, clutch 24 is arranged on power input shaft 1 by high-speed drive unit can also realize the present invention.Specific transmission process is basically identical with such scheme, just no longer repeats one by one herein.High-speed drive unit is highest gear, most high-grade to install freewheel clutch 23 additional for clutch coupling type, effectively can prevent freewheel clutch from wearing and tearing.
Embodiment 9
The overlapping speed change gear of gear that the present invention is provided, can make between adjacent variable-speed unit 2 using hub arrangement of clutch transmission altogether according to actual needs.Of course it is to be understood that the present invention is not limited only to this, the clutch 24, freewheel clutch 23 and engine braking clutch 25 in multiple variable-speed units 2 can also be using hub arrangement of clutch transmissions altogether.Hub arrangement of clutch can be arranged on power input shaft 1 altogether, can also be arranged on power output shaft 3.Adjacent variable-speed unit 2 can set common hub arrangement of clutch to be driven according to actual needs, by setting hub arrangement of clutch transmission altogether to reduce gearbox volume.Hub arrangement of clutch includes altogether：Two clutches 24 or two freewheel clutches 23 are provided with two-sided hub, the two-sided hub.Multiple arrangement of clutch can be included in hub arrangement of clutch altogether, can be clutch 24, freewheel clutch 23 and/or engine braking clutch 25.As shown in figure 13, in the embodiment, hub arrangement of clutch is arranged on power output shaft 3 altogether, the common hub of freewheel clutch 23 of two neighboring gear unit.As shown in figure 14, in the embodiment, hub arrangement of clutch is arranged on power output shaft 3 altogether, and the common hub of clutch 24 of two neighboring gear unit is simultaneously arranged on power output shaft 3.As shown in figure 15, it is of course possible to understand, engine braking clutch 25 can also be using hub altogether.Hub is arranged on power output shaft 3 clutch 24 and engine braking clutch 25 of two neighboring gear unit altogether.Hub arrangement of clutch can also be arranged on power input shaft 1 altogether, as shown in figure 16, and the common hub of clutch 24 and freewheel clutch 23 of two neighboring gear unit is simultaneously arranged on power input shaft 1.Herein it should be noted that, in the speed change gear that the present invention is provided, clutch 24, freewheel clutch 23 or the engine braking clutch 25 of two variable-speed units 2 of arbitrary neighborhood of the embodiment 2 into embodiment 6 can be arranged on power input shaft 1 or on power output shaft 3 while hub altogether, implementation and Figure 13 to Figure 16 are substantially similar, will not enumerate repeat herein.As shown in figure 17, multiple variable-speed units can pass through a common common hub of hub arrangement of clutch in the present invention, first grade of clutch 24, second gear clutch 24, third gear clutch 24, fourth speed clutch 24 are using the common hub form of clutch, and the scheme relative to Figure 13 to Figure 16 more saves the space of speed change gear.As shown in figure 18, in another the present invention program, multiple variable-speed units can pass through a common common hub of hub arrangement of clutch, first grade of clutch 24, second gear clutch 24, third gear clutch 24, fourth speed clutch 24 are using the common hub form of clutch, fifth speed clutch 24, sixth speed clutch 24, seventh speed clutch 24, eighth speed clutch 24 are using the common hub form of clutch, and fifth speed freewheel clutch 23, sixth speed freewheel clutch 23, seventh speed freewheel clutch 23, eighth speed freewheel clutch 23 are using the common hub form of freewheel clutch.
As shown in figure 19, the overlapping speed change gear of gear that the present invention is provided is using first grade to the multiple variable-speed units 2 of sixth speed hub altogether, the automatically controlled oil clutch 24X and 24Y of use of this programme, the overlapping speed change gear of the gear also includes control system part, and the control system part includes：The clutch controller A and oil pump main oil pressure adjusting means C being connected with clutch controller, first grade to third gear clutch hydraulic adjustment device D, fourth speed to sixth speed clutch hydraulic adjustment device E, first grade to third gear clutch oil pressure sensing device F, fourth speed to sixth speed clutch oil pressure sensing device G and with oil pump main oil pressure adjusting means C lead to oil pump B；Oil pump main oil pressure adjusting means C is connected with first grade to third gear clutch hydraulic adjustment device D, fourth speed to sixth speed clutch hydraulic adjustment device E；First grade to third gear clutch oil pressure sensing device F and first grade to third gear from
Close hydraulic adjustment device D connections；Fourth speed is connected with fourth speed to sixth speed clutch hydraulic adjustment device E to sixth speed clutch oil pressure sensing device G.First grade connects to third gear clutch oil pressure sensing device F, with the first oil pressure chamber 27X,.Fourth speed is connected with the second oil pressure chamber 27Y to sixth speed clutch oil pressure sensing device G, the overlapping speed change gear of gear that the present invention is provided also includes throttle sensor H and vehicle speed sensor I, throttle sensor H and vehicle speed sensor I are connected with clutch controller A, vehicle speed sensor I is connected with power output shaft 3, to oil pump main oil pressure adjusting means C after the GES COMPREHENSIVE CALCULATING that clutch control device A is detected by the throttle sensor H throttle signals detected and vehicle speed sensor I, first grade to third gear clutch hydraulic adjustment device D, fourth speed to sixth speed clutch hydraulic adjustment device E output control signals adjust each gear clutch.The specific work process of the overlapping speed change gear of the gear is such：
When the overlapping speed change gear of the gear that the present invention is provided is in neutral gear, clutch controller A adjusts main oil pressure power by oil pump main oil pressure adjusting means C, in case first grade uses to third gear clutch hydraulic adjustment device D, fourth speed to sixth speed clutch hydraulic adjustment device E, clutch controller A controls first grade to provide lubrication pressure, control fourth speed to sixth speed clutch hydraulic adjustment device E to fourth speed to sixth speed clutch 24Y and gear offer lubrication pressure to first grade to third gear clutch 24X and gear to third gear clutch hydraulic adjustment device D.
When the overlapping speed change gear of the gear that the present invention is provided brakes stopping in drive shift, clutch controller A adjusts main oil pressure power by oil pump main oil pressure adjusting means C, first grade of control provides oil pressure of creeping to third gear clutch hydraulic adjustment device D to first grade to third gear clutch 24X, and control fourth speed to sixth speed clutch hydraulic adjustment device E provides lubrication pressure to fourth speed to sixth speed clutch 24Y and gear.
When the overlapping speed change gear of the gear that the present invention is provided is started to walk in drive shift, clutch controller A adjusts main oil pressure power by oil pump main oil pressure adjusting means C, first grade of control provides starting oil pressure to third gear clutch hydraulic adjustment device D to first grade to third gear clutch 24X, the first shelves gear is entered from slip driving condition and be completely combined state, gearbox enters one grade of state, now second gear, third gear clutch is in sliding friction driving condition, enter preparation to rise up into two grades, clutch controller A is also by controlling fourth speed to sixth speed clutch hydraulic adjustment device E to fourth speed to sixth speed clutch 24Y and gear offer lubrication pressure.
When the overlapping speed change gear of the gear that the present invention is provided accelerates to upshift in drive shift, second gear clutch switchs to be completely combined state in sliding friction state, into second gear working condition, now first grade of clutch 24X is done in the case where the state that is completely combined is acted on by one grade of freewheel clutch 23 surmounts first grade of power interruption of operating, now third gear clutch is in sliding friction driving condition, now clutch controller A provides sliding pressure by fourth speed to sixth speed clutch hydraulic adjustment device E to fourth speed to sixth speed clutch 24Y, it is ready for fourth speed to sixth speed work, speed gradually rises, first grade to third gear clutch hydraulic adjustment device D control clutch engagement oil gradually rise, third gear is from Frotteurism to bonding state, first grade, second gear enters and surmounts state, now fourth speed to sixth speed clutch hydraulic adjustment device E controls fourth speed to sixth speed clutch 24Y engagement oils gradually rise, fourth speed clutch enters from sliding friction driving condition is completely combined state,
First grade, second gear, third gear enter surmount state, fifth speed, sixth speed gradually enter bonding state from sliding friction state by that analogy.
When the overlapping speed change gear of the gear that provides of the present invention, when drive shift lift throttle slides downshift, clutch controller A first adjusts fourth speed and made to sixth speed clutch hydraulic adjustment device E in corresponding gear at fourth speed to sixth speed, controls first grade to make first grade to be in corresponding gear to third gear to third gear clutch hydraulic adjustment device D when speed drops to certain speed again.
The overlapping speed change gear of gear that the present invention is provided adjusts first grade to third gear clutch hydraulic adjustment device D, fourth speed to sixth speed clutch hydraulic adjustment device E by first grade to third gear clutch oil pressure sensing device F, fourth speed to sixth speed clutch oil pressure sensing device G and throttle sensor H and vehicle speed sensor I and controls the overlapping speed change gear of gear to lift shelves.
More than, embodiment is illustrated for a preferred scheme therein, and the overlapping speed change gear of the gear in other embodiments can also be realized with reference to the scheme in the present embodiment, then this is not just being repeated one by one.
As shown in figure 1, the overlapping speed change gear of the gear of the invention provided, sets corresponding gear, one variable-speed unit 2 of each gear correspondence according to actual needs.Different gears have the corresponding passive wheel diameter ratio of master.Driving wheel 21 is different with the diameter of follower 22, produces different gears.Reverse gear can add the control mode of clutch 24 using driving wheel 21 and follower 22 by idle wheel, or driving wheel 21 adds the connected mode of clutch 24 with follower 22 using chain, or power input shaft 1 and power output shaft 3 install the single control mode of planet additional, or the electric combination drive mode of oil realizes reverse gear by motor control.As shown in figures 20-21, the overlapping speed change gear of the gear of the invention provided, multiple gears can be driven using the identical variable-speed unit 2 into embodiment 6 of embodiment 1.As shown in Figure 22,23, the overlapping speed change gear of the gear of the invention provided, it is of course possible to which understanding can also be transmitted using a variety of variable-speed units 2 that a variety of variable-speed units 2 are driven into embodiment 6 combination of embodiment 1.
The overlapping speed change gear of gear that the present invention is provided, it is that pinion rotation can also select to be that chain is rotated that in gear, the driving wheel 21 of transmission device can be selected with driven pulley 22, certainly it is also an option that belt transmission.During using belt transmission, belt can be selected flexibly according to actual needs, for example cingulum, flat rubber belting, V-belt and special-shaped band.
The overlapping speed change gear of gear that the present invention is provided, realizes different gear torques outputs, it is necessary to set corresponding clutch 24, engine braking clutch 25 in each gear as needed.Wherein, clutch round engine brake coupling 25 can be friction clutch, embeddeding clutch, air flexible clutch, electromagnetic clutch, magnetic powder cluth, torque clutch (overload-release clutch), centrifugal clutch, and the control method of clutch has：Surge control, pneumatic control, Mechanical course, Electromagnetic Control, automatically control.Wherein, freewheel clutch 23 is called referred to as finder, one-way clutch or unilateral bearing, freewheel clutch 23 transmits moment of torsion using the wedge action of roller voussoir, when power input shaft 1 drives rotating speed to be more than power output shaft 3 by driving rotating speed by variable-speed unit, moment of torsion is transmitted in wedge action, and when power output shaft 3 drives rotating speed by driving rotating speed more than power input shaft 1, interruption moment of torsion, which is operated in, surmounts state.
In the overlapping speed change gear of the gear of the invention provided, when switching between different gears, the stackable Engagement Control of clutch 24, the low or first gear engaged during upshift is without disconnecting.Described in detail below using multiple gear switch processes of the clutch 24 for hydraulic clutch as the preference speed change gear overlapping to the gear of the invention provided.During one gear clutch engaging work, multiple gear clutchs 24, which are slidably engaged, assists work upshift.During starting, other slidable engagements of gear clutch 24 assist one grade of work while one grade of clutch 24 works, switch to bonding state from more than this grade sliding engagement state of clutch 24 during upshift progressively to upshift, less than this grade clutch 24 in the case where freewheel clutch 23 surmounts work without disconnect.From top grade to low-grade sequentially opened clutch 24 during downshift.The control of each shelves clutch 24 is main to be controlled by computer according to engine load and speed.
When being worked from low grade to top grade, when the clutch 24 of which gear engages which gear is just delivered to the torsion from power input shaft 1 on power output shaft 3 by current gear driving wheel 21, driven pulley 22, clutch 24 and freewheel clutch 23.When being linked into drive shift, by single hydraulic control switch unit from the first gear clutch 24, second gear clutch 24, third gear clutch 24, fourth speed position clutch 24, fifth speed position clutch 24, sixth speed position clutch 24, seventh speed position clutch 24, eighth gear clutch 24, the overlapping offer engagement oil of clutch 24 is upshiftd ninth speed position clutch 24 to tenth speed position clutch 24 one by one, and downshift is realized from top grade to the low-grade engagement oil of cut-off clutch 24 successively.Or one to multiple shelves provide oil pressure and realize that starting upshifts and downshifted by changing charge oil pressure simultaneously, due to the interference of no gear, multiple gears are simultaneously operable, during starting when certain clutch 24 starts to walk pressure, low-grade wheel drive torque is more than the high-grade first engaging work of wheel drive torque when multiple range pressures are consistent, and high-grade wheel drive torque is small to carry out frictional engagement driving.When speed gradually rises, the driving moment of automobile is gradually reduced, and high tap position gradually switchs to engagement driving from friction-driven.When many gears are simultaneously engaged with, when high tap position is fully engaged as active transfer torsion, although low-grade location engagement carries out surmounting work by freewheel clutch 23, torsion is not transmitted.First gear engine braking clutch 25 and the second gear engine braking clutch 25 are mainly used in controlling engine braking, and required gear is installed at according to actual needs.In order to extend gearbox service life, gearbox is most high-grade to be not added with freewheel clutch 23.Power input shaft 1 passes through the work engagement driving driving wheel 21 of clutch 24, driving wheel 21 drives driven pulley 22, driven pulley 22 drives the working end of power output shaft 3 to rotate by freewheel clutch 23, due to the interference of no gear, multi gear is simultaneously operable, the clutch 24 on power output shaft 3 from low grade to high-gear clutch 24 can simultaneously fuel feeding, lift gear by adjusting charge oil pressure, oil pressure is gradually risen as shifting up operation, and oil pressure is gradually reduced to downshift process afterwards.Also can by from low grade to high-gear clutch 24 overlapping fuel system 24 realize lifting shelves by shelves oil-break mode from top grade to low regime clutch again.Shift procedure of the present invention simply smoothes out, and gear shift interference problem will not occur for multi gear, and can effectively improve switching speed simultaneously.
In order to shorten speed changer length as far as possible, to adapt to different use environments, when engine is excessive for the numbers of gear steps of horizontal engine or speed change gear, power input shaft 1 and/or power output shaft 3 are driven using drive part by part mode.The driving of drive part by part formula is inputted, power input shaft 1 is divided into two sections and is parallel to the two ends of power output shaft 3 transmission moment of torsion；Using output drive part by part formula driving, power output shaft 3 be divided into two sections be parallel to it is dynamic
Transmit moment of torsion in the two ends of power input shaft 1.The sectional of power input shaft 1 is connected in parallel on power output shaft 3 to transmit moment of torsion；Or the sectional of power output shaft 3 is connected in parallel on power input shaft 1 to transmit moment of torsion.
Due to the interference of no gear, shifted up during upshift on shelves, without interrupting or slowing down engine driving torque, the low-grade location engaged is without disconnecting, only need to be from high tap position to the clutch 24 of low-grade location variable-speed unit 2 oil-break one by one during downshift, can arbitrarily odd number or even number trip stop, also can be from up to deep low gear or from deep low gear to most high-grade trip stop.Also can adjacent multiple different clutches 24 of gear speed-changing unit 2 can simultaneously fuel feeding, gear is lifted by adjusting the charge oil pressure of clutch 24, the oil pressure of the different clutches 24 of gear speed-changing unit 2 is gradually risen as shifting up operation, the oil pressure of the clutch 24 of different gear speed-changing units 2 is gradually reduced to downshift process afterwards, and a gear engages multiple gears and assists to promote working gear.Such two kinds of gear changing modes substantially increase gear shift smooth degree, improve switching speed, increase driving torque., without double clutch, without valve body, manufacturing cost can be substantially reduced without torque-converters in structure.Due to can be without engine braking clutch 25 when there is no engine braking, generator is converted into instead of the completion engine braking of engine braking clutch 25 by motor in electric hybrid vehicle of oil, more improve and reclaim braking energy for motor-driven vehicle, save fuel oil.Also can be using electronic-controlled engine braking different mode control, such as economic model；Snow field mode and slope mode etc..
Embodiment 10
As shown in figure 24, multiple driving wheels are housed on the overlapping speed change gear power input shaft 1 of the gear of the invention provided, each driving wheel is corresponding with a gear, and multiple driven pulleys are accordingly housed on power output shaft 3, and each driven pulley is corresponding with a gear；In the present embodiment, provided with 5 forwards, 5 driving wheels, i.e., first grade driving wheel 21, second gear driving wheel 21, third gear driving wheel 21, fourth speed driving wheel 21, fifth speed driving wheel 21 are housed on corresponding power input shaft 1；It is corresponding equipped with 5 driven pulleys, i.e., first grade driven pulley 22, second gear driven pulley 22, third gear driven pulley 22, fourth speed driven pulley 22, fifth speed driven pulley 22 on power output shaft 3.
Selector shaft 7 is provided with power input shaft 1, one end of selector shaft 7 is fixed with piston 26, and the outside of piston 26 is the first oil pressure chamber 27 for controlling gear shift.
As shown in Figure 24, Figure 25, freewheel clutch 23 and clutch 24 are provided with each driving wheel, clutch 24 is hydraulic control friction disk type or hand operated speed gear box synchronous device formula, and freewheel clutch 23 is sprag type one-way bearing, overrunning cluth or one-way damper.Freewheel clutch 23 is on power input shaft 1, and clutch 24 is located at the outside of freewheel clutch 23, and power input shaft 1 drives the working end of driving wheel to rotate by clutch 24, and the working end of driving wheel is engaged with the driven pulley on power output shaft 3；Clutch oil pocket 241 and clutch plunger 242 are additionally provided with driving wheel, clutch oil pocket 241 can be connected with the first oil pressure chamber 27, clutch plunger 242 can be by oil pressure actuated, and bonding state can be in by the oil pressure cntrol of the first oil pressure chamber 27 by clutch 24 is in bonding state, i.e. clutch 24.
Reverse gear driving wheel 81 is also equipped with power input shaft 1, power output shaft 3 is accordingly equipped with reverse gear driven pulley 82, and reverse idler gear 80, reverse idler gear are provided between reverse gear driving wheel 81 and reverse gear driven pulley 82
80 on reversing shaft 85；The second oil pressure chamber 86 being correspondingly provided with the clutch 24 by oil pressure cntrol, power input shaft 1 for controlling reverse gear is provided with reverse gear driving wheel 81, power input shaft 1 drives reverse gear driving wheel 81 to rotate by clutch 24.
Being equipped with power input shaft 1 is used for the oil pump 9 for the first oil pressure chamber 27 and the fuel feeding of the second oil pressure chamber 86, and oil pump 9 is gear pump, is driven by power input shaft 1.
During work, it is linked into drive shift, selector shaft 7 is moved to the left, hydraulic oil in first oil pressure chamber 27 enters in the clutch oil pocket 241 of first grade of driving wheel 21, clutch plunger 242 is promoted to combine clutch 24, i.e. clutch 24 is in bonding state, the power of power input shaft 1 is delivered to by the freewheel clutch 23 in first grade of driving wheel wheel 21, clutch 24, the working end of first grade of driving wheel 21 and one grade of driven pulley 22 on power output shaft 3, one grade of work；When selector shaft 7 continues to move left to second gear 21 correspondence position of driving wheel, hydraulic oil in first oil pressure chamber 27 enters the clutch oil intracavitary of second gear driving wheel 21 (i.e. with the movement of selector shaft, the space of first oil pressure chamber changes therewith), the clutch of second gear driving wheel 21 is set to be in bonding state, two grades of work；By that analogy, realize that 5 gear shifts are operated.The gear shift of selector shaft 7 automatically determines gear according to the rotating speed of power output shaft 3 and the driving load of power input shaft 1, is controlled by independent circuit drives.During driving upshift, the clutch of each gear is combined one by one in gearbox, combined low-regime clutch is without separation, upshift one by one, the clutch previously combined during downshift is separated one by one from high to low, and clutch is in upshift, in the absence of the separated program of bound low or first gear clutch, clutch downshift when, only need to from high tap position one by one cut-off clutch realize downshift.
When reverse gear R is linked into when using, reverse idler gear 80 is combined with reverse gear driving wheel 81 and reverse gear driven gear 82, second oil pressure chamber 86 combines the clutch 24 in reverse gear driving wheel 81, the power of power input shaft 1 is delivered to by clutch 24, reverse gear driving wheel 81, idler gear 17, reverse gear driven gear 16 on power output shaft 3, travel vehicle backing.
Selector shaft is arranged in power output shaft, is provided with driven pulley in one-way clutch and clutch, power output shaft and is provided with selector shaft, one end of selector shaft is fixed with piston, and the lateral compartments of piston are the 3rd oil pressure chamber for controlling gear shift；One-way clutch and clutch are provided with each driven pulley, clutch can be in bonding state by the oil pressure cntrol of the 3rd oil pressure chamber, and driven pulley drives power output shaft to rotate by clutch.One-way clutch in driven pulley is on power output shaft, and clutch is located at the outside of one-way clutch；Clutch oil pocket and clutch plunger are additionally provided with driven pulley, clutch oil pocket can be connected with the 3rd oil pressure chamber, clutch plunger can make clutch be in bonding state by oil pressure actuated.Example of the shifting shaft of the course of work ibid in power input shaft.
The each driving wheel of speed change gear that the gear of the present embodiment offer is overlapping is interior provided with one-way clutch and clutch, power input shaft drives the working end of driving wheel to rotate by clutch, with the movement of selector shaft, the clutch of the corresponding gear of oil pressure cntrol of first oil pressure intracavitary is combined, and gear shift is realized, during driving upshift, the clutch of each gear is combined one by one in gearbox, combined low-regime clutch upshifts one by one without separation, drops
The clutch that had previously combined is separated one by one from high to low during shelves, and clutch is in upshift, in the absence of the separated program of bound low or first gear clutch, when clutch downshifts, only need to cut-off clutch realizes downshift one by one from high tap position.Only one of which executive component and a clutch job during gear shift of the present invention, shift procedure simply smooth out, and will not occur gear shift interference problem, and can effectively improve switching speed.
Embodiment 11
As shown in figure 26, the speed change gear that the gear of the present embodiment offer is overlapping includes power input shaft 1, power output shaft 3, at least seven driving wheels 21 are housed on power input shaft 1, each driving wheel 21 is corresponding with a gear, at least seven driven pulleys 22 are accordingly housed, each driven pulley 22 is corresponding with a gear on power output shaft 3.In the present embodiment, referring to Figure 26, provided with 7 driving wheels 21,7 driven pulleys 22.The power input shaft 1 is provided with first grade of driving wheel 21, second gear driving wheel 21, third gear driving wheel 21, fourth speed driving wheel 21, fifth speed driving wheel 21, sixth speed driving wheel 21 and seventh speed driving wheel 21.The power output shaft 3 is provided with first grade of driven pulley 22, second gear driven pulley 22, third gear driven pulley 22, fourth speed driven pulley 22, fifth speed driven pulley 22, sixth speed driven pulley 22 and seventh speed driven pulley 22.Each outside of driven pulley 22 is provided with clutch 24 and freewheel clutch 23, clutch 24 is by gear shift oil pressure cntrol, power output shaft 3 drives the working end of driven pulley 22 to rotate by clutch 24 and freewheel clutch 23, and the working end of driven pulley 22 is engaged with the driving wheel 21 on power input shaft 1.
As shown in figure 26, the each driven pulley side of speed change gear that the gear of the present embodiment offer is overlapping is provided with freewheel clutch 23 and clutch 24, clutch 24 is hydraulic control friction plate clutch or hand operated speed gear box synchronous device formula clutch, and freewheel clutch 23 is sprag type one-way bearing, overrunning cluth or one-way damper.
As shown in figure 26, the power output shaft 3 for the overlapping speed change gear of gear that the present embodiment is provided is provided with hub arrangement of clutch altogether, hub arrangement of clutch is built with first grade of clutch 24 and second gear clutch 24 altogether, and provided with first grade of engine braking clutch 25 between first grade of clutch and second gear clutch, first grade of freewheel clutch 23 of connection in first grade of clutch 24, first grade of driven pulley 22 of connection in first grade of freewheel clutch 23, connection second gear driven pulley 22 in connection second gear freewheel clutch 23, second gear freewheel clutch 23 in second gear clutch 24.
Power output shaft 3 is provided with hub arrangement of clutch altogether, the common hub arrangement of clutch is built with third gear freewheel clutch 23 and fourth speed freewheel clutch 23, connection third gear clutch 24 in third gear freewheel clutch 23, after third gear engine braking clutch 25 is in parallel with third gear freewheel clutch 23, third gear clutch 24, it is connected with third gear driven pulley 22, connection fourth speed driven pulley 22 in connection fourth speed clutch 24, fourth speed clutch 24 in fourth speed freewheel clutch 23.
Power output shaft 3 is provided with connection fifth speed freewheel clutch 23 in fifth speed clutch 24, the fifth speed clutch 24, the outer connection fifth speed driven pulley 22 of fifth speed freewheel clutch 23.Power output shaft 3 is provided with sixth speed clutch 24, the outside of sixth speed clutch 24 connection sixth speed freewheel clutch 23, the outside of sixth speed freewheel clutch 23 connection sixth speed driven pulley 22.
Power output shaft 3 is provided with seventh speed freewheel clutch 23, the outside of the seventh speed freewheel clutch 23 connection seventh speed clutch 24, and the outside of seventh speed clutch 24 is connected with seventh speed driven pulley 22.
As shown in figure 26, during the overlapping speed change gear work of gear that the present embodiment is provided, when the clutch 24 of which gear is just delivered to the torsion from power input shaft 1 on power output shaft 3 by this gear driving wheel 21, driven pulley 22, clutch 24 and freewheel clutch 23 with reference to which gear.When being linked into drive shift, by single hydraulic control switch unit from first grade of clutch 24, second gear clutch 24, third gear clutch 24, fourth speed clutch 24, fifth speed clutch 24, sixth speed clutch 24 to seventh speed clutch 24 is superimposed offer clutch engagement oil and upshiftd one by one, and downshift is realized from top grade to low-grade cut-off clutch engagement oil successively.Or one to seven grade simultaneously provide oil pressure by change charge oil pressure realize upshift and downshift, due to the interference of no gear, multiple gears are simultaneously operable, during starting when certain clutch starts to walk pressure, the driving moment of low-grade driving wheel 21 and driven pulley 22 is big when all range pressures are consistent first combines work, and the driving moment of high-grade driving wheel 21 and driven pulley 22 is small to carry out frictional engagement driving.When speed gradually rises, the driving moment of automobile is gradually reduced, and high tap position gradually switchs to combine driving from friction-driven.When many gears are simultaneously engaged with, high tap position transmission torsion, although low-grade location does not transmit torsion with reference to carrying out surmounting work by freewheel clutch.First grade of engine brake 25 is mainly used in controlling engine braking with third gear engine brake 25, and required gear is installed at according to actual needs.In order to extend gearbox service life, gearbox is most high-grade to be not added with freewheel clutch.
Another gear superposition formula multistage automatic transmission, each outside of driving wheel 21 is provided with clutch 24 and freewheel clutch 23, clutch 24 is by gear shift oil pressure cntrol, power input shaft 1 drives the working end of driving wheel 21 to rotate by clutch 24 and freewheel clutch 23, and the working end of driving wheel 21 is engaged with the driven pulley 22 on power output shaft 3.Wherein, first grade of driving wheel 21 is that clutch type is connected altogether with the second gear driving wheel 21；The third gear driving wheel 21 is that super-clutch type is connected altogether with the fourth speed driving wheel 21；The fifth speed driving wheel 21, the sixth speed driving wheel 21 are connected with power input shaft 1 by clutch connecting shaft delivery type respectively, and seventh speed driven pulley 22 is connected with power input shaft 1 by the connecting shaft delivery type of freewheel clutch 23.It is that power input shaft in embodiment two is divided into two sections and is connected in parallel on power output shaft to transmit moment of torsion using power input shaft or power output shaft drive part by part formula, power input shaft segmented to shorten transmission length gear is excessive or during horizontal engine.Power output shaft segmented, is that power output shaft in embodiment one is divided into two sections and is connected in parallel on power input shaft to transmit moment of torsion.
In summary, the overlapping speed change gear of gear that the present invention is provided can be applied to automobile, motorcycle, electric car, steamer, military affairs, engineering, machinery, electric power, aviation, lathe, generating, industry, agricultural, etc. mechanical driving speed changing box and gear-box speed change, become drive technology field of turning round, more particularly to a kind of gear eclipsed form multistage automatic transmission.The overlapping speed change gear of gear of the invention, there is no gear interference in work transmission moment of torsion, interference friction is small between each shelves, gear can be with overlapping, in starting and upshift, multiple clutches, which are simultaneously operable, makes starting and gear shift steadily while increasing transmission moment of torsion, need not be the low or first gear clutch point engaged during upshift
Open, during downshift, only need to cut-off clutch realizes downshift one by one from high tap position to low-grade location, shift procedure is simply various；Gear shift smooth-going is quick, and output torque is big, slides fast, switching speed is fast, fuel-saving environmental protection.
Embodiment of above is merely to illustrate the present invention, and not limitation of the present invention, relevant person skilled in the art, without departing from the spirit and scope of the present invention, can also make a variety of changes and modification.Therefore all equivalent technical schemes fall within the protection category of the present invention.
The overlapping speed change gear of gear that the present invention is provided, there is no gear interference in work transmission moment of torsion, interference friction is small between each shelves, gear can be with overlapping, in starting and upshift, and multiple clutches, which are simultaneously operable, makes starting and gear shift steadily while increasing transmission moment of torsion, the low or first gear clutch engaged need not be separated during upshift, during downshift, only need to from high tap position, cut-off clutch realizes downshift one by one, shift procedure is simply various；Gear shift smooth-going is quick, and output torque is big, slides fast, switching speed is fast, and fuel-saving environmental protection possesses industrial applicibility.
Claims (22)
- A kind of overlapping speed change gear of gear, it is characterised in that：Including power input shaft, power output shaft, multiple driving wheels are housed on power input shaft, each driving wheel is corresponding with a gear, multiple driven pulleys are accordingly housed on power output shaft, each driven pulley is corresponding with a gear；Selector shaft is provided with power input shaft, one end of selector shaft is fixed with piston, and the outside of piston is the first oil pressure chamber for controlling gear shift；One-way clutch and clutch are provided with each driving wheel, clutch can be in bonding state by the oil pressure cntrol of the first oil pressure chamber, power input shaft drives the working end of driving wheel to rotate by clutch, and the working end of driving wheel is engaged with the driven pulley on power output shaft.
- The overlapping speed change gear of gear as claimed in claim 1, it is characterised in that：One-way clutch is on power input shaft, and clutch is located at the outside of one-way clutch；Clutch oil pocket and clutch plunger are provided with driving wheel, clutch oil pocket can be connected with the first oil pressure chamber, clutch plunger can make clutch be in bonding state by oil pressure actuated.
- A kind of overlapping speed change gear of gear, it is characterised in that：Including power input shaft, power output shaft, multiple driving wheels are housed on power input shaft, each driving wheel is corresponding with a gear, multiple driven pulleys are accordingly housed on power output shaft, each driven pulley is corresponding with a gear, selector shaft is provided with power output shaft, one end of selector shaft is fixed with piston, and the lateral compartments of piston are the 3rd oil pressure chamber for controlling gear shift；One-way clutch and clutch are provided with each driven pulley, clutch can be in bonding state by the oil pressure cntrol of the 3rd oil pressure chamber, and driven pulley drives power output shaft to rotate by clutch.
- The overlapping speed change gear of gear as claimed in claim 3, it is characterised in that：One-way clutch in driven pulley is on power output shaft, and clutch is located at the outside of one-way clutch；Clutch oil pocket and clutch plunger are additionally provided with driven pulley, clutch oil pocket can be connected with the 3rd oil pressure chamber, clutch plunger can make clutch be in bonding state by oil pressure actuated.
- A kind of overlapping speed change gear of gear, including power input shaft, power output shaft, at least seven driving wheels are housed on power input shaft, each driving wheel is corresponding with a gear, at least seven driven pulleys are accordingly housed on power output shaft, each driven pulley is corresponding with a gear, the power input shaft is provided with first grade of driving wheel, second gear driving wheel, third gear driving wheel, fourth speed driving wheel, fifth speed driving wheel, sixth speed driving wheel and seventh speed driving wheel, the power output shaft is provided with first grade of driven pulley, second gear driven pulley, third gear driven pulley, fourth speed driven pulley, fifth speed driven pulley, sixth speed driven pulley and seventh speed driven pulley, it is characterized in that：Clutch and freewheel clutch are provided with the outside of each driven pulley or driving wheel, clutch is by gear shift oil pressure cntrol, power output shaft drives the working end of driven pulley to rotate by clutch and freewheel clutch, engaged with the driving wheel on power input shaft the working end of driven pulley, or power input shaft drives the working end of driving wheel to rotate by clutch and freewheel clutch, the working end of driving wheel is engaged with the driven pulley on power output shaft.
- The overlapping speed change gear of gear as claimed in claim 5, it is characterised in that：Clutch and freewheel clutch are provided with the outside of each driven pulley, clutch is by gear shift oil pressure cntrol, power output shaft drives the working end of driven pulley to rotate by clutch and freewheel clutch, engaged with the driving wheel on power input shaft the working end of driven pulley, wherein, first grade of driven pulley is that clutch type is connected altogether with the second gear driven pulley；The third gear driven pulley is that super-clutch type is connected altogether with the fourth speed driven pulley；The fifth speed driven pulley, the sixth speed driven pulley are connected with power output shaft by clutch connecting shaft delivery type respectively, and the seventh speed driven pulley is connected with power output shaft by freewheel clutch connecting shaft delivery type.
- The overlapping speed change gear of gear as claimed in claim 5, it is characterised in that：Clutch and freewheel clutch are provided with the outside of each driving wheel, clutch is by gear shift oil pressure cntrol, power input shaft drives the working end of driving wheel to rotate by clutch and freewheel clutch, engaged with the driven pulley on power output shaft the working end of driving wheel, wherein, first grade of driving wheel is that clutch type is connected altogether with the second gear driving wheel；The third gear driving wheel is that super-clutch type is connected altogether with the fourth speed driving wheel；The fifth speed driving wheel, the sixth speed driving wheel are connected with power input shaft by clutch connecting shaft delivery type respectively, and the seventh speed driven pulley is connected with power input shaft by freewheel clutch connecting shaft delivery type.
- A kind of overlapping speed change gear of gear, it is characterised in that including：The variable-speed unit of power input shaft, power output shaft and multiple parallel connection transmissions, the power input shaft, multiple variable-speed units, the power output shaft sequentially tandem sequence；The variable-speed unit includes transmission device, clutch and freewheel clutch, and the transmission device includes driving wheel and driven pulley；The transmission device and the clutch, freewheel clutch tandem sequence in any order.
- The overlapping speed change gear of gear as claimed in claim 8, it is characterised in that the transmission device, the clutch and the freewheel clutch sequentially tandem sequence.
- The overlapping speed change gear of gear as claimed in claim 8, it is characterised in that the clutch, the transmission device and the freewheel clutch sequentially tandem sequence.
- The overlapping speed change gear of gear as claimed in claim 8, it is characterised in that the transmission device, the freewheel clutch and the clutch sequentially tandem sequence.
- The overlapping speed change gear of gear as claimed in claim 8, it is characterised in that the freewheel clutch, the transmission device and the clutch sequentially tandem sequence.
- The overlapping speed change gear of gear as claimed in claim 8, it is characterised in that the clutch, the freewheel clutch and the transmission device sequentially tandem sequence.
- The overlapping speed change gear of gear as claimed in claim 8, it is characterised in that the freewheel clutch, the clutch and the transmission device sequentially tandem sequence.
- The overlapping speed change gear of gear as described in claim 8-14 any one, it is characterised in that the variable-speed unit also includes engine braking clutch, the engine braking clutch and the freewheel clutch and/or clutch Parallel Control engine braking.
- The overlapping speed change gear of gear as described in claim 8-14 any one, it is characterized in that, also include transmitting the power on the power input shaft to the high-speed drive unit on the power output shaft, the high-speed drive unit includes transmission device and clutch；The transmission device and the clutch tandem sequence.
- The overlapping speed change gear of gear as described in claim 8-14 any one, it is characterised in that using hub arrangement of clutch transmission altogether between adjacent two or more variable-speed units.
- The overlapping speed change gear of gear as claimed in claim 17, it is characterised in that the hub arrangement of clutch altogether is arranged on power input shaft or power output shaft.
- The overlapping speed change gear of gear as claimed in claim 17, it is characterised in that at least adjacent two grades of clutches and/or the common hub of the freewheel clutch.
- The overlapping speed change gear of gear as described in claim 8-19 any one, it is characterised in that Also include brake, the brake is arranged on power output shaft or between power output shaft and differential mechanism.
- The overlapping speed change gear of gear as described in claim 8-20 any one, it is characterised in that power input shaft and/or the power output shaft sectional parallel is set.
- The overlapping speed change gear of gear as claimed in claim 21, it is characterised in that the power input shaft is segmented transfer of torque in parallel with the power output shaft；OrThe power output shaft subsection setup transmission moment of torsion in parallel with the power input shaft.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410434004.0A CN105370879B (en) | 2014-08-29 | 2014-08-29 | Isolated conjunction multistage automatic transmission |
| CN2014104340040 | 2014-08-29 | ||
| CN201510014762.1A CN104633017A (en) | 2015-01-13 | 2015-01-13 | Gear position overlapped type multistage automatic transmission |
| CN2015100147621 | 2015-01-13 | ||
| PCT/CN2015/079228 WO2016029719A1 (en) | 2014-08-29 | 2015-05-18 | Speed change mechanism with gears overlap |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105793607A true CN105793607A (en) | 2016-07-20 |
| CN105793607B CN105793607B (en) | 2019-08-30 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580000487.6A Active CN105793607B (en) | 2014-08-29 | 2015-05-18 | A kind of speed change gear of gear overlapping |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN105793607B (en) |
| WO (1) | WO2016029719A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111365436A (en) * | 2020-04-17 | 2020-07-03 | 丁红涛 | Automatic gearbox of power switch |
| CN114235394A (en) * | 2021-12-23 | 2022-03-25 | 苏州英特模汽车科技有限公司 | Variable speed loading mechanism and loading method |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110345205B (en) * | 2019-07-11 | 2024-02-13 | 杭州萧山江南通用机械有限公司 | Multi-output marine gearbox |
| CN212131211U (en) * | 2020-01-23 | 2020-12-11 | 熵零技术逻辑工程院集团股份有限公司 | Transmission mechanism |
| CN112984106B (en) * | 2020-04-02 | 2022-08-23 | 天津叠挡传动技术有限公司 | Clutch device with overlapped gears, speed changing device, power generation device and electric automobile |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2055882U (en) * | 1989-08-26 | 1990-04-11 | 勇化军 | Mechanical automatic transmission |
| CN1601148A (en) * | 2003-09-27 | 2005-03-30 | 江廷普 | Automatic stepless transmission gearbox |
| CN102678840A (en) * | 2012-04-25 | 2012-09-19 | 长城汽车股份有限公司 | Seven-gear transmission |
| US20140087911A1 (en) * | 2012-09-26 | 2014-03-27 | GM Global Technology Operations LLC | Multi-speed transmission with a one-way clutch |
| CN204025642U (en) * | 2014-08-29 | 2014-12-17 | 解利 | Isolated conjunction multistage automatic transmission |
| CN104633017A (en) * | 2015-01-13 | 2015-05-20 | 解利 | Gear position overlapped type multistage automatic transmission |
| CN105370879A (en) * | 2014-08-29 | 2016-03-02 | 解利 | Single-clutch and multi-level automatic transmission |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1749065A1 (en) * | 1990-05-03 | 1992-07-23 | Войсковая часть 26271 | Automatic transmission |
| CN2448617Y (en) * | 2000-09-04 | 2001-09-19 | 郭永志 | Electric control automatic speed variator for vehicle |
| CN2553186Y (en) * | 2002-07-26 | 2003-05-28 | 赵洪义 | All machinery wedging block type overrunning stepless automatic variable speed device |
| CN2643078Y (en) * | 2003-09-24 | 2004-09-22 | 杨庆成 | Automatic shifter for automobile or tricycle |
| CN100400940C (en) * | 2004-02-02 | 2008-07-09 | 杨斌彬 | Uninterruptible power gear speed variator |
| WO2010099315A1 (en) * | 2009-02-27 | 2010-09-02 | Nacco Materials Handling Group, Inc. | Power shift transmission with clutch pack overrun |
| JP2014031857A (en) * | 2012-08-06 | 2014-02-20 | Ntn Corp | Multi-shaft transmission |
-
2015
- 2015-05-18 CN CN201580000487.6A patent/CN105793607B/en active Active
- 2015-05-18 WO PCT/CN2015/079228 patent/WO2016029719A1/en active Application Filing
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2055882U (en) * | 1989-08-26 | 1990-04-11 | 勇化军 | Mechanical automatic transmission |
| CN1601148A (en) * | 2003-09-27 | 2005-03-30 | 江廷普 | Automatic stepless transmission gearbox |
| CN102678840A (en) * | 2012-04-25 | 2012-09-19 | 长城汽车股份有限公司 | Seven-gear transmission |
| US20140087911A1 (en) * | 2012-09-26 | 2014-03-27 | GM Global Technology Operations LLC | Multi-speed transmission with a one-way clutch |
| CN204025642U (en) * | 2014-08-29 | 2014-12-17 | 解利 | Isolated conjunction multistage automatic transmission |
| CN105370879A (en) * | 2014-08-29 | 2016-03-02 | 解利 | Single-clutch and multi-level automatic transmission |
| CN104633017A (en) * | 2015-01-13 | 2015-05-20 | 解利 | Gear position overlapped type multistage automatic transmission |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111365436A (en) * | 2020-04-17 | 2020-07-03 | 丁红涛 | Automatic gearbox of power switch |
| CN114235394A (en) * | 2021-12-23 | 2022-03-25 | 苏州英特模汽车科技有限公司 | Variable speed loading mechanism and loading method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105793607B (en) | 2019-08-30 |
| WO2016029719A1 (en) | 2016-03-03 |
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