CN102588524A - Transmission for motor vehicle, and control method thereof - Google Patents
Transmission for motor vehicle, and control method thereof Download PDFInfo
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- CN102588524A CN102588524A CN2012100221397A CN201210022139A CN102588524A CN 102588524 A CN102588524 A CN 102588524A CN 2012100221397 A CN2012100221397 A CN 2012100221397A CN 201210022139 A CN201210022139 A CN 201210022139A CN 102588524 A CN102588524 A CN 102588524A
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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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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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
- F16H61/04—Smoothing ratio shift
- F16H61/0437—Smoothing ratio shift by using electrical signals
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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
- F16H61/68—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 specially adapted for stepped gearings
- F16H61/684—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 specially adapted for stepped gearings without interruption of drive
- F16H61/688—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 specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
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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
- F16H3/093—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 with two or more countershafts
- F16H2003/0931—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 with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
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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
- F16H3/093—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 with two or more countershafts
- F16H2003/0933—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 with two or more countershafts with coaxial countershafts
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0073—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eleven forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The transmission has two input shafts (1,2), which are drive connected with drive motor by two clutches (K1,K2). An output shaft (3) is connected with a drive train for driving wheels of motor vehicles. A parallel shaft (14) is drive connected with the input shaft by a gear pair. The parallel shaft is coupled with another output shaft (18) over a switching arrangement (D). An independent claim is also included for a method for controlling a transmission.
Description
Technical field
The present invention relates to a kind of speed changer that is used for motor vehicle, it comprises: first input shaft can be connected to drive motor through first clutch according to driving mode; Second input shaft can be connected to drive motor through second clutch according to driving mode; First output shaft; Be connected to the power-transmitting unit of driving machine motor vehicle; Described first output shaft can be connected to first input shaft through at least one pair of gear pair according to driving mode, is connected to second input shaft through at least one pair of gear pair, and parallel axes; Can be connected to first input shaft through a pair of gear pair according to driving mode, and can be connected to second input shaft through at least one pair of gear pair according to driving mode.
Background technique
DE 10015336A1 discloses the instance of such speed changer.According to document record, dual-clutch transmission comprises two input shafts, and they can be connected to drive motor through a friction clutch respectively.Every input shaft can optionally be connected to an output shaft through two pairs of gear pairs.Like this, the driving torque of drive motor is delivered to output shaft through first input shaft, perhaps is delivered to output shaft through second input shaft, depends on that which friction clutch is closed.Therefore, this speed changer can be realized four gears altogether.In order to increase the gear number, a parallel axes is provided, this parallel axes is connected with one of two input shafts with driving mode through a pair of gear pair with two fixed gears.In addition, parallel axes can optionally be connected to another root input shaft through two pairs of gear pairs.Therefore, in a gear of selecting especially and cutting, the trend of power path is from first input shaft at least, parallel axes, and second input shaft is to output shaft.Another kind of situation is, the trend of power path can be from second input shaft, parallel axes, and first input shaft is to output shaft.Therefore, can realize 12 gears in theory.
Summary of the invention
The objective of the invention is to realize more available gears, and the installing space of not obvious increase speed changer.
According to the object of the invention, a kind of speed changer that is used for motor vehicle is provided, it comprises:
First input shaft can be connected to drive motor through first clutch according to driving mode;
Second input shaft can be connected to drive motor through second clutch according to driving mode;
First output shaft is connected to the power-transmitting unit that drives motor vehicle wheel, and said first output shaft can be connected to first input shaft through at least one pair of gear pair according to driving mode, is connected to second input shaft through at least one pair of driving gear pair; And
Parallel axes can be connected to first input shaft through a pair of gear pair according to driving mode, and can be connected to second input shaft through at least one pair of driving gear pair according to driving mode;
Wherein, said parallel axes can be coupled to second output shaft through a coupling device, and said second output shaft can be connected to the power-transmitting unit of motor vehicle.
Therefore, be used for to be used to provide some additional gears to the gear pair that each input shaft is connected to parallel axes.
In the speed changer that provides of the present invention, two output shafts are connected to the same part of the power transmission of said motor vehicle.Said output shaft passes through the same gear engagement of gear and differential speed gears respectively.
In this case, the coaxial assembling of the preferably and said parallel axes of said second output shaft.
In a preferred embodiment provided by the invention, first input shaft can be according to driving mode, be connected to first output shaft through at least two pairs of gear pairs selectively.In the same way, preferably, second input shaft can be according to driving mode, be connected to first output shaft through at least two pairs of gear pairs selectively.
Described parallel axes can be connected to second live axle through at least two pairs of driving gear pairs selectively according to driving mode.
In order to realize reverse gear, the gearing with three gears can be provided, by said gearing, first input shaft can be connected to second output shaft according to driving mode.
All removable gear pairs; Comprise at least one pair of driving gear pair, comprise a fixed gear and an idle pulley respectively, wherein; Said idle pulley can be coupled to the mobile sleeve pipe that has axle separately through common coupling device, and said idle pulley is bearing on the said mobile sleeve pipe.
Preferably, first clutch and second clutch are configured to friction clutch.
In the configuration of described speed changer; If in velocity ratio two direct gears adjacent to each other; Second input shaft is not coupled to parallel axes through at least one pair of driving gear pair; Then between these two gears, arrange the gear of deriving at least, make its second input shaft be coupled to parallel axes through at least one pair of driving gear pair.
In the case, from mechanically feasible lowest gear, to mechanically feasible high tap position, all gears that in shift sequence, can realize all have been taken into account, and in the situation of the shift sequence that reality is carried out, keep indivedual gears and do not use.So, possibly have only two velocity ratio direct gears adjacent to each other being used usually really by actual.Yet, between these two direct gears, always arrange one to be the attainable in theory machinery gear of deriving at least.The definition here is only relevant with forward gears, and is irrelevant with reverse gear.
Another object of the present invention provides a kind of method that is used to control above-mentioned speed changer, wherein, controls said speed changer; The trend that makes its power path is via second clutch, second input shaft, at least one pair of driving gear pair between second input shaft and the parallel axes; Parallel axes, the gear pair between the parallel axes and first input shaft, first input shaft; At least one pair of gear pair between first input shaft and first output shaft, and first output shaft.(first and the 9th grade)
In addition, the trend of the power path that can provide is via first clutch, first input shaft, at least one pair of gear pair between first input shaft and first output shaft, and first output shaft.(second and the tenth grade)
In addition, input shaft and parallel axes all are available for arriving the power path of first output shaft, wherein; Control described speed changer, the trend that makes power path is via first clutch, first input shaft; Gear pair between first input shaft and the parallel axes, parallel axes, at least one pair of driving gear pair between the parallel axes and second input shaft; Second input shaft, at least one pair of gear pair between second input shaft and first output shaft, and first output shaft.(the 3rd and the 7th grade)
This is effective equally to the second clutch and second input shaft, wherein, controls described speed changer; The trend that makes power path is via second gear shift sleeve; Second input shaft, at least one pair of gear pair between second input shaft and first output shaft, and first output shaft.(the 4th and the 8th grade)
In addition, can control described speed changer, the trend that makes power path is via second clutch, second input shaft, at least one pair of driving gear pair between second input shaft and the parallel axes, parallel axes, coupling device and second output shaft.So the gear pair between second input shaft and the parallel axes also can be used to provide some other gears.(the 5th grade)
The trend of power path can also be via first clutch, first input shaft, the gear pair between first input shaft and the parallel axes, parallel axes, the 3rd coupling device and second output shaft.So the gear pair between first input shaft and the parallel axes is used to the gear that provides other.Usually, between first input shaft and parallel axes, not only a pair of gear pair can be provided, these gear pairs that wherein can be coupled selectively, making all has a pair of available gear pair for each gear.(the 6th grade)
First reverse gear can realize like this: control described speed changer; The trend that makes power path is via second clutch, second input shaft, at least one pair of driving gear pair between second input shaft and the parallel axes; Parallel axes; Gear pair between the parallel axes and first input shaft, the gearing between first input shaft and second output shaft, coupling device and second output shaft.(first reverse gear)
Second reverse gear can realize like this, controls described speed changer, and the trend that makes power path is via first clutch, first input shaft, the gearing between first input shaft and second output shaft, coupling device and second output shaft.(second reverse gear)
In order to realize two gear shift between the gear; Especially between two adjacent gears; Universal sequence as common dual-clutch transmission can be provided; The gearshift procedure that switches to higher or lower follow-up gear (driving through among two clutches another) from initial gear (driving through among two clutches), the clutch that is used to control follow-up gear is closed continuously, and the clutch that is used to control initial gear is opened continuously.So, under the situation that does not cause tractive force to interrupt, from a gear " gradual transition " to another gear.
In addition, when two follow-up gears have to use same clutch to drive, carry out one and switch to the more central gearshift lever of high tap position, described more high tap position uses another clutch.In the case, described central gearshift lever is just interim as " support gear shift " during the gearshift procedure, interrupts to prevent tractive force.In the case, for example, can use the next but one gear, perhaps other higher gear.A more special embodiment of this gearshift procedure can be provided, and when changing to next higher follow-up gear from initial gear when, wherein initial gear and follow-up gear all are to drive through same clutch; During in opening two clutches continuously one, another in two clutches is closed just continuously, with gear in the middle of changing to from initial gear; Gear drives through this another clutch in the middle of described; And during driving via described another clutch, follow-up gear begins incision, then; When described another clutch was opened continuously, the clutch that is used for follow-up gear driving was closed continuously.
Description of drawings
Following accompanying drawing is used to describe in detail embodiment preferred:
Fig. 1 is the principle schematic of speed changer of the present invention;
Fig. 2 is the distribution of torque from first gear to the second gear gearshift procedure;
Fig. 3 is the distribution of torque from second gear to the third gear gearshift procedure;
Fig. 4 is the gear sequence chart.
Embodiment
Fig. 1 illustrates first input shaft 1, and it can be connected to drive motor through first clutch K1 according to driving mode, is generally the internal-combustion engine of automobile.In addition, second input shaft 2 shown in the figure, it can also be connected to drive motor through second clutch K2 according to driving mode.These two clutch K1, K2 is a friction clutch, wherein, as the reduced representation of schematic representation, clutch K1, K2 only are expressed as a clutch element.Yet, in general, also can consider other clutch, this clutch will guarantee to have a slippage gearshift procedure.
In addition, first output shaft 3 is provided, itself and two parallel assemblings of input shaft 1 with 2.Through two couples of gear pair II and X, first input shaft 1 can be connected to first output shaft 3 according to driving mode.These two couples of gear pair II and X comprise 4,6 and idle pulleys 5,7 of a fixed gear respectively, and wherein, described two fixed gears 4 and 6 are connected on first input shaft 1 non-rotatingly, and described two idle pulleys 5 and 7 are around the 3 rotatable assemblings of first output shaft.Two idle pulleys 5 and 7 can optionally be connected to first output shaft 3 through coupling device A, that is, according to the mobile position of coupling device A, idle pulley 5 or idle pulley 7 are coupled to first output shaft 3.In general, coupling device A also provides a neutral position, and two idle pulleys 5 and 7 are not coupled with first output shaft 3 in this position.
Similarly, second input shaft 2 can be connected to first output shaft 3 through gear pair IV and gear pair VIII according to driving mode.These two couples of gear pair IV and VIII comprise 8,10 and idle pulleys 9,11 of a fixed gear respectively.Described two fixed gears 8 are connected second input shaft 2 with 10 non-rotatingly, and described two idle pulleys 9 and 11 rotatably are assemblied on first output shaft 3.Through the second coupling device B, two idle pulleys 9,11 optionally are connected to first output shaft 3, that is, according to the mobile position of the second coupling device B, idle pulley 9 or idle pulley 11 are according to the driving mode connection and be coupled to first output shaft 3.In certain mobile position, two idle pulleys 9 are not connected with first output shaft 3 with 11.
In addition, second output shaft 18 is provided, itself and parallel axes 14 coaxial assemblings.In the present embodiment, second output shaft, 18 rotatable being assemblied on the parallel axes 14.Yet, also can adopt different fit, for example, parallel axes 14 also can adopt the hollow shaft form, around 18 assemblings of second output shaft.
Through the 4th coupling device D,, they are rotated together parallel axes 14 is coupled to second output shaft 18.In the case, especially when the parallel axes and second output shaft 18 are not mutual coaxial assembling, also can consider to pass through gears.
Through the 4th coupling device D, second output shaft 18 also can be connected with gearing R according to driving mode.Described gearing R comprises idle pulley 5 and idle pulley 19, and idle pulley 5 rotations are assemblied on first output shaft 3, and idle pulley 19 is with idle pulley 5 engagements and around the 18 rotation assemblings of second output shaft.Through the 4th coupling device D, second output shaft 18 can non-rotatingly be coupled to idle pulley 19.All gear pairs have to be noted that this annexation is simplified in the expression of Fig. 1, so that can be presented on the plane.In fact, when when axial direction is seen, first input shaft 1 or coaxial second input shaft 2 that is assembled to first input shaft 1 with first output shaft 3 and second output shaft 18, are arranged as an imaginary triangle, so idle pulley 19 can mesh with idle pulley 5.
In this embodiment, use first power path to describe first gear, when second clutch K2 closure and first clutch K1 opened, the trend of this power path was to driving gear pair T2 from second input shaft 2.The 3rd coupling device C is coupled to the idle pulley 17 of driving gear pair T2 to parallel axes 14, and therefore, the trend of this power path is to parallel axes 14 through driving gear pair T2.The trend of first power path is passed through gear pair VI further to first input shaft 1, and passes through gear pair II thus to first output shaft 3, and wherein, the first coupling device A is idle pulley 5 non-rotating first output shafts 3 that are coupled to.First output shaft 3 comprises first output gear 20, the actuation gear engagement of this output gear and differential speed gears.
Second gear uses second power path to realize; When first clutch K1 is closed; The trend of this power path is to pass through gear pair II to first output shaft 3 from first input shaft 1, and wherein, the first coupling device A is coupled to and first output shaft, the 3 non-rotating idle pulleys that are connected 5.
Gearshift procedure, take place from second clutch K2 " gradual transition " to first clutch K1, as common dual-clutch transmission that kind from first gear to second gear.That is, when second clutch K2 opened continuously, first clutch K1 was closed continuously, therefore, in gearshift procedure, can not produce tractive force and interrupt.Two groups of clutch K1, the distribution of torque of K2 between transfer period is as shown in Figure 2.When first gear was driven, second gear was in and pre-selects, therefore can be under the situation that does not have tractive force to interrupt " gradual transition ".Degree according to the torque of second clutch K2 reduces increases the torque of first clutch K1.
In third gear, when first clutch K1 closure, when second clutch K2 opens, the trend of the 3rd power path is passed through gear pair VI to parallel axes 14 via first input shaft 1.The 3rd coupling device C is coupled to the idle pulley 16 of driving gear pair T1 to parallel axes 14, and like this, the 3rd power path further is extended to second input shaft 2.The 3rd power path further is extended to first output shaft 3 through gear pair IV from this place, and wherein, the second coupling device B is coupled to first output shaft 3 to the idle pulley 11 of gear pair IV.
Use the 4th power path to describe the fourth speed position, when first clutch K1 opens and second clutch K2 when closed, the trend of this power path be from second input shaft 2 through gear pair IV to first output shaft 3.In the case, the second coupling device B switches, and makes idle pulley 11 non-rotating first output shafts 3 that are coupled to of gear pair IV.
The gearshift procedure from second gear to third gear, because these two gears all are that second clutch K2 opens when first clutch K1 is closed, therefore, in gearshift procedure, first clutch K1 has a bit of time to have to open usually always.This will cause tractive force to interrupt.For preventing this situation; In gearshift procedure, switch the first coupling device A and make it discharge the idle pulley 5 of gear pair II, switch the 3rd coupling device C and make its idle pulley that is coupled to driving gear pair T1 16; Utilize the fourth speed position to support operation, interrupt to prevent tractive force.
In the case, when through second gear and second power path controlling and driving, initial, first clutch K1 opens continuously, and second clutch K2 is closed continuously.Therefore, power path is to the 4th power path direction " gradual transition ".Then, second grade is cancelled and selects and third gear is selected.Then, first clutch K1 is closed continuously again, and second clutch K2 opens continuously, and therefore, it is to the 3rd power path " gradual transition " from the 4th power path.In the case, the 4th power path only uses when gearshift procedure continues.Two groups of clutch K1, the distribution of torque of K2 between transfer period is as shown in Figure 3.In the case, can find out significantly, during gearshift procedure from second gear to third gear; Utilized the fourth speed position, wherein, because there is very high kinetic energy to be stored in the driving mechanism; Even the torque peak appears, therefore can compensate the low torque of fourth speed.Degree according to first clutch K1 torque reduces increases the torque of second clutch K2.And when third gear was selected, the fourth speed position provided support.Therefore, the degree of the torque of second clutch K2 reduction increases identical with the torque of first clutch K1.
Then, continue upwards gear shift, it can " gradual transition " arrive the fourth speed position again.
At the 5th gear; When first clutch K1 opens, when second clutch K2 is closed; The trend of the 5th power path is passed through driving gear pair T2 to parallel axes 14 via second input shaft 2, and wherein, the 3rd coupling device C is coupled to parallel axes 14 to the idle pulley 17 of driving gear pair T2.The 4th coupling device D is coupled to parallel axes 14 to second output shaft 18; Therefore; The 5th power path is extended to second output shaft 18 and connected second output gear 21 again, and wherein, second output gear 21 meshes (not shown) with the actuation gear of differential speed gears.
When first clutch K1 closure, when second clutch K2 opens; The 6th power path of the 6th gear extends to parallel axes 14 from first input shaft 1 through gear pair VI; And from extending to second output shaft 18 through the 4th coupling device D here, described the 4th coupling device D is coupled to second output shaft 18 to parallel axes 14.
The 7th power path of the 7th gear is corresponding to the 3rd power path of third gear; But; Here second input shaft 2 is not through gear pair IV but is connected to first output shaft 3 through gear pair VIII; Wherein, the second coupling device B is coupled to first output shaft 3 to the idle pulley 9 of gear pair VIII.
The 8th power path of the 8th gear is corresponding to the 4th power path of fourth speed position; But; Wherein second input shaft 2 is not through gear pair IV but is connected to first output shaft 3 through gear pair VIII, and wherein, the second coupling device B is coupled to first output shaft 3 to the idle pulley 9 of gear pair VIII.
The 9th power path of the 9th gear is corresponding to first power path of first gear; But; Here first input shaft 1 is not through gear pair II but is connected to first output shaft 3 through gear pair X, and wherein, the first coupling device A is coupled to first output shaft 3 to the idle pulley 7 of gear pair X.
The tenth power path of the tenth gear is corresponding to second power path of second gear; But; Here first input shaft 1 is not through gear pair II but is connected to first output shaft 3 through gear pair X, and wherein, the first coupling device A is coupled to first output shaft 3 to the idle pulley 7 of gear pair X.
The 11 power path of the 11 gear is corresponding to the 9th power path of the 9th gear; But; Here second input shaft 2 is not through driving gear pair T2 but is connected to parallel axes 14 through driving gear pair T1; Wherein, the 3rd coupling device C is coupled to parallel axes 14 to the idle pulley 16 of driving gear pair T1.
Therefore, the advantage of the above-mentioned embodiment of speed changer of the present invention also comprises and can realize two kinds of different gearshift procedures.On the one hand, as common dual-clutch transmission, can be from a clutch gradual transition to another clutch.On the other hand; When two adjacent gears are realized by same clutch; Between two gears, can produce tractive force and interrupt, in the case, can prevent that tractive force from interrupting through the mode of " gear shift support "; Described gear shift support provides support with a gear during gearshift procedure exactly, and the power path of this gear is through the continuity of another one clutch.
Shown in Figure 4 is the gearshift procedure figure of different gears (shelves).Corresponding to illustrated each shelves, which clutch K1 and K2 are driven.Corresponding to illustrated each bar straight line, which its power path passes through to gear pair.According to diagram, second clutch K2 is used to first grade (first gear), and wherein, as stated, the trend of its power path is through driving gear pair T2 and gear pair VI and II.When gear shift to the second grade, directly gradual transition is to first clutch K1.The gearshift procedure from second grade to third gear, these two gears use first clutch K1 to drive respectively, and this process is passed through the fourth speed support, thereby through second clutch K2.Fourth speed is just interim to be used.After this, from third gear to fourth speed generation gradual transition gearshift procedure.Must be from fourth speed through the 6th grade with five grades of support pattern gear shift to the.In order to obtain favourable velocity ratio, especially in than low-grade location, should avoid the too little gear of velocity ratio, perhaps wise way is to skip the gear of the trend of indivedual gears, especially those power paths through parallel axes.In the present embodiment, third gear can be omitted, and representes with the dotted line between third and fourth grade among the figure.
Can be from the 5th grade with six grades of gradual transition mode gear shift to the.Change to the 7th grade from the 6th grade through the 8th grade with support pattern.Change to the 8th grade with the gradual transition mode again from the 7th grade.Change to the 9th grade from the 8th grade through the tenth grade with support pattern, change to the tenth grade with the gradual transition mode again from these shelves.From the tenth grade also is to change to the 11 grade with the gradual transition mode.
Label list:
1-first input shaft, 2-second input shaft, 3-first output shaft, 4-fixed gear, 5-idle pulley, 6-fixed gear; The 7-idle pulley, 8-fixed gear, 9-idle pulley, 10-fixed gear, 11-idle pulley; The 12-fixed gear, 13-fixed gear, 14-parallel axes, 15-fixed gear, 16-idle pulley; The 17-idle pulley, 18-second output shaft, 19-idle pulley, 20-first output gear, 21-second output gear; A-first coupling device, B-second coupling device, C-the 3rd coupling device, D-the 4th coupling device; The II-gear pair, IV-gear pair, VI-gear pair, VIII-gear pair, X-gear pair; The R-gearing, T1-driving gear pair, T2-driving gear pair, K1-first clutch, K2-second clutch.
Claims (19)
1. be used for the speed changer of motor vehicle, comprise
First input shaft (1), said first input shaft is connected to drive motor according to driving mode through first clutch (K1);
Second input shaft (2), said second input shaft is connected to drive motor according to driving mode through second clutch (K2);
First output shaft (3); Be connected to the power-transmitting unit that drives motor vehicle wheel; (II X) is connected to said first input shaft (1), through at least one pair of gear pair (IV to said first output shaft (3) through at least one pair of gear pair according to driving mode; VIII) be connected to said second input shaft (2), and
Parallel axes (14), said parallel axes can be connected to said first input shaft (1) through a pair of gear pair (VI) according to driving mode, and (T1 T2) is connected to said second input shaft (2) through at least one pair of driving gear pair according to driving mode;
Wherein, said parallel axes (14), to second output shaft (18), said second output shaft (18) can be connected to the power-transmitting unit of motor vehicle through coupling device coupling (D).
2. speed changer according to claim 1 is characterized in that, (II X) is connected to said first output shaft (3) to said first input shaft (1) through at least two pairs of gear pairs selectively according to driving mode.
3. according to the speed changer of one of aforesaid right requirement, it is characterized in that (IV VIII) is connected to said first output shaft (3) to said second input shaft (2) through at least two pairs of gear pairs selectively according to driving mode.
4. according to the speed changer of one of aforesaid right requirement, it is characterized in that (T1 T2) is connected to said second input shaft (2) to said parallel axes (14) through at least two pairs of driving gear pairs selectively according to driving mode.
5. according to the speed changer of one of aforesaid right requirement, it is characterized in that the gearing (R) with three gears (4,5,19) is provided, and through said gearing, said first input shaft (1) is connected to said second output shaft (18) according to driving mode.
6. according to the speed changer of one of aforesaid right requirement, it is characterized in that said first clutch (K1) and said second clutch (K2) are friction clutches.
7. according to the speed changer of one of aforesaid right requirement, it is characterized in that said second output shaft (18) and the coaxial assembling of said parallel axes (14).
8. according to the speed changer of one of aforesaid right requirement, it is characterized in that, in the configuration of said speed changer; If in velocity ratio two direct gears adjacent to each other; (T1 T2) is not coupled to parallel axes (14) to said second input shaft (2), then between these two gears, arranges the gear of deriving at least through at least one pair of driving gear pair; (T1 T2) is coupled to said parallel axes (14) to wherein said second input shaft (2) through at least one pair of driving gear pair.
9. be used to control method, it is characterized in that, control said speed changer according to the speed changer of one of aforesaid right requirement; Make the trend of power path via second clutch (K2), second input shaft (2), at least one pair of the driving gear pair (T1 between said second input shaft (2) and the parallel axes (14); T2), parallel axes (14), the gear pair (VI) between the said parallel axes and first input shaft; First input shaft (1); At least one pair of gear pair between said first input shaft (1) and first output shaft (3) (II, X), and first output shaft (3).(first and the 9th grade)
10. method according to claim 9; It is characterized in that, control said speed changer, make the trend of power path via first clutch (K1); First input shaft (1); At least one pair of gear pair between said first input shaft (1) and first output shaft (3) (II, X), and first output shaft (3).(second and the tenth grade)
11. according to one of claim 9 or 10 described method, it is characterized in that, control said speed changer; Make power path via first clutch (K1), first input shaft (1), the gear pair (VI) between said first input shaft (1) and the parallel axes (14); Parallel axes (14), and at least one pair of driving gear pair between said parallel axes (14) and second input shaft (2) (T1, T2); Second input shaft (2); At least one pair of gear pair between said second input shaft (2) and first output shaft (3) (IV, VIII), and first output shaft (3).(the 3rd and the 7th grade)
12. according to one of claim 9 to 11 described method; It is characterized in that, control said speed changer, make the trend of power path via second clutch (K2); Second input shaft (2); At least one pair of gear pair between said second input shaft (2) and first output shaft (3) (IV, VIII), and first output shaft (3).(the 4th and the 8th grade)
13. according to one of claim 9 to 12 described method, it is characterized in that, control said speed changer; Make the trend of power path via second clutch (K2); Second input shaft (2), and at least one pair of driving gear pair between said second input shaft (2) and the parallel axes (14) (T1, T2); Parallel axes (14), coupling device (D) and second output shaft (18).(the 5th grade)
14. according to one of claim 9 to 13 described method; It is characterized in that, control said speed changer, make the trend of power path via first clutch (K1); First input shaft (1); Gear pair (VI) between said first input shaft (1) and the parallel axes (14), parallel axes (14), coupling device (D) and second output shaft (18).(the 6th grade)
15. according to one of claim 9 to 14 described method, it is characterized in that, control said speed changer; Make the trend of power path via second clutch (K2); Second input shaft (2), and at least one pair of driving gear pair between said second input shaft (2) and the parallel axes (14) (T1, T2); Parallel axes (14); Gear pair (VI) between said parallel axes (14) and first input shaft (1), the gearing (R) between first input shaft (1) and second output shaft (18), coupling device (D) and second output shaft (18).(first reverse gear)
16. according to one of claim 9 to 15 described method; It is characterized in that, control said speed changer, make the trend of power path via first clutch (K1); First input shaft (1); Gearing (R) between said first input shaft (1) and second output shaft (18), coupling device (D), and second output shaft (18).(second reverse gear)
17., it is characterized in that, during from initial gear switch to follow-up gear according to one of claim 9 to 16 described method; Be used to control said follow-up gear clutch (K2, K1) closed continuously, and be used to control the clutch (K1 of said initial gear; K2) opening continuously, wherein, is through two clutch (K1 at said initial gear; K2) driving among, and be through two clutches (K2, another driving among K1) at said follow-up gear.
18., it is characterized in that, during from initial gear switch to follow-up gear, wherein according to one of claim 9 to 17 described method; In said initial gear and said follow-up gear, all pass through same clutch (K1, K2) control is at two clutches (when K1, in K2) one open continuously; Two clutches (K2, another in K1) is closed continuously, with gear in the middle of changing to from said initial gear; Gear is that (K2 K1) drives, and via said another clutch (K2 through said another clutch in the middle of wherein said; K1) during the driving, said follow-up gear begins incision, then; When said another clutch is opened continuously, be used for the clutch that said follow-up gear drives (K1, K2) closed continuously.
19. method according to claim 18 is characterized in that, said in the middle of gear just be used for a period of time of replacing at gear from said initial gear switch to said follow-up gear.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011000151.4A DE102011000151B4 (en) | 2011-01-14 | 2011-01-14 | Transmission for a motor vehicle and method for controlling such a transmission |
| DE102011000151.4 | 2011-01-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102588524A true CN102588524A (en) | 2012-07-18 |
| CN102588524B CN102588524B (en) | 2015-04-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210022139.7A Active CN102588524B (en) | 2011-01-14 | 2012-01-13 | Transmission for motor vehicle, and control method thereof |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN102588524B (en) |
| DE (1) | DE102011000151B4 (en) |
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| CN104251304A (en) * | 2013-06-26 | 2014-12-31 | 腓特烈斯港齿轮工厂股份公司 | Method for operating a double clutch transmission |
| CN107225958A (en) * | 2017-05-22 | 2017-10-03 | 安徽纽恩卡自控科技有限公司 | One kind nine keeps off mixed power automobile driving system |
| CN107917167A (en) * | 2016-10-09 | 2018-04-17 | 昆山德拉特兰传动科技有限公司 | Eight fast double-clutch automatic gearboxes |
| CN109780143A (en) * | 2017-11-14 | 2019-05-21 | 吉利汽车研究院（宁波）有限公司 | A kind of automobile front drive Duo Dang continuous change mechanism |
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| DE102012001948A1 (en) | 2012-02-02 | 2013-08-08 | Daimler Ag | Double clutch |
| DE102013010723B4 (en) | 2013-06-27 | 2022-09-15 | Mercedes-Benz Group AG | Double clutch |
| DE102013019120A1 (en) | 2013-11-15 | 2015-05-21 | Daimler Ag | Double clutch |
| CN106321747B (en) * | 2015-07-10 | 2019-02-19 | 长城汽车股份有限公司 | Speed changer and power drive system and vehicle with it |
| DE102015010252A1 (en) * | 2015-08-06 | 2016-03-03 | Daimler Ag | Double clutch |
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| JP2004263708A (en) * | 2003-01-14 | 2004-09-24 | Kyowa Metal Work Co Ltd | Twin clutch type transmission |
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| DE10015336A1 (en) * | 2000-03-28 | 2001-10-04 | Volkswagen Ag | Dual clutch gearbox has elements arranged so that for certain engaged gear drive train consists of first drive shaft, parallel shaft, second input shaft and output shaft |
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| CN107917167A (en) * | 2016-10-09 | 2018-04-17 | 昆山德拉特兰传动科技有限公司 | Eight fast double-clutch automatic gearboxes |
| CN107225958A (en) * | 2017-05-22 | 2017-10-03 | 安徽纽恩卡自控科技有限公司 | One kind nine keeps off mixed power automobile driving system |
| CN107225958B (en) * | 2017-05-22 | 2019-05-24 | 安徽纽恩卡自控科技有限公司 | One kind nine keeps off mixed power automobile driving system |
| CN109780143A (en) * | 2017-11-14 | 2019-05-21 | 吉利汽车研究院（宁波）有限公司 | A kind of automobile front drive Duo Dang continuous change mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102011000151B4 (en) | 2021-02-04 |
| DE102011000151A1 (en) | 2012-07-19 |
| CN102588524B (en) | 2015-04-15 |
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