CN102207172B - Multi-speed transmission - Google Patents
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- CN102207172B CN102207172B CN201110079952.3A CN201110079952A CN102207172B CN 102207172 B CN102207172 B CN 102207172B CN 201110079952 A CN201110079952 A CN 201110079952A CN 102207172 B CN102207172 B CN 102207172B
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Abstract
The present invention relates to multi-speed transmission.A kind of speed changer comprises input block, output block, intermediate member and simple planetary group, all these element coaxials.First countershaft and the second countershaft are arranged to and limit the second spin axis and the 3rd spin axis respectively.Speed changer has five groups of pitch wheels, and part group is arranged to and moment of torsion is delivered to countershaft from input block, and other groups are arranged to moment of torsion from corresponding of being delivered in intermediate member and simple planetary group countershaft.Each in seven torque-transmitting mechanisms can optionally engage, the different respective gears of described group of pitch wheel to be connected to corresponding or the fixed component in countershaft.Seven torque-transmitting mechanisms can engage in various combination mode, to set up multiple forward speed ratio and a reversing speed ratio between input block and output block.
Description
This application claims the interests of No. 2010112596 Russ P application that on March 31st, 2010 submits to, be all herein incorporated by reference to by it.
Technical field
The present invention relates to the multi-speed planetary gear-shift transmission with countershaft and simple planetary group, described countershaft has the gear setting up five groups of intermeshing transfer gears.
Background technique
Motor Vehicle comprises dynamical system, and it is made up of motor, multi-speed transmission and differential mechanism or main reducing gear.The integrated operation scope of multi-speed transmission by allowing motor multi-pass operation in its torque range to increase Motor Vehicle.The quantity of forward speed ratio available in speed changer determines the number of repetition of engine torque bands.Early stage automatic transmission has two velocity ranges.This severely limits the bulk velocity scope of vehicle, therefore need to produce the relative large motor of wide speed and torque range.This causes motor at the specific fuel consumption point operation of period outside most Available Point that cruise.Therefore, manual shift (layshaft transmission) is the most popular.
Along with three and four gear transmissions come out, the personage that drives more and more welcomes self shifter (planetary pinion) speed changer.These speed changers improve operating characteristics and the fuel economy of Motor Vehicle.The increase of number of ratios decreases the step-length between ratio, therefore, in normal Motor Vehicle acceleration situation, exchanges by making operator's fundamental sensation the shift quality improving speed changer less than ratio.
Have multi-speed transmission higher than four speed ratios than three and four gear transmissions in acceleration and fuel efficiency, provide further improvement.But the complexity of the usual increase of this speed changer, size and cost are unfavorable factors, may stop the use in some applications of these speed changers.
Summary of the invention
There is provided a kind of multi-speed transmission, it utilizes simple planetary group and uses many group pitch wheels and countershaft moment of torsion transfer case.Speed changer comprises input block, output block and intermediate member, all these element coaxials.Provide fixed component, such as transmission case.Speed changer also comprises simple planetary group.Input block, output block, intermediate member and simple planetary group are arranged coaxially to each other, to limit the first spin axis.First countershaft and the second countershaft limit the second spin axis and the 3rd spin axis respectively.The torque-transmitting mechanisms that seven energy selectivity engage, such as clutch, engaged with transmitting torque, thus set up various speed ratio.As used herein, " clutch " refers to rotary clutch or fixed clutch, and fixed clutch is also referred to as break.Different clutches can be friction clutcch, synchronizer, band clutch, the overrunning clutch selecting to engage, dog-clutch or other types clutch.
There is provided five groups of pitch wheels, part group is arranged to and moment of torsion is delivered to countershaft from input block, and other groups are arranged to and moment of torsion is delivered to intermediate member or simple planetary group from countershaft.These five groups of pitch wheels are also referred to as transfer gear.Often organize pitch wheel and other are organized pitch wheel axially spaced-apart and arrange.Each in seven torque-transmitting mechanisms can optionally engage, the different respective gears in described group of pitch wheel to be connected to corresponding or the fixed component in countershaft.Seven torque-transmitting mechanisms can engage with various combination, to set up multiple forward speed ratio and a reversing speed ratio between input block and output block.As used herein, " jointly rotate " be meant to rotate (that is, without relatively rotating) with identical speed.As used herein, " velocity ratio " is the ratio of the moment of torsion of output block and the moment of torsion of input block, and " speed ratio " is the ratio of the speed of input block and the speed of output block.
Realize most preferred embodiment of the present invention according to what describe in detail below in conjunction with accompanying drawing, above-mentioned feature and advantage of the present invention and other feature and advantage will be obvious.
The present invention also provides following scheme:
Scheme 1. 1 kinds of multi-speed transmissions, comprising:
Input block;
Output block;
Fixed component;
Intermediate member;
Simple planetary group;
Wherein, input block, output block, intermediate member and simple planetary group are arranged coaxially to each other, to limit the first spin axis;
First countershaft and the second countershaft limit the second spin axis and the 3rd spin axis respectively;
The torque-transmitting mechanisms that seven energy selectivity engage;
Five groups of pitch wheels, part group is arranged to and moment of torsion is delivered to countershaft from input block, and other groups are arranged to of to be delivered to from countershaft by moment of torsion intermediate member and simple planetary group; Often organize pitch wheel and other are organized pitch wheel axially spaced-apart and arrange;
Wherein, each in seven torque-transmitting mechanisms can optionally engage, the different respective gears in described group of pitch wheel to be connected to corresponding or the fixed component in countershaft; Wherein, seven torque-transmitting mechanisms can engage in various combination mode, to set up multiple forward speed ratio and a reversing speed ratio between input block and output block.
The multi-speed transmission of scheme 2. as described in scheme 1, wherein, simple planetary group has: first component, and it continues to be connected to intermediate member thus jointly rotates; Second component, it continues to be connected to output block thus jointly rotates; 3rd parts, it continues to be connected in the gear being arranged to and being delivered to from countershaft by moment of torsion in a group of described group of pitch wheel of simple planetary group thus jointly rotates.
The multi-speed transmission of scheme 3. as described in scheme 1, wherein, the first and second torque-transmitting mechanisms energy selectivity in seven torque-transmitting mechanisms engage, respectively the first countershaft and the second countershaft are fixed to fixed component.
The multi-speed transmission of scheme 4. as described in scheme 1, wherein, first group in five groups of pitch wheels and each group of second group of pitch wheel all comprise and are connected to input block thus the common respective gears rotated, around the rotatable respective gears of the first countershaft with around the rotatable respective gears of the second countershaft; Wherein, two in seven torque-transmitting mechanisms can selectivity engage, so that corresponding in the rotatable gear of the first countershaft is connected to the first countershaft thus jointly rotates respectively; Wherein, two other in seven torque-transmitting mechanisms can selectivity engage, so that corresponding in the rotatable gear of the second countershaft is connected to the second countershaft thus jointly rotates respectively.
The multi-speed transmission of scheme 5. as described in scheme 1, wherein, the 3rd group of pitch wheel in five groups of pitch wheels comprises: the first gear, and it is connected to input block thus jointly rotates; Second component, it is rotatable around the second countershaft; And the 3rd gear, it engages with the first gear and the second gear; Wherein, an energy selectivity in seven torque-transmitting mechanisms engages, the second gear is connected to the second countershaft thus jointly rotates.
Multi-speed transmission described in scheme 6. scheme 1, wherein, the 4th group of pitch wheel in five groups of pitch wheels comprises: the first gear, and it is connected to the second countershaft thus jointly rotates; With the second gear, itself and the first gears meshing and be connected to intermediate member thus jointly rotate.
Multi-speed transmission described in scheme 7. scheme 1, wherein, the 5th group of pitch wheel in five groups of pitch wheels comprises: the first gear, and it is connected to the first countershaft thus jointly rotates; With the second gear, itself and the first gears meshing and be connected to the parts of simple planetary group thus jointly rotate.
Multi-speed transmission described in scheme 8. scheme 1, wherein, in seven torque-transmitting mechanisms is synchronizer at least partially.
Multi-speed transmission described in scheme 9. scheme 8, wherein, four in seven torque-transmitting mechanisms are coaxial and be synchronizer about the 3rd spin axis, wherein, in seven torque-transmitting mechanisms other three coaxial and be rotate or fixed friction formula clutch about the second spin axis.
Multi-speed transmission described in scheme 10. scheme 9, wherein, seven torque-transmitting mechanisms can engage in combination of two mode, thus enter in each of front in speed ratio to engage about at least one of coaxial described four torque-transmitting mechanisms of the 3rd spin axis.
Multi-speed transmission described in scheme 11. scheme 1, wherein, seven torque-transmitting mechanisms can engage in different combination of two mode, to set up at least eight forward speed ratios and a reversing speed ratio between input block and output block, wherein, between the forward speed ratio of order, only a gearshift is two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift.
Multi-speed transmission described in scheme 12. scheme 1, wherein, seven torque-transmitting mechanisms can engage in different combination of two mode, to set up ten forward speed ratios and a reversing speed ratio between input block and output block, wherein, between the forward speed ratio of order, only two gearshifts are two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift.
Multi-speed transmission described in scheme 13. scheme 1, wherein, seven torque-transmitting mechanisms comprise two breaks and five rotary clutchs.
Multi-speed transmission described in scheme 14. scheme 1, wherein, seven torque-transmitting mechanisms energy selectivity engage to set up eight forward speed ratios, and wherein, the step-length ratio between the forward speed ratio of the order at least partially in forward speed ratio is identical.
Scheme 15. 1 kinds of multi-speed transmissions, comprising:
Input block;
Output block;
Fixed component;
Intermediate member;
Simple planetary group, the one group of small gear that there are sun gear parts, ring gear component, gear carrier parts and engage by gear carrier parts rotary support and with sun gear parts and ring gear component; Wherein, input block, output block, intermediate member and simple planetary group are arranged coaxially to each other, to limit the first spin axis;
First countershaft and the second countershaft limit the second spin axis and the 3rd spin axis respectively;
The torque-transmitting mechanisms that seven energy selectivity engage, comprises two breaks and five rotary clutchs;
Five groups of pitch wheels, part group is arranged to and moment of torsion is delivered to countershaft from input block, and other groups are arranged to moment of torsion from corresponding of being delivered in intermediate member and simple planetary group countershaft; Often organize pitch wheel and other are organized pitch wheel axially spaced-apart and arrange;
Wherein, sun gear parts are connected to intermediate member thus jointly rotate, and gear carrier parts are connected to output block thus jointly rotate, and ring gear component is connected in the parts of pitch wheel group thus jointly rotates;
Wherein, each in seven torque-transmitting mechanisms can optionally engage, the different respective gears in described group of pitch wheel to be connected to corresponding or the fixed component in countershaft; Wherein, seven torque-transmitting mechanisms can engage in different combination of two modes, to set up nearly ten forward speed ratios and a reversing speed ratio between input block and output block.
Multi-speed transmission described in scheme 16. scheme 15, wherein, seven torque-transmitting mechanisms can optionally engage, to set up eight forward speed ratios, wherein, between the forward speed ratio of order, only a gearshift is two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift; Wherein, seven torque-transmitting mechanisms energy selectivity engage, and to set up ten forward speed ratios, wherein, between the forward speed ratio of order, only two gearshifts are two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift.
Multi-speed transmission described in scheme 17. scheme 15, wherein, seven torque-transmitting mechanisms energy selectivity engage to set up eight forward speed ratios, and wherein, the step-length ratio between the forward speed ratio of the order at least partially in forward speed ratio is identical.
Accompanying drawing explanation
Fig. 1 is schematically illustrating of the clavate schematic form of the dynamical system with multi-speed transmission; And
Fig. 2 is the truth table of some operating characteristics describing the speed changer shown in Fig. 1.
Embodiment
With reference to accompanying drawing, wherein, identical label indicates identical parts.Fig. 1 illustrates dynamical system 10, and dynamical system 10 has motor 12(and is designated as E), the countershaft of combination and planetary transmission 14 and final drive mechanism 16(be designated as FD).All kinds fuel can be passed through to motor 12 energy supply, to improve efficiency and the fuel efficiency of application-specific.Such as, these fuel can comprise: gasoline, diesel oil, ethanol, dimethyl ether etc.Speed changer 14 comprises input block 17, and it continues to be connected, optionally by torque-converters with the output block of the motor 12 of such as bent axle.The output block 19 that speed changer 14 also comprises five groups of pitch wheels as described below, intermediate member 50, first countershaft 52, second countershaft 54, first planet gear train 20 and is connected with final drive mechanism 16 for providing propelling force to wheel.
Simple planetary group 20 comprises sun gear parts 22, ring gear component 24 and supports the gear carrier parts 26 of one group of small gear 27 rotatably.Small gear 27 engages with sun gear parts 22 and ring gear component 24.Sun gear parts 22 are called as the first component of simple planetary group 20, and are connected to intermediate member 50 thus jointly rotate.Gear carrier parts 26 are called as the second component of simple planetary group 20, and are connected to output block 19 thus jointly rotate.Ring gear component 24 is called as the 3rd parts of simple planetary group 20, and is connected to gear 92 thus jointly rotates.
Speed changer 14 comprises the multiple transmission shafts being arranged to restriction three different rotary axis A, B and C.Input block 17, output block 19, intermediate member 50 and planetary gear set 20 are coaxial and limit the first spin axis A.It is spaced apart that first countershaft 52 and the second countershaft 54 are parallel to the first spin axis A, and limit the second spin axis B and the 3rd spin axis C respectively.
First group of pitch wheel S1 is included in the gear 70,60 and 80 of the first face of gear P1 internal messing.Gear 60 is connected to input block 17 to rotate.Gear 70 engages with gear 60 and around countershaft 52 Concentric rotation.Gear 80 engages with gear 60 and around countershaft 54 Concentric rotation.Input block 17, countershaft 52 and 54, intermediate member 50 and output block 19 are supported to rotate by rigid bearing 56.
Second group of pitch wheel S2 is included in the gear 72,62 and 82 of the second face of gear P2 internal messing.Gear 62 is connected to input block 17 to rotate.Gear 72 engages with gear 62 and around countershaft 52 Concentric rotation.Gear 82 engages with gear 62 and around countershaft 54 Concentric rotation.
3rd group of pitch wheel S3 is included in the gear 64,69 and 84 of the 3rd face of gear P3 internal messing.Gear 64 is connected to input block 17 to rotate.Gear 69 engages with gear 64 and is connected to pony axle I to rotate.Gear 84 engages with gear 69 and around countershaft 54 Concentric rotation.
4th group of pitch wheel S4 is included in the gear 90 and 86 of the 4th face of gear P4 internal messing.Gear 90 is connected to intermediate member 50 to rotate.Gear 86 engages with gear 90 and is connected to countershaft 54 to rotate.
5th group of pitch wheel S5 is included in the gear 74 and 92 of the 5th face of gear P5 internal messing.Gear 74 is connected to countershaft 52 to rotate.Gear 92 engages with gear 74 and is connected to ring gear component 24 to rotate.
The sun gear parts 22 of planetary gear set 20, ring gear component 24 and small gear 27 are at the 6th face of gear P6 internal messing.Face of gear P1-P6 extends perpendicular to the drawing of Fig. 1.
Speed changer 14 also comprises seven torque-transmitting mechanisms: the first torque-transmitting mechanisms C1, the second torque-transmitting mechanisms C2, the 3rd torque-transmitting mechanisms C3, the 4th torque-transmitting mechanisms C4, the 5th torque-transmitting mechanisms C5, the 6th torque-transmitting mechanisms C6 and the 7th torque-transmitting mechanisms C7.Torque-transmitting mechanisms C3, C4, C5, C6 and C7 are rotary clutchs.Torque-transmitting mechanisms C1 and C2 is fixed clutch, is also referred to as break.Torque-transmitting mechanisms C1, C5 and the C6 concentric with countershaft 52 can be friction clutcches, and torque-transmitting mechanisms C2, C3, C4 and C7 concentric with countershaft 54 can be the synchronizer activated by selector fork (not shown), as is known to the person skilled in the art.By being placed adjacent to each other by all friction clutcches on identical countershaft 52, simplify the requirement of fluid route, this is because the hydraulic fluid flowing to clutch C1, C5 and C6 can mainly through public supply passage.The entire length simplifying hydraulic pressure supply passage and reduction supply passage simplifies the production of speed changer 14, and makes less pump be used for hydraulic system.In addition, if only clutch C1, C5 and C6 is friction clutcch, then according to the joint chart of Fig. 2 discussed below, in each speed ratio, only there are two clutches opened, limit spin loss.Alternatively, torque-transmitting mechanisms C2, C3, C4 and C7 also can be friction clutcches, or torque-transmitting mechanisms C2 and C7 can be Unilateral synchronizer and torque-transmitting mechanisms C3 and C4 can be bilateral synchronous device.Torque-transmitting mechanisms C5 and C6 also can be bilateral synchronous device.Synchronizer is used to replace clutch to decrease spin loss.In other embodiments, torque-transmitting mechanisms can be dissimilar clutch.
First torque-transmitting mechanisms C1 is also referred to as break C1, is fixed clutch, can selectivity engage so that countershaft 52 is fixed to fixed component 40, thus keeps gear 74 and ring gear component 24 to fix.Second torque-transmitting mechanisms C2 is also referred to as break C2, is fixed clutch, can selectivity engage so that countershaft 54 is fixed to fixed component 40, thus keeps gear 86, gear 90, intermediate member 50 and sun gear parts 22 to fix.3rd torque-transmitting mechanisms C3 is also referred to as clutch C3, is rotary clutch, can selectivity engage connection gear 80 is connected to countershaft 54 thus jointly rotates.4th torque-transmitting mechanisms C4 is also referred to as clutch C4, is rotary clutch, can selectivity engage gear 82 is connected to countershaft 54 thus jointly rotates.5th torque-transmitting mechanisms C5 is also referred to as clutch C5, is rotary clutch, can selectivity engage gear 70 is connected to countershaft 52 thus jointly rotates.6th torque-transmitting mechanisms C6 is also referred to as clutch C6, is rotary clutch, can selectivity engage gear 72 is connected to countershaft 52 thus jointly rotates.7th torque-transmitting mechanisms C73 is also referred to as clutch C7, is rotary clutch, can selectivity engage gear 84 is connected to countershaft 54 thus jointly rotates.
As shown in the truth table of Fig. 2, torque-transmitting mechanisms C1, C2, C3, C4, C5, C6 and C7 optionally can engage with combination of two, to provide up to ten forward speed ratios and reversing speed ratio (being listed as range state).List the umerical velocity ratio corresponding to speed ratio in fig. 2.Velocity ratio is the ratio of the moment of torsion of output block 19 and the moment of torsion of input block 17.
Because the 3rd and the 7th forward speed ratio is optional, in bracket, therefore list the 3rd and the 7th forward speed ratio.If these two speed ratios are all unavailable, then speed changer 14 is 8 speed transmissions, if one only in these two speed ratios available, then speed changer 14 is 9 speed transmissions.
The velocity ratio of the numeral set forth in Fig. 2 obtains from the number of teeth setting up following velocity ratio.Gear 70 is-0.5 with the velocity ratio of gear 60 and the velocity ratio of gear 80 and gear 60.Gear 72 is-1.0 with the velocity ratio of gear 62 and the velocity ratio of gear 82 and gear 62.Gear 84 is+1.0 with the velocity ratio of gear 64.Gear 90 is-2.0 with the velocity ratio of gear 86.Gear 92 is-1.5 with the velocity ratio of gear 74.Suppose that gear carrier parts 26 stop (only in order to calculate object), ring gear component 24 is-2.5 with the velocity ratio of sun gear parts 22.
Use the number of teeth listed above, there are 8 the gearing down speed ratios (first to the 8th) and two overdrive speed ratios (the 9th and the tenth) that produce the ratio step-length listed in Fig. 2.As shown in Figure 2, in the 3rd to the tenth forward speed ratio, ratio step-length is relatively uniform, because motor 12 only needs, in the operation of relatively narrow velocity range, therefore cause smooth and easy gear shift to be experienced and improve fuel efficiency at each speed ratio.
In order to set up reversing speed ratio (REV), engagement brake C1 and clutch C7.Because engagement brake C1, so keep ring gear component 24 to fix.Because engaging clutch C7, so moment of torsion is transmitted along countershaft 54 by pitch wheel 64,69 and 84, be delivered to sun gear parts 22 by pitch wheel 86 and 90, and be delivered to output block 19 by planetary gear set 20.Output block 19 rotates according to the direction contrary with input block 17.
In order to set up the first speed ratio, engagement brake C1 and clutch C4.Because engagement brake C1, so keep ring gear component 24 to fix.Because engaging clutch C4, so moment of torsion is delivered to countershaft 54 by pitch wheel 62 and 82 from input block 17, is delivered to sun gear parts 22 by pitch wheel 86 and 90, and is delivered to output block 19 by planetary gear set 20.At all forward speed ratios, input block 17 and output block 19 rotate with equidirectional.
In order to set up the second speed ratio, engagement brake C1 and clutch C3.Because engagement brake C1, so keep ring gear component 24 to fix.Because engaging clutch C3, so moment of torsion is delivered to countershaft 54 by pitch wheel 60,80 from input block 17, by pitch wheel 86,90 are delivered to sun gear parts 22, and are delivered to output block 19 by planetary gear set 20.Gearshift from the first speed ratio to the second speed ratio singly changes gearshift.
In order to set up the 3rd speed ratio, engaging clutch C6 and C7.Because engaging clutch C6, so moment of torsion is delivered to countershaft 52 by pitch wheel 62,72 from input block 17, by pitch wheel 74,92 are delivered to ring gear component 24.Because engaging clutch C7, so moment of torsion is delivered to countershaft 54 by pitch wheel 64,69,84 from input block 17, by pitch wheel 86,90 are delivered to sun gear parts 22.The moment of torsion that sun gear parts 22 place provides is added to the moment of torsion that ring gear component 24 place provides, thus arrive gear carrier parts 26 and output block 19 by planetary gear set 20.Gearshift from the second speed ratio to the 3rd speed ratio is two conversion gearshifts.
In order to set up the 4th speed ratio, engagement brake C2 and C6.Because engagement brake C2, so keep sun gear parts 22 to fix.Because engaging clutch C6, so moment of torsion is delivered to countershaft 52 by pitch wheel 62,72 from input block 17, by pitch wheel 74,92 are delivered to ring gear component 24, and are delivered to output block 19 by planetary gear set 20.Gearshift from the 3rd speed ratio to the 4th speed ratio singly changes gearshift.
In order to set up the 5th speed ratio, engaging clutch C4 and C6.Because engaging clutch C4, so moment of torsion is delivered to countershaft 54 by pitch wheel 62,82 from input block 17, by pitch wheel 86,90 are delivered to sun gear parts 22.Because engaging clutch C6, so moment of torsion is delivered to countershaft 52 by pitch wheel 62,72 from input block 17, by pitch wheel 74,92 are delivered to annular positive geared parts 24.Deduct the moment of torsion being supplied to sun gear parts 22 from the moment of torsion being supplied to ring gear component 24, and moment of torsion is delivered to gear carrier parts 26 and output block 19 by planetary gear set 20.Gearshift from the 4th speed ratio to the 5th speed ratio singly changes gearshift.
In order to set up the 6th speed ratio, engaging clutch C3 and C6.Because engaging clutch C3, so moment of torsion is delivered to countershaft 54 by pitch wheel 60,80 from input block 17, by pitch wheel 86,90 are delivered to sun gear parts 22.Because engaging clutch C6, so moment of torsion is delivered to countershaft 52 by pitch wheel 62,72 from input block 17, by pitch wheel 74,92 are delivered to annular positive geared parts 24.Deduct the moment of torsion being supplied to sun gear parts 22 from the moment of torsion being supplied to ring gear component 24, and moment of torsion is delivered to gear carrier parts 26 and output block 19 by planetary gear set 20.Gearshift from the 5th speed ratio to the 6th speed ratio singly changes gearshift.
In order to set up the 7th speed ratio, engaging clutch C5 and C7.Because engaging clutch C5, so moment of torsion is delivered to countershaft 52 by pitch wheel 60,70 from input block 17, by pitch wheel 74,92 are delivered to ring gear component 24.Because engaging clutch C7, so moment of torsion is delivered to countershaft 54 by pitch wheel 64,69 and 84 from input block 17, by pitch wheel 86,90 are delivered to sun gear parts 22.The moment of torsion being supplied to sun gear parts 22 adds the moment of torsion being supplied to ring gear component 24 to, and moment of torsion is delivered to gear carrier parts 26 and output block 19 by planetary gear set 20.Gearshift from the 6th speed ratio to the 7th speed ratio is two conversion gearshifts.
In order to set up the 8th speed ratio, engagement brake C2 and clutch C5.Because engagement brake C2, so keep sun gear parts 22 to fix.Because engaging clutch C5, so moment of torsion is delivered to countershaft 52 by pitch wheel 60,70 from input block 17, by pitch wheel 74,92 are delivered to ring gear component 24, are delivered to output block 19 by planetary gear set 20.Gearshift from the 7th speed ratio to the 8th speed ratio singly changes gearshift.
In order to set up the 9th speed ratio, engaging clutch C4 and C5.Because engaging clutch C5, so moment of torsion is delivered to countershaft 52 by pitch wheel 60,70 from input block 17, by pitch wheel 74,92 are delivered to ring gear component 24.Because engaging clutch C4, so moment of torsion is delivered to countershaft 54 by pitch wheel 62,82 from input block 17, by pitch wheel 86,90 are delivered to sun gear parts 22.Deduct the moment of torsion being supplied to sun gear parts 22 from the moment of torsion being supplied to ring gear component 24, and moment of torsion is delivered to gear carrier parts 26 and output block 19 by planetary gear set 20.Gearshift from the 8th speed ratio to the 9th speed ratio singly changes gearshift.
In order to set up the tenth speed ratio, engaging clutch C3 and C5.Because engaging clutch C5, so moment of torsion is delivered to countershaft 52 by pitch wheel 60,70 from input block 17, by pitch wheel 74,92 are delivered to ring gear component 24.Because engaging clutch C3, so moment of torsion is delivered to countershaft 54 by pitch wheel 60,80 from input block 17, by pitch wheel 86,90 are delivered to sun gear parts 22.Deduct the moment of torsion being supplied to sun gear parts 22 from the moment of torsion being supplied to ring gear component 24, and moment of torsion is delivered to gear carrier parts 26 and output block 19 by planetary gear set 20.Gearshift from the 9th speed ratio to the tenth speed ratio singly changes gearshift.
Although ten forward speed ratios can be used, can controlled variator 14, to make only with the available forward speed ratio operation of part.Such as, speed changer 14 can be configured to as 6 speed transmissions, 7 speed transmissions, 8 speed transmissions or 9 speed transmissions.Speed changer 14 can with the forward speed ratio operation being less than 6.
In a kind of mode that speed changer 14 operates as 8 speed transmissions, control to guide hydraulic fluid to flow to the algorithm stored in the controller of the valve of torque-transmitting mechanisms and only can set up reversing speed ratio and the 3rd, the 4th, the 5th, the 6th, the 7th, the 8th, the 9th and the tenth forward speed ratio as above is established as the first, second, third, fourth, the 5th, the 6th, the 7th and the 8th forward speed ratio.In this 8 speed transmissions, between the 4th and the 5th forward speed ratio, only there is two conversion gearshift (that is, from the six to the seven forward speed ratio of Fig. 2), and residue gearshift singly changes gearshift.Change compared with gearshift with single, two conversion is shifted gears more difficult timing, thus torque ripple not obvious and maintain smooth gear shift and experience.
In order to be operated as 9 speed transmissions by speed changer 14, first or second forward speed ratio of all forward speed ratios and Fig. 2 that 8 speed transmissions are described will be used.9 speed transmissions have two two conversion gearshifts and residue gearshift singly changes gearshift.
Other gear numbers of teeth and corresponding velocity ratio can be selected, to realize applying favourable speed ratio and ratio step-length to certain variator.Such as, speed changer 14 can as 8 speed transmission operations, there are 8 the continuous forward speed ratios corresponding to the second of Fig. 2, the 8th, the tenth, first, the 9th, the 4th, the 6th and the 5th forward speed ratio, there is velocity ratio below: gear 80 is-1.247 to the velocity ratio of gear 60; Gear 82 is-0.702 to the velocity ratio of gear 62; Gear 70 is-0.551 to the velocity ratio of gear 60; Gear 72 is-0.174 to the velocity ratio of gear 62; Gear 90 is-1.775 to the velocity ratio of gear 86; Gear 92 is-3.508 to the velocity ratio of gear 74; Suppose that gear carrier parts 26 stop (only in order to calculate object), gear 24 is-1.164 to the velocity ratio of gear 22.As set forth in Fig. 2, reversing ratio can be set up, or different reversing ratio can be set up.
Use these velocity ratios, realize the velocity ratio between input block 17 below and output block 19: velocity ratio 4.789 in the first forward speed ratio; Velocity ratio 3.592 in the second forward speed ratio; Velocity ratio 2.695 in 3rd forward speed ratio; Velocity ratio 2.053 in 4th forward speed ratio; Velocity ratio 1.540 in 5th forward speed ratio; Velocity ratio 1.138 in 6th forward speed ratio; Velocity ratio 0.919 in 7th forward speed ratio; Velocity ratio 0.800 in 8th forward speed ratio.Corresponding ratio step-length is: from the first forward speed ratio to the ratio step-length of the second forward speed ratio be 1.333; Ratio step-length from the second forward speed ratio to the 3rd forward speed ratio is 1.333; Ratio step-length from the 3rd forward speed ratio to the 4th forward speed ratio is 1.313; Ratio step-length from the 4th forward speed ratio to the 5th forward speed ratio is 1.333; Ratio step-length from the 5th forward speed ratio to the 6th forward speed ratio is 1.353; Ratio step-length from the 6th forward speed ratio to the 7th forward speed ratio is 1.238; Ratio step-length from the 7th forward speed ratio to the 8th forward speed ratio is 1.149.The those of ordinary skill in speed changer field will know the number of teeth how selecting to expect.
Power system 10 can with hybrid motor vehicle common components, and this combination can operate under " charge consumption pattern ".For the purposes of the present invention, " charge consumption pattern " is such pattern: mainly through motor/generator to Motor Vehicle energy supply, thus when Motor Vehicle arrives its object exhaustion of the accumulators or close to exhausting.In other words, during charge consumption pattern, motor 12 is only for guaranteeing that storage battery before reaching its destination not exhausting, necessary degree operates.Traditional hybrid motor vehicle operates under " charge consumption pattern ", and wherein, if charge in batteries level drops under predeterminated level (such as, 25%), motor runs to charge a battery automatically.Therefore, by operating under charge consumption pattern, hybrid motor vehicle can be saved and be consumed in conventional hybrid Motor Vehicle for part or all of the fuel of maintenance 25% charge in batteries level.Should be appreciated that, if charged a battery by storage battery is inserted power supply after arrival destination, then preferably under charge consumption pattern, operate hybrid motor vehicle power system.
Realize most preferred embodiment of the present invention although described in detail, person of skill in the art will appreciate that, realize various replacement design and implementation example of the present invention and fall in the scope of claims.
Claims (14)
1. a multi-speed transmission, comprising:
Input block;
Output block;
Fixed component;
Intermediate member;
Simple planetary group;
Wherein, input block, output block, intermediate member and simple planetary group are arranged coaxially to each other, to limit the first spin axis;
First countershaft and the second countershaft limit the second spin axis and the 3rd spin axis respectively;
The torque-transmitting mechanisms that seven energy selectivity engage, wherein, seven torque-transmitting mechanisms comprise two breaks and five rotary clutchs;
Five groups of pitch wheels, part group is arranged to and moment of torsion is delivered to countershaft from input block, and other groups are arranged to of to be delivered to from countershaft by moment of torsion intermediate member and simple planetary group; Often organize pitch wheel and other are organized pitch wheel axially spaced-apart and arrange; First group wherein in five groups of pitch wheels and each group of second group of pitch wheel all comprise and are connected to input block thus the common respective gears rotated, around the rotatable respective gears of the first countershaft with around the rotatable respective gears of the second countershaft; The 3rd group of pitch wheel in five groups of pitch wheels comprises: the first gear, and it is connected to input block thus jointly rotates; Second gear, it is rotatable around the second countershaft; And the 3rd gear, it engages with the first gear and the second gear; The 4th group of pitch wheel in five groups of pitch wheels comprises: the first gear, and it is connected to the second countershaft thus jointly rotates; With the second gear, itself and the first gears meshing and be connected to intermediate member thus jointly rotate; The 5th group of pitch wheel in five groups of pitch wheels comprises: the first gear, and it is connected to the first countershaft thus jointly rotates; With the second gear, itself and the first gears meshing and be connected to the parts of simple planetary group thus jointly rotate;
Wherein, each in seven torque-transmitting mechanisms can optionally engage, the different respective gears in described five groups of pitch wheels to be connected to corresponding or the fixed component in countershaft; Wherein, seven torque-transmitting mechanisms can engage in various combination mode, to set up nearly ten forward speed ratios and a reversing speed ratio between input block and output block.
2. multi-speed transmission as claimed in claim 1, wherein, simple planetary group has: first component, and it continues to be connected to intermediate member thus jointly rotates; Second component, it continues to be connected to output block thus jointly rotates; 3rd parts, it continues to be connected in the gear being arranged to and being delivered to from countershaft by moment of torsion in a group of described five groups of pitch wheels of simple planetary group thus jointly rotates.
3. multi-speed transmission as claimed in claim 1, wherein, the first and second torque-transmitting mechanisms energy selectivity in seven torque-transmitting mechanisms engage, respectively the first countershaft and the second countershaft are fixed to fixed component.
4. multi-speed transmission as claimed in claim 1, wherein, two in seven torque-transmitting mechanisms can selectivity engage, so that corresponding in the rotatable gear of the first countershaft is connected to the first countershaft thus jointly rotates respectively; Wherein, two other in seven torque-transmitting mechanisms can selectivity engage, so that corresponding in the rotatable gear of the second countershaft is connected to the second countershaft thus jointly rotates respectively.
5. multi-speed transmission as claimed in claim 1, wherein, an energy selectivity in seven torque-transmitting mechanisms engages, the second gear is connected to the second countershaft thus jointly rotates.
6. multi-speed transmission according to claim 1, wherein, in seven torque-transmitting mechanisms is synchronizer at least partially.
7. multi-speed transmission according to claim 6, wherein, four in seven torque-transmitting mechanisms are coaxial and be synchronizer about the 3rd spin axis, wherein, in seven torque-transmitting mechanisms other three coaxial and be rotate or fixed friction formula clutch about the second spin axis.
8. multi-speed transmission according to claim 7, wherein, seven torque-transmitting mechanisms can engage in combination of two mode, thus enter in each of front in speed ratio to engage about at least one of coaxial described four torque-transmitting mechanisms of the 3rd spin axis.
9. multi-speed transmission according to claim 1, wherein, seven torque-transmitting mechanisms can engage in different combination of two mode, to set up at least eight forward speed ratios and a reversing speed ratio between input block and output block, wherein, between the forward speed ratio of order, only a gearshift is two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift.
10. multi-speed transmission according to claim 1, wherein, seven torque-transmitting mechanisms can engage in different combination of two mode, to set up ten forward speed ratios and a reversing speed ratio between input block and output block, wherein, between the forward speed ratio of order, only two gearshifts are two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift.
11. multi-speed transmissions according to claim 1, wherein, seven torque-transmitting mechanisms energy selectivity engage to set up eight forward speed ratios, and wherein, the step-length ratio between the forward speed ratio of the order at least partially in forward speed ratio is identical.
12. 1 kinds of multi-speed transmissions, comprising:
Input block;
Output block;
Fixed component;
Intermediate member;
Simple planetary group, the one group of small gear that there are sun gear parts, ring gear component, gear carrier parts and engage by gear carrier parts rotary support and with sun gear parts and ring gear component; Wherein, input block, output block, intermediate member and simple planetary group are arranged coaxially to each other, to limit the first spin axis;
First countershaft and the second countershaft limit the second spin axis and the 3rd spin axis respectively;
The torque-transmitting mechanisms that seven energy selectivity engage, comprises two breaks and five rotary clutchs;
Five groups of pitch wheels, part group is arranged to and moment of torsion is delivered to countershaft from input block, and other groups are arranged to moment of torsion from corresponding of being delivered in intermediate member and simple planetary group countershaft; Often organize pitch wheel and other are organized pitch wheel axially spaced-apart and arrange;
Wherein, sun gear parts are connected to intermediate member thus jointly rotate, and gear carrier parts are connected to output block thus jointly rotate, and ring gear component is connected in the parts of pitch wheel group thus jointly rotates;
Wherein, each in seven torque-transmitting mechanisms can optionally engage, the different respective gears in described five groups of pitch wheels to be connected to corresponding or the fixed component in countershaft; Wherein, seven torque-transmitting mechanisms can engage in different combination of two modes, to set up nearly ten forward speed ratios and a reversing speed ratio between input block and output block.
13. multi-speed transmissions according to claim 12, wherein, seven torque-transmitting mechanisms can optionally engage, to set up eight forward speed ratios, wherein, between the forward speed ratio of order, only a gearshift is two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift; Wherein, seven torque-transmitting mechanisms energy selectivity engage, and to set up ten forward speed ratios, wherein, between the forward speed ratio of order, only two gearshifts are two conversion gearshift, and the residue gearshift between the forward speed ratio of order is for singly to change gearshift.
14. multi-speed transmissions according to claim 12, wherein, seven torque-transmitting mechanisms energy selectivity engage to set up eight forward speed ratios, and wherein, the step-length ratio between the forward speed ratio of the order at least partially in forward speed ratio is identical.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| RU2010112596/11A RU2010112596A (en) | 2010-03-31 | 2010-03-31 | MULTI-STAGE TRANSMISSION (OPTIONS) |
| RU2010112596 | 2010-03-31 | ||
| US12/954,942 US8360919B2 (en) | 2010-03-31 | 2010-11-29 | Multi-speed transmission |
| US12/954942 | 2010-11-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102207172A CN102207172A (en) | 2011-10-05 |
| CN102207172B true CN102207172B (en) | 2015-09-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110079952.3A Active CN102207172B (en) | 2010-03-31 | 2011-03-31 | Multi-speed transmission |
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| Country | Link |
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| CN (1) | CN102207172B (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101311579A (en) * | 2007-05-21 | 2008-11-26 | 通用汽车公司 | Nine or ten speed split clutch countershaft automatic transmission |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7666112B2 (en) * | 2007-01-26 | 2010-02-23 | Gm Global Technology Operations, Inc. | Electro-hydraulic control system with multiplexed trim valves for a transmission |
| DE102007043695A1 (en) * | 2007-09-15 | 2009-03-19 | Zf Friedrichshafen Ag | Method for switching control of an automated group transmission |
| DE102007043694A1 (en) * | 2007-09-15 | 2009-03-19 | Zf Friedrichshafen Ag | Method for switching control of an automated group transmission |
| US8075437B2 (en) * | 2008-07-30 | 2011-12-13 | Allison Transmission, Inc. | Gear assembly for multi-speed countershaft transmission |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101311579A (en) * | 2007-05-21 | 2008-11-26 | 通用汽车公司 | Nine or ten speed split clutch countershaft automatic transmission |
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