CN102588525A - Gear box of combustion engine and control method thereof - Google Patents
Gear box of combustion engine and control method thereof Download PDFInfo
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- CN102588525A CN102588525A CN201210022140XA CN201210022140A CN102588525A CN 102588525 A CN102588525 A CN 102588525A CN 201210022140X A CN201210022140X A CN 201210022140XA CN 201210022140 A CN201210022140 A CN 201210022140A CN 102588525 A CN102588525 A CN 102588525A
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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
Abstract
The gear box has input shafts (1,2) that are connected to clutch unit (K1,K2) with drive motor. An output shaft (3) is connected with power train for driving wheels of motor vehicle. The input shafts are connected with gear portions (II,IV,VIII,X). A parallel shaft (14) is drive-connected with primary gear (VI) which is connected to input shaft (1), and is drive-connected with transfer gears (T1,T2) which is connected to input shaft (2). The input shaft (2) is coupled or uncoupled with transfer gears of parallel shaft in lower/higher gear switching stages respectively.
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 can be connected to the power-transmitting unit that drives motor vehicle wheel, and 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.Every input shaft can optionally be connected to an output shaft through two pairs of gear pairs.Like this, be delivered to output shaft through first input shaft, perhaps be delivered to output shaft, depend on that which friction clutch is closed through second input shaft from the driving torque of drive motor.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, at least at a selected especially gear, the guiding of power path is from first input shaft, parallel axes, and second input shaft is to output shaft.Another kind of situation is, the guiding 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, realize shifting gears more easily sequence, and significantly do not increase the installing space of speed changer with more available gears.
According to the object of the invention, a kind of speed changer that is used for motor vehicle is provided, comprise
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 can be 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 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, In the configuration of said 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, arranges the gear of deriving at least, makes its second input shaft be coupled to parallel axes through at least one pair of driving gear pair.
In this 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 " directly " 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.
In a preferred embodiment provided by the invention, 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 being connected to the many of parallel axes to each input shaft, can be used to provide some additional gears gear pair.
In this case, two output shafts are connected to the same part of the power transmission of said motor vehicle.Said output shaft passes through the gear engagement of gear and differential speed gears respectively.
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.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 input shaft 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, through 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, and wherein, said idle pulley can be coupled to back shaft separately through having the public same coupling device of mobile sleeve pipe.
Preferably, first clutch and second clutch are configured to friction clutch.
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, two input shafts and parallel axes all are available for arriving a 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, and the trend that makes power path is via second clutch, 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 between the parallel axes and second output shaft, and second output shaft.So many between second input shaft and the parallel axes also can be used to provide some other gears to gear pair.(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 coupling device between the parallel axes and second output shaft, 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)
The realization approach of first reverse gear is, controls described speed changer, and 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, the gear pair between the parallel axes and first input shaft; Gear pair device between first input shaft and second output shaft, coupling device and second output shaft.(first reverse gear)
The realization approach of second reverse gear is, 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) from initial gear (driving), be used to control the clutch of follow-up gear closed continuously the time, and the clutch that is used to control initial gear is opened continuously through among two clutches another through one among two clutches.So, under the situation that does not cause tractive force to interrupt, from a gear " gradual transition " to next gear.
In addition, when two follow-up gears have to use same clutch to drive, take place 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.More accurate 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 continuously, with gear in the middle of changing to from initial gear; Gear drives through this another clutch in the middle of described, so, 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, in general is 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, and as the reduced representation of schematic representation, clutch K1, K2 just representes with a clutch element.Yet, in general, also can consider other clutch, as long as guarantee this clutch a slippage gearshift procedure is arranged.
In addition, first output shaft 3 is provided, itself and the parallel assembling of two input shafts 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, wherein, described two fixed gears 4 and 6 non-rotating being connected on first input shaft 1, 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 non-rotatingly are connected second input shaft 2 with 10, and described two idle pulleys 9 and 11 rotatable being 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 gear of the second coupling device B, idle pulley 9 or idle pulley 11 are coupled to second output shaft 3.In certain mobile position, two idle pulleys 9 are not connected with first output shaft 3 with 11.
In addition, in an illustrated embodiment, second output shaft 18 is provided, with parallel axes 14 coaxial assemblings.Yet in general, with regard to the enforcement of this patent, second output shaft 18 can omit.But, adopt after second output shaft 18, in same installing space, can realize gear more.In the present embodiment, second output shaft, 18 rotatable being assemblied on the parallel axes 14.Yet, also can adopt other fit, for example, parallel axes 14 also can adopt the hollow shaft form, around 18 assemblings of second output shaft.
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, this power path is extended to parallel axes 14 through driving gear pair T2.The trend of first power path via gear pair VI further to first input shaft 1, and therefrom through gear pair II to first output shaft 3, 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, and this output gear is engaged to an actuation gear (not shown) of 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 predetermined state, therefore can be under the situation that does not have tractive force to interrupt " gradual transition ".According to reducing identical degree, increase the torque of first clutch K1 with the torque of second clutch K2.
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.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 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, 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 realize the fourth speed position, when first clutch K1 opens, when second clutch K2 is closed, the trend of this power path be from second input shaft 2 through gear pair IV to first output shaft 3.In this embodiment, the second coupling device B replaces, 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 two gears all are first clutch K1 closures and second clutch K2 opens, 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, move the first coupling device A and make its idle pulley 5 that discharges gear pair II, move 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 ".Break away from second grade and get into third gear then.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 produce the torque peak, 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 was used to provide support.Therefore, the total amount of second clutch K2 torque reduction increases identical with the torque of first clutch K1.
Then, continue upwards gear shift, it again again " gradual transition " to fourth speed position state.
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 again, and arrives second output gear 21 of its connection; 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 trend of the 6th power path of the 6th gear is passed through gear pair VI to parallel axes 14 from first input shaft 1; And from arriving 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 the 4th gear pair IV; But; Wherein 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 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 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.Can be as common dual-clutch transmission, can be from a clutch gradual transition to another clutch.In addition; 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 trend of the power path of this gear is through the another one clutch.
Shown in Figure 4 is the shift sequence figure of different gears (shelves).Each shelves corresponding to cited show that which clutch K1 and K2 are driven.In addition, corresponding to each bar straight line of enumerating, show that which its power path passes through to gear pair.According to diagram, first grade (first gear) uses second clutch K2 to drive, and wherein, as stated, the trend of its power path is through described 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.Then, the gradual transition gearshift procedure takes place again from the third gear to the fourth speed.From five grades of fourth speed gear shift to the, have to through the 6th grade with the support pattern gear shift.In order to obtain favourable notch level, especially in than low-grade location, should avoid the too little gear of velocity ratio, wise way possibly be 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 (18)
1. be used for motor vehicle, can gear shift between many gears speed changer, 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); Said first output shaft is connected to the power-transmitting unit that drives motor vehicle wheel; And (II X) is connected to said first input shaft (1), through at least one pair of driving gear pair (IV 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 is connected to said first input shaft (1) according to driving mode through a pair of gear pair (VI), 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, In the configuration of said speed changer, if in velocity ratio two direct gears adjacent to each other, said second input shaft (2) is not through at least one pair of driving gear pair (T1; T2) be coupled to said parallel axes (14); Then between these two gears, arrange the gear of deriving at least, (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.
2. speed changer according to claim 1 is characterized in that, said parallel axes (14) is coupled to said second output shaft (18) through a coupling device (D), and said second output shaft is connected to the power-transmitting unit of said motor vehicle.
3. according to the speed changer of one of aforesaid right requirement, it 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.
4. 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.
5. 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.
6. according to the speed changer of one of aforesaid right requirement, it is characterized in that the gearing (R) with three gears (19,5,4) is provided, and by said gearing, said first input shaft (1) is connected to said second output shaft (18) according to driving mode.
7. 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.
8. 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)
9. method according to claim 8; 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)
10. according to Claim 8 or one of 9 described methods, 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)
11. according to Claim 8 to one of 10 described methods; 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)
12. to one of 11 described methods, it is characterized in that according to Claim 8, 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) between said parallel axes (14) and second output shaft (18) and second output shaft (18).(the 5th grade)
13. to one of 12 described methods, it is characterized in that according to Claim 8, control said speed changer; Make the trend of 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); Coupling device (D) between said parallel axes (14) and second output shaft (18), and second output shaft (18).(the 6th grade)
14. to one of 13 described methods, it is characterized in that according to Claim 8, control said speed changer; 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 said parallel axes (14) and first output shaft (1), the gearing (R) between first input shaft (1) and said second output shaft (18); Coupling device (D) between said parallel axes (14) and second output shaft (18), and second output shaft (18).(first reverse gear)
15. according to Claim 8 to one of 14 described methods; 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)
16. to one of 15 described methods, it is characterized in that, during according to Claim 8 from initial gear switch to follow-up gear; (K2 in the time of K1) continuously closed, controls the clutch (K1 of initial gear at the clutch of the follow-up gear of control; K2) opening continuously, wherein, is through two clutch (K1 at said initial gear; K2) driving among, and be that (K2, another among K1) drives continuously through two clutches at said follow-up gear.
17. to one of 16 described methods, it is characterized in that, during from initial gear switch to follow-up gear, wherein according to Claim 8; 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 from said initial gear switch to middle 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 clutch (K1, K2) continuous closure that said follow-up gear drives.
18. method according to claim 17 is characterized in that, said in the middle of gear just be used for time period 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 |
|---|---|---|---|
| DE102011000152A DE102011000152A1 (en) | 2011-01-14 | 2011-01-14 | Gear box of combustion engine for motor car, has input shaft that is coupled/uncoupled with transfer gears of parallel shaft in lower/higher gear switching stages respectively |
| DE102011000152.2 | 2011-01-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102588525A true CN102588525A (en) | 2012-07-18 |
| CN102588525B CN102588525B (en) | 2015-06-17 |
Family
ID=46477606
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210022140.XA Expired - Fee Related CN102588525B (en) | 2011-01-14 | 2012-01-13 | Gear box of combustion engine and control method thereof |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN102588525B (en) |
| DE (1) | DE102011000152A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108625265A (en) * | 2017-03-15 | 2018-10-09 | 维特根有限公司 | Ground side machining apparatus with the speed changer between drive motor and revolvable equipment |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012001948A1 (en) * | 2012-02-02 | 2013-08-08 | Daimler Ag | Double clutch |
| CN113685505B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685507B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685502B (en) * | 2020-05-18 | 2024-01-19 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| DE102020005103B4 (en) | 2020-08-20 | 2022-12-01 | Mercedes-Benz Group AG | Double clutch |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| US7340973B2 (en) * | 2003-01-14 | 2008-03-11 | Kyowa Metal Works Co., Ltd. | Twin-clutch transmission |
| US7752934B2 (en) * | 2007-02-20 | 2010-07-13 | Gm Global Technology Operations, Inc. | Multi speed transmission having a countershaft gearing arrangement |
| CN101865258A (en) * | 2009-04-14 | 2010-10-20 | 腓特烈斯港齿轮工厂股份公司 | Dual-clutch transmission |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100610107B1 (en) * | 2004-08-13 | 2006-08-09 | 현대자동차주식회사 | double clutch transmission |
-
2011
- 2011-01-14 DE DE102011000152A patent/DE102011000152A1/en not_active Withdrawn
-
2012
- 2012-01-13 CN CN201210022140.XA patent/CN102588525B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| US7340973B2 (en) * | 2003-01-14 | 2008-03-11 | Kyowa Metal Works Co., Ltd. | Twin-clutch transmission |
| US7752934B2 (en) * | 2007-02-20 | 2010-07-13 | Gm Global Technology Operations, Inc. | Multi speed transmission having a countershaft gearing arrangement |
| CN101865258A (en) * | 2009-04-14 | 2010-10-20 | 腓特烈斯港齿轮工厂股份公司 | Dual-clutch transmission |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108625265A (en) * | 2017-03-15 | 2018-10-09 | 维特根有限公司 | Ground side machining apparatus with the speed changer between drive motor and revolvable equipment |
| US10718431B2 (en) | 2017-03-15 | 2020-07-21 | Wirtgen Gmbh | Earth working machine having a shiftable transmission between a drive motor and a rotatable working apparatus |
| CN108625265B (en) * | 2017-03-15 | 2020-08-18 | 维特根有限公司 | Floor-processing machine with a transmission between a drive motor and a rotatable working device |
| US11346443B2 (en) | 2017-03-15 | 2022-05-31 | Wirtgen Gmbh | Earth working machine having a shiftable transmission between a drive motor and a rotatable working apparatus |
| US11859717B2 (en) | 2017-03-15 | 2024-01-02 | Wirtgen Gmbh | Earth working machine having a shiftable transmission between a drive motor and a rotatable working apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102588525B (en) | 2015-06-17 |
| DE102011000152A1 (en) | 2012-07-19 |
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