WO2006049096A1 - 変速装置 - Google Patents
変速装置 Download PDFInfo
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- WO2006049096A1 WO2006049096A1 PCT/JP2005/019884 JP2005019884W WO2006049096A1 WO 2006049096 A1 WO2006049096 A1 WO 2006049096A1 JP 2005019884 W JP2005019884 W JP 2005019884W WO 2006049096 A1 WO2006049096 A1 WO 2006049096A1
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- gear
- shaft
- input shaft
- transmission
- speed
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
- 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
- F16H2003/0803—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with countershafts coaxial with input or 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
-
- 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
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
- 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
- F16H3/091—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 including a single countershaft
- F16H3/0915—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 including a single countershaft with coaxial input and output shafts
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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
- F16H3/097—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 the input and output shafts being aligned on the same axis
Definitions
- the present invention relates to a transmission, and more particularly to a transmission corresponding to a double clutch device.
- an automatic transmission As a means for automatically shifting a vehicle.
- AT automatic transmission
- a combination of a torque converter and a plurality of planetary gears and clutches has become the mainstream. Due to the continuously variable speed action of the torque converter and the automatic switching of multiple clutches, the AT does not require clutch operation by the driver when starting, stopping, and shifting as required by the manual transmission (MT).
- MT manual transmission
- AT uses a torque converter that uses fluid
- transmission efficiency is inferior to MT, which mechanically connects the input and output sides directly to transmit torque. Therefore, the AT has the advantage of reducing the driver's labor, but has the disadvantage of reducing the fuel consumption of the vehicle. Therefore, in order to ensure the transmission efficiency of MT and eliminate the need for clutch operation, an automatic transmission (AMT) that has been automated based on the MT structure has been developed.
- the AMT automates the MT clutch operation and the transmission gear shifting operation, and can eliminate the need for clutch operation while ensuring the same transmission efficiency as the conventional MT.
- AMT disengages the clutch during the shifting operation, just like MT, so torque transmission is temporarily interrupted. While the torque transmission is interrupted, the vehicle is driven only by inertia without acceleration, so when the gear is shifted, the slight torque loss greatly affects the acceleration of the vehicle, causing the driver to feel uncomfortable. Cheap.
- AT since multiple clutches are used, torque is not lost during gear shifting.
- the compound clutch device mainly includes an input shaft, a first output shaft, a second output shaft, a first clutch, and a second clutch.
- the input shaft is also used to input torque to the double clutch device.
- the first output shaft is used to output torque to the transmission side and is arranged coaxially with the input shaft. Is placed.
- the second output shaft is for outputting torque to the transmission side, and is a cylindrical member arranged coaxially on the outer peripheral side of the first output shaft.
- the first clutch is for transmitting and interrupting the torque input to the input shaft to the first output shaft.
- the second clutch is for transmitting and interrupting the torque input to the input shaft to the second output shaft, and is disposed on the outer peripheral side of the first clutch (see, for example, Patent Document 1;). .
- torque can be transmitted alternately to the first and second output shafts by the first and second clutches in order to prevent torque interruption.
- the first and second output shafts can be selectively connected to different gear pairs.
- the first clutch is connected and torque is transmitted to the first output shaft.
- the second output shaft is connected to any one of the gear pairs, and the first clutch is connected.
- the second clutch can be connected to transmit torque to the second output shaft. The reverse operation is also possible. Therefore, the AMT that employs this dual clutch device does not lose torque during gear shifting, and allows smooth and wasteful gear shifting operations.
- Patent Document 1 JP 2000-352431 A
- Patent Document 2 Japanese Patent Application Laid-Open No. 2004-217204
- the AMT described above employs a stepped transmission that is composed of a plurality of gears and the like.
- a stepped transmission due to the reduction ratio, the engine speed after a shift decreases when shifting up. Therefore, it is necessary to increase the engine speed before shifting by the step of the reduction ratio.
- fuel consumption is reduced and noise is increased.
- the transmission installed in the AMT needs to increase the number of shift stages in order to reduce the reduction ratio step compared to the conventional one, and the transmission becomes large.
- this transmission shifts only one clutch in a half-clutch state at the time of starting, there is a problem that the facing of one clutch is worn compared to the other.
- the multiple clutch device has a larger axial dimension than a conventional MT clutch due to a plurality of clutches and a mechanism associated therewith.
- the overall axial dimension of the AMT becomes large, and a reduction in the size of the transmission is desired.
- the transmission needs as many gear pairs as the number of shift stages for forward movement.
- four retaining structures are required (see, for example, Patent Document 2;). Since these gear pairs and the switching mechanism are arranged in the axial direction, it is difficult to reduce the size of the transmission.
- An object of the present invention is to realize a simple and compact transmission with a smaller number of gears and fewer gears.
- Another object of the present invention is to reduce the wear of the clutch housing when the vehicle starts.
- the transmission according to claim 1 is mounted on an automatic transmission having a double clutch device that can selectively connect and disconnect the first and second clutches, and the torque from the engine is output to the output side. It is for transmission.
- the transmission is composed of a first input shaft, a second input shaft, a counter shaft, an output shaft, a first gear pair, a first switching mechanism, and a second switching mechanism.
- the first input shaft is for inputting torque via the first clutch.
- the second input shaft is for inputting torque via the second clutch.
- the secondary axis is arranged in parallel to the first input axis.
- the output shaft is arranged coaxially with respect to either the first input shaft or the auxiliary shaft.
- the first gear pair is composed of a first gear fixed to the second input shaft and a second gear fixed to the counter shaft and meshed with the first gear.
- the first mechanism can selectively connect and disconnect the first input shaft and the sub shaft with at least two different reduction ratios.
- the second switching mechanism can selectively connect and disconnect either the first input shaft or the sub shaft and the output shaft.
- the dual clutch device can selectively operate the first and second clutches, torque is input from one of the first and second input shafts to the transmission. it can.
- the torque transmission path of this speed change device becomes several.
- the first switching mechanism is capable of selectively connecting and disconnecting the first input shaft and the secondary shaft with two types of reduction ratios, There are the following six torque transmission paths from the second input shaft to the output shaft.
- this transmission can realize a six-speed transmission. Compared with the conventional six-speed transmission, the conventional transmission requires six gear pairs and four gears, whereas this transmission has four gear pairs and two gear pairs. Only a retaining structure is needed. As a result, this transmission can realize a six-speed transmission corresponding to the double clutch device with fewer components than in the past. As a result, this transmission can be reduced in size in the axial direction as compared with the prior art, and can be downsized. And the enlargement of the whole AMT can be prevented.
- the transmission according to claim 2 further includes a second gear pair and a third gear pair according to claim 1.
- the second gear pair includes a third gear fixed to one of the first input shaft and the counter shaft, and a third gear arranged to be rotatable relative to the other of the first input shaft and the counter shaft. It consists of a meshing fourth gear.
- the third gear pair includes a fifth gear fixed to one of the first input shaft and the counter shaft, and a fifth gear arranged to be rotatable relative to the other of the first input shaft and the counter shaft. It consists of a 6th gear that meshes.
- the first switching mechanism can connect the first input shaft and the auxiliary shaft via either one of the second and third gear pairs.
- the transmission includes the second and third gear pairs, by appropriately setting the reduction ratios thereof, a six-stage speed change corresponding to the dual clutch device with fewer components than in the past. Can be realized. As a result, this transmission can reduce the axial dimension as compared with the prior art. And miniaturization can be achieved. And it is possible to prevent the entire AMT from becoming large.
- the speed change device can reduce the step of the speed reduction ratio of each gear in the low speed range by appropriately setting the speed reduction ratio of the second and third gear pairs. As a result, in this transmission, the vehicle can be started by sliding the second clutch at the second speed before the first clutch finishes sliding at the first speed, for example. As a result, in this speed change device, the wearing of the facing can be reduced by sharing the load at the time of starting with the first and second clutches.
- the transmission according to claim 3 further includes a fourth gear pair according to claim 1 or 2.
- the fourth gear pair meshes with the seventh gear fixed to either the countershaft or the output shaft and the seventh gear arranged to be rotatable relative to the other of the countershaft or the output shaft. It consists of the eighth gear.
- the second switching mechanism selectively switches between the connection of the auxiliary shaft and the output shaft through the fourth gear pair and the connection of the first input shaft and the output shaft without using the fourth gear pair. It is possible to cancel.
- the second switching mechanism can selectively switch the connection between the auxiliary shaft and the output shaft and the connection between the first input shaft and the output shaft.
- Torque transmission by connecting the subshaft and the output shaft is performed via the fourth gear pair.
- this transmission device can reduce the step of the reduction ratio of each gear in the low speed range by appropriately setting the reduction ratio of the fourth gear pair.
- this transmission can be reduced in size in the axial direction as compared with the prior art, and can be downsized. And it is possible to prevent the overall size of the ATM from being increased.
- a transmission according to a fourth aspect of the present invention further includes the fourth gear pair according to the first or second aspect.
- the fourth gear pair is a seventh gear fixed to one of the first input shaft and the output shaft, and a seventh gear disposed so as to be rotatable relative to the other of the first input shaft and the output shaft. It is composed of an 8th gear that meshes with.
- the second switching mechanism selectively switches between the connection between the first input shaft and the output shaft via the fourth gear pair and the connection between the sub shaft and the output shaft not via the fourth gear pair. It is possible to cancel.
- the second switching mechanism connects the first input shaft and the output shaft and connects the sub shaft to the output.
- the connection with the force shaft can be selectively switched.
- Torque transmission by the connection between the first input shaft and the output shaft is performed via the fourth gear pair.
- this transmission device can reduce the step of the reduction ratio of each gear in the low speed range by appropriately setting the reduction ratio of the fourth gear pair.
- the speed change device can be reduced in size in the axial direction and can be downsized. And it is possible to prevent the entire AMT from becoming large.
- a transmission according to a fifth aspect includes the fifth gear pair and the third switching mechanism according to any one of the first to third aspects.
- the fifth gear pair includes a ninth gear fixed to one of the first input shaft and the counter shaft, and a ninth gear arranged to be rotatable relative to the other of the first input shaft and the counter shaft. It consists of a tenth gear that meshes.
- the third switching mechanism can selectively connect and disconnect one of the first input shaft and the counter shaft and the other of the first input shaft and the counter shaft via the fifth gear pair.
- this transmission device includes the fifth gear pair and the third notch structure, a maximum of eight speeds can be achieved by combining with another gear pair.
- the first gear is fixed to the second input shaft and the first mechanism allows the first input shaft and the sub shaft to be selectively connected and disconnected by two types of reduction ratios
- the first and first 2Torque transmission paths from the input shaft to the output shaft are as follows.
- this transmission can realize an eight-speed shift. .
- the conventional transmission requires eight gear pairs and at least four gears, which is the same number as the speed stage, whereas this transmission is Only 5 gear pairs and 3 gears are needed.
- this transmission can achieve an eight-speed transmission corresponding to the dual clutch device with fewer components than in the past.
- the transmission according to claim 6 is the transmission device according to any one of claims 2 to 5, wherein the reduction ratio from the second input shaft to the sub shaft of the first gear pair is the first input shaft of the second gear pair.
- the reduction ratio from the first input shaft of the third gear pair to the sub shaft is smaller than the reduction ratio from the first gear to the sub shaft. Smaller than the reduction ratio to /!
- the reduction gear ratio becomes smaller in the order of the second, first, and third gear pairs, so that the desired number of shift stages can be realized with certainty.
- the transmission can be reduced in size in the axial direction and can be reduced in size. And it is possible to prevent the entire AMT from becoming large.
- the reduction ratio means a reduction ratio from the drive side to the driven side.
- the transmission according to claim 7 is the transmission according to claim 6, wherein the reduction ratio from the first input shaft to the sub shaft of the fifth gear pair is the first input axial force of the second gear pair.
- the reduction ratio from the first input shaft to the countershaft of the fifth gear pair which is smaller than the ratio, is greater than the reduction ratio from the second input shaft to the subshaft of the first gear pair.
- the reduction ratio becomes smaller in the order of the second, fifth, first, and third gear pairs, so that it is possible to reliably realize an eight-speed transmission.
- the transmission can be reduced in size in the axial direction as compared with the prior art, and can be downsized. And it is possible to prevent the entire AMT from becoming large.
- the reduction ratio means the reduction ratio from the drive side to the driven side.
- the transmission according to claim 8 is the transmission according to any one of claims 1 to 7, wherein the output shaft is arranged coaxially with respect to the first input shaft.
- FR vehicle means a rear-wheel drive vehicle (Front Engine Rear Drive) equipped with an engine in front.
- a transmission according to a ninth aspect is the transmission according to any one of the first to seventh aspects, wherein the output shaft is coaxially arranged with respect to the auxiliary shaft.
- the output shaft is arranged coaxially with respect to the sub-shaft, this transmission can be used for FF vehicles.
- the front-wheel drive means a front-wheel drive (Front Engine Front Drive) equipped with an engine in front.
- a transmission according to a tenth aspect is the cylindrical member according to any one of the first to seventh aspects, wherein the output shaft is coaxially disposed on the outer peripheral side of the auxiliary shaft.
- this transmission can be used for an FF vehicle.
- FF vehicles are front-wheel drive with an engine in front (
- a transmission according to an eleventh aspect is the cylindrical member according to any one of the first to tenth aspects, wherein the second input shaft is coaxially disposed on the outer peripheral side of the first input shaft.
- a transmission according to a twelfth aspect is the cylindrical member according to any one of the first to tenth aspects, wherein the first input shaft is coaxially disposed on the outer peripheral side of the second input shaft.
- FIG. 1 is a configuration diagram of an AMT equipped with a double clutch device.
- FIG. 2 is a configuration diagram of a transmission as a first embodiment of the present invention, and torque transmission of the transmission The schematic diagram of a path
- FIG. 3 shows the control and reduction ratio of a fastening element at each gear stage of the transmission as the first embodiment of the present invention.
- FIG. 4 is a configuration diagram of a transmission as a second embodiment of the present invention, and a schematic diagram of a torque transmission path of the transmission.
- FIG. 5 shows control and reduction ratio of a fastening element at each gear position of a transmission as a second embodiment of the present invention.
- FIG. 6 is a configuration diagram of a transmission as a third embodiment of the present invention, and a schematic diagram of a torque transmission path of the transmission.
- FIG. 7 shows control and reduction ratio of a fastening element at each gear position of a transmission as a third embodiment of the present invention.
- FIG. 8 is a configuration diagram of a transmission as a fourth embodiment of the present invention, and a schematic diagram of a torque transmission path of the transmission.
- FIG. 9 is a configuration diagram of a transmission as a fourth embodiment of the present invention, and a schematic diagram of a torque transmission path of the transmission.
- FIG. 10 is a configuration diagram of a transmission as a fifth embodiment of the present invention, and a schematic diagram of a torque transmission path of the transmission.
- FIG. 11 Control of a fastening element and a reduction gear ratio at each shift stage of a transmission as a fifth embodiment of the present invention.
- Figure 1 shows the configuration of an AMT equipped with a dual clutch device.
- the engine is located on the right side.
- the AMT is mainly composed of a double clutch device 1, a transmission device 2, and a casing (not shown), and the operation of each device is automatically performed by hydraulic control or the like.
- the double clutch device 1 mainly includes an input shaft 5, a first output shaft 50, a second output shaft 60, a first clutch C1, and a second clutch C2.
- the input shaft 5 is a member to which torque from the engine is input, and is inertially connected to the flywheel 3 on the engine (not shown) side via the damper mechanism 4 in the rotational direction.
- the first output shaft 50 starts from the input shaft 5 This is for outputting the input torque to the transmission 2 side.
- the second output shaft 60 is for outputting torque input from the input shaft 5 to the transmission 2 side.
- the first clutch C1 is for transmitting and interrupting torque between the input shaft 5 and the first output shaft 50.
- the second clutch C2 is for transmitting and interrupting torque between the input shaft 5 and the second output shaft 60.
- the double clutch device 1 can selectively output the torque to the first output shaft 50 or the second output shaft 60 by selectively operating the first and second clutches 50 and 60.
- the torque transmitted to the first output shaft 50 or the second output shaft 60 is output from the output shaft 40 after being shifted by the transmission 2.
- the transmission 2 of the present invention employed in the AMT described above the following first to fifth embodiments can be considered.
- FIG. 2 (a) shows a configuration diagram of the transmission as the first embodiment of the present invention.
- the transmission 2 includes a first input shaft 10, a second input shaft 20, a counter shaft 30, an output shaft 40, a first gear pair 110, and a second gear pair. 120, a third gear pair 130, a fourth gear pair 140, a first switching mechanism 160, a second shelf structure 170, a casing (not shown), and a force are also configured.
- the first input shaft 10 is for receiving torque from the double clutch device 1, and is provided so as not to rotate relative to the first output shaft 50 of the first clutch C1.
- the second input shaft 20 is for receiving torque from the dual clutch device 1, and is provided so as not to rotate relative to the second output shaft 60 of the second clutch C2.
- the second input shaft 20 is a cylindrical member that is coaxially disposed on the outer peripheral side of the first input shaft 10.
- the secondary shaft 30 is arranged in parallel to the first input shaft 10.
- the output shaft 40 is for outputting torque from the transmission 2 and is disposed coaxially with the first input shaft 10.
- the first input shaft 10, the second input shaft 20, and the output shaft 40 are arranged on the same axis, and the auxiliary shaft 30 is arranged in parallel to these axes. ing.
- the transmission 2 can be used in FR vehicles.
- the first gear pair 110 is for connecting the second input shaft 20 and the countershaft 30 with the gear 111 and , And gear 112.
- the gear 111 is fixed to the second input shaft 20.
- the gear 112 is fixed to the ⁇ IJ shaft 30.
- the gear 111 and the gear 112 are intertwined with each other.
- the second gear pair 120 is for connecting the first input shaft 10 and the countershaft 30, and includes a gear 121 and a gear 122.
- the gear 121 is disposed so as to be rotatable relative to the first input shaft 10.
- the gear 122 is fixed to the countershaft 30. The tooth wheel 121 and the gear 122 are squeezed together.
- the third gear pair 130 is for connecting the first input shaft 10 and the countershaft 30, and includes a gear 131, a gear 132, and a force.
- the gear 131 is arranged to be rotatable relative to the first input shaft 10.
- the gear 132 is fixed to the countershaft 30.
- the gear 131 and the gear 132 are intertwined with each other.
- the fourth gear pair 140 is for connecting the output shaft 40 and the countershaft 30 and includes a gear 141 and a gear 142.
- the gear 141 is disposed so as to be rotatable relative to the output shaft 40.
- the gear 142 is fixed to the countershaft 30.
- the gear 141 and the gear 142 are intertwined with each other.
- the first structure 160 is for selectively connecting and disconnecting the first input shaft 10 and the countershaft 30 at two different reduction ratios.
- the gear 161 and the first switching gear S1 And a second switching gear S2 and a first sleeve 162.
- the gear 161 is fixed to the first input shaft 10.
- the first switching gear S1 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 121.
- the second switching gear S2 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 131.
- the first sleeve 162 is a cylindrical member disposed on the outer peripheral side of the gear 161, and the inner peripheral side thereof meshes with the gear 161.
- the first sleeve 162 is movable relative to the first input shaft 10 in the axial direction, so that one of the first switching gear S1 and the second switching gear S2 is connected to and disconnected from the gear 161. Can be switched.
- the second notch structure 170 is for selectively connecting and disconnecting either the first input shaft 10 or the counter shaft 30 and the output shaft 40, and the gear 171 and the third switch.
- a gear S3, a fourth switching gear S4, and a second sleeve 172 are included.
- the gear 171 is fixed to the output shaft 40.
- the third switching gear S3 is provided such that it can rotate relative to the output shaft 40 and cannot rotate relative to the gear 141.
- the fourth switching gear S4 is connected to the first input shaft 10. On the other hand, it is provided so as not to be able to rotate relatively.
- the second sleeve 172 is a cylindrical member disposed on the outer peripheral side of the gear 171, and the inner peripheral side thereof meshes with the gear 171. The second sleeve 172 can be moved relative to the output shaft 40 in the axial direction to switch between connection and disconnection of either the third switching gear S3 or the fourth switching gear S4 and the gear 171. It is.
- the reduction gear ratio is generally the number of teeth on the driven side gear divided by the number of teeth on the driving side gear.
- each gear pair is switched between the driven side and the driving side.
- the gears on the first input shaft 10 and the second input shaft 20 side are assumed to be drive gears.
- the drive side and the driven side are not interchanged, so the gear on the output shaft 40 side is the driven side gear.
- the reduction ratio of the first to fourth gear pairs is, for example,
- this transmission 2 can reliably realize a six-speed shift. Specifically, it is sufficient if the condition of ⁇ 2> ⁇ 1> ⁇ 3 is satisfied.
- FIG. 2 (b) is a schematic diagram of the torque transmission path of the transmission as the first embodiment of the present invention
- FIG. 3 is a diagram showing the control of the fastening elements at each gear stage of the transmission according to the first embodiment of the present invention. Indicates the reduction ratio.
- the dotted lines indicate the respective axes, and the solid lines indicate the torque transmission paths at the respective shift stages.
- the operating clutch is indicated by “C1” or “C2”. Further, in FIG.
- this transmission 2 can achieve a forward six-speed shift with only four gear pairs and two gears.
- the transmission 2 can be reduced in axial dimension as compared with the prior art, and can be downsized.
- the overall size of the bag can be prevented from increasing.
- the transmission 2 can reduce the step of the reduction ratio between the first forward speed and the second speed as shown in FIG.
- the forward first speed is You can start by sliding the second clutch C2 at the second speed before the first clutch CI finishes sliding.
- the wear of the facing can be reduced by sharing the load at the time of starting with the first and second clutches Cl and C2.
- FIG. 4 (a) shows a configuration diagram of a transmission as a second embodiment of the present invention.
- the transmission 2 includes a first input shaft 10, a second input shaft 20, a counter shaft 30, an output shaft 40, a first gear pair 210, and a second gear pair. 220, a third gear pair 230, a fourth gear pair 240, a first switching mechanism 260, a second shelf structure 270, a casing (not shown), and a force are also configured.
- the first input shaft 10 is for receiving torque from the double clutch device 1, and is provided so as not to rotate relative to the first output shaft 50 of the first clutch C1.
- the second input shaft 20 is for receiving torque from the dual clutch device 1, and is provided so as not to rotate relative to the second output shaft 60 of the second clutch C2.
- the first input shaft 10 is a cylindrical member that is coaxially disposed on the outer peripheral side of the second input shaft 20.
- the secondary shaft 30 is arranged in parallel to the second input shaft 20.
- the output shaft 40 is for outputting torque from the transmission 2 and is arranged coaxially with the subshaft 30.
- the output shaft 40 is disposed on the engine side with respect to the auxiliary shaft 30.
- the auxiliary shaft 30 and the output shaft are arranged in parallel to the first and second input shafts 10 and 20. With this configuration, the transmission 2 can be used in a front-wheel drive vehicle.
- the first gear pair 210 is for connecting the second input shaft 20 and the countershaft 30, and includes a gear 211 and a gear 212.
- the gear 211 is fixed to the second input shaft 20.
- the gear 212 is fixed to the ⁇ IJ shaft 30.
- the gear 211 and the gear 212 are intertwined with each other.
- the second gear pair 220 is for connecting the first input shaft 10 and the countershaft 30 and includes a gear 221 and a gear 222.
- the gear 221 is fixed to the first input shaft 10.
- the gear 222 is disposed so as to be rotatable relative to the countershaft 30.
- the gear 221 and the gear 222 are intertwined with each other.
- the third gear pair 130 is for connecting the first input shaft 10 and the subshaft 30 and includes a gear 231, a gear 232, and the like.
- Gear 2 31 is fixed to the first input shaft 10.
- the gear 232 is disposed so as to be rotatable relative to the countershaft 30.
- the gear 231 and the gear 232 are intertwined with each other.
- the fourth gear pair 240 is for connecting the output shaft 40 and the first input shaft 10, and includes a gear 241 and a gear 242.
- the gear 241 is fixed to the first input shaft 10.
- the gear 242 is disposed so as to be rotatable relative to the output shaft 40.
- the gear 241 and the gear 242 are intertwined with each other.
- the first mechanism 260 is for selectively connecting and disconnecting the first input shaft 10 and the countershaft 30 with two different reduction ratios.
- the gear 261 and the first switching gear S1 And a second switching gear S2 and a first sleeve 262.
- the gear 261 is fixed to the countershaft 30.
- the first switching gear S1 is provided such that it can rotate relative to the countershaft 30 and cannot rotate relative to the gear 222.
- the second switching gear S2 is provided such that it can rotate relative to the countershaft 30 and cannot rotate relative to the gear 232.
- the first sleeve 262 is a cylindrical member disposed on the outer peripheral side of the gear 261, and the inner peripheral side thereof meshes with the gear 261. The first sleeve 262 can be moved relative to the countershaft 30 in the axial direction to switch between connection and release of either the first switching gear S1 or the second switching gear S2 and the gear 261. It is said.
- the second cut-off shelf structure 270 is for selectively connecting and disconnecting either the first input shaft 10 or the counter shaft 30 and the output shaft 40, and includes a gear 271 and a third switch.
- a gear S3, a fourth switching gear S4, and a second sleeve 272 are included.
- the gear 271 is fixed to the output shaft 40.
- the third switching gear S3 is provided such that it can rotate relative to the output shaft 40 and cannot rotate relative to the gear 242.
- the fourth switching gear S4 is provided so as not to rotate relative to the countershaft 30.
- the second sleeve 272 is a cylindrical member disposed on the outer peripheral side of the gear 271, and the inner peripheral side thereof meshes with the gear 271.
- the second sleeve 272 is movable relative to the output shaft 40 in the axial direction so that the connection and disconnection of either the third switching gear S3 or the fourth switching gear S4 and the gear 271 can be switched. Yes.
- the reduction gear ratio is generally the number of teeth on the driven side gear divided by the number of teeth on the driving side gear.
- each gear pair is switched between the driven side and the driving side.
- the first input shaft 10 The gear on the second input shaft 20 side is used as the gear on the driving side.
- the fourth gear pair 140 the drive side and the driven side are not interchanged, so the gear on the output shaft 40 side is the driven side gear.
- the reduction ratio of the first to fourth gear pairs is, for example,
- this transmission 2 can reliably realize a six-speed shift. Specifically, the condition of ⁇ 2> ⁇ 1> ⁇ 3 may be satisfied.
- FIG. 4 (b) is a schematic diagram of the torque transmission path of the transmission according to the second embodiment of the present invention, and FIG. Indicates the reduction ratio.
- dotted lines indicate the respective axes, and solid lines indicate the torque transmission paths at the respective shift stages.
- the operating clutch is indicated by “C1” or “C2”.
- the clutches and the switching gears that are connected at each gear stage are indicated by “ ⁇ ”, and the switching gears that are connected in preparation for upshifting and downshifting are indicated by “( ⁇ )”.
- the right side of FIG. 5 shows the reduction ratio of the entire transmission 2, the step of the reduction ratio of each shift stage, and the entire range.
- the transmission 2 can realize a forward six-speed shift with only four gear pairs and two gears. As a result, the transmission 2 can be reduced in axial dimension as compared with the prior art, and can be downsized. In addition, the overall size of the bag can be prevented from increasing. Further, the transmission 2 can reduce the step of the reduction ratio between the first forward speed and the second speed as shown in FIG. As a result, the transmission 2 can start by sliding the second clutch C2 at the second speed before the first clutch C1 finishes sliding at the first forward speed. As a result, in this transmission 2, the wear of the facing can be reduced by sharing the load at the time of starting with the first and second clutches Cl and C2.
- FIG. 6 (a) shows a configuration diagram of a transmission as a third embodiment of the present invention.
- the transmission 2 includes a first input shaft 10, a second input shaft 20, a counter shaft 30, an output shaft 40, a first gear pair 310, and a second gear pair. 320, a third gear pair 330, a fourth gear pair 340, a first switching mechanism 360, a second shelf structure 370, a casing (not shown), and a force are also configured.
- the first input shaft 10 is for receiving torque from the double clutch device 1, and is provided so as not to rotate relative to the first output shaft 50 of the first clutch C1.
- the second input shaft 20 is for receiving torque from the dual clutch device 1, and is provided so as not to rotate relative to the second output shaft 60 of the second clutch C2.
- the first input shaft 10 is a cylindrical member that is coaxially disposed on the outer peripheral side of the second input shaft 20.
- the secondary shaft 30 is arranged in parallel to the second input shaft 20.
- the output shaft 40 is for outputting torque from the transmission 2 and is arranged coaxially with the subshaft 30.
- the output shaft 40 is disposed on the engine side with respect to the auxiliary shaft 30.
- the auxiliary shaft 30 and the output shaft are arranged in parallel to the first and second input shafts 10 and 20. With this configuration, the transmission 2 can be used in a front-wheel drive vehicle.
- the first gear pair 310 is for connecting the second input shaft 20 and the countershaft 30, and includes a gear 311 and a gear 312.
- the gear 311 is fixed to the second input shaft 20.
- the gear 312 is fixed to the IJ shaft 30.
- the gear 311 and the gear 312 are intertwined with each other.
- the second gear pair 320 is used to connect the first input shaft 10 and the countershaft 30 and includes a gear 321 and a gear 322.
- the gear 321 is fixed to the first input shaft 10.
- the gear 322 is disposed so as to be rotatable relative to the countershaft 30.
- the gear 321 and the gear 322 are intertwined with each other.
- the third gear pair 330 is for connecting the first human power shaft 10 and the ij shaft 30 and includes a gear 331, a gear 332, and the like.
- the gear 331 is fixed to the first input shaft 10.
- the gear 332 is disposed so as to be rotatable relative to the countershaft 30.
- the gear 331 and the gear 332 are intertwined with each other.
- the fourth gear pair 340 is for connecting the output shaft 40 and the first input shaft 10, and includes a gear 341 and a gear 342.
- the gear 341 is fixed to the first input shaft 10.
- the gear 342 is disposed so as to be rotatable relative to the output shaft 40.
- the gear 341 and the gear 342 are intertwined with each other.
- the first structure 360 is for selectively connecting and disconnecting the first input shaft 10 and the countershaft 30 at two different reduction ratios.
- the gear 361 is fixed to the countershaft 30.
- the first switching gear S1 is rotatable relative to the countershaft 30 and to the gear 322. So that it cannot rotate relative to the other.
- the second switching gear S2 is provided such that it can rotate relative to the countershaft 30 and cannot rotate relative to the gear 332.
- the first sleeve 362 is a cylindrical member disposed on the outer peripheral side of the gear 361, and the inner peripheral side thereof meshes with the gear 361. The first sleeve 362 can be moved relative to the countershaft 30 in the axial direction, so that the connection between the first switching gear S1 and the second switching gear S2 and the gear 361 can be switched. It is said.
- the second cut shelf structure 370 is for selectively connecting and disconnecting either the first input shaft 10 or the counter shaft 30 and the output shaft 40.
- a gear S3, a fourth switching gear S4, and a second sleeve 372 are included.
- the gear 371 is fixed to the output shaft 40.
- the third switching gear S3 is provided such that it can rotate relative to the output shaft 40 and cannot rotate relative to the gear 342.
- the fourth switching gear S4 is provided so as not to rotate relative to the countershaft 30.
- the second sleeve 372 is a cylindrical member disposed on the outer peripheral side of the gear 371, and the inner peripheral side of the second sleeve 372 meshes with the gear 371.
- the second sleeve 372 can be switched between connection and disengagement of one of the third switching gear S3 and the fourth switching gear S4 and the gear 371 by moving relative to the output shaft 40 in the axial direction.
- the reduction gear ratio is generally the number of teeth on the driven side gear divided by the number of teeth on the driving side gear.
- each gear pair is switched between the driven side and the driving side.
- the gears on the first input shaft 10 and the second input shaft 20 side are assumed to be drive gears.
- the drive side and the driven side are not interchanged, so the gear on the output shaft 40 side is the driven side gear.
- the reduction ratio of the first to fourth gear pairs is, for example,
- this transmission 2 can reliably realize a six-speed shift. Specifically, the condition of ⁇ 2> ⁇ 1> ⁇ 3 may be satisfied. [0075] (2) Operation of transmission
- FIG. 6 (b) is a schematic diagram of a torque transmission path of a transmission as a third embodiment of the present invention, and FIG. Indicates the reduction ratio.
- the dotted lines indicate the respective axes, and the solid lines indicate the torque transmission paths at the respective shift stages.
- the clutch to be operated is indicated by “C1” or “C2”.
- the clutches and the switching gears that are connected at each gear stage are indicated by “ ⁇ ”, and the switching gears that are connected in preparation for upshifting and downshifting are indicated by “( ⁇ )”.
- the right side of FIG. 7 shows the reduction ratio of the entire transmission 2, the step of the reduction ratio of each shift stage, and the entire range.
- the first clutch C1 is disengaged so that torque is not input to the first input shaft 10.
- the gear 361 and the second switching gear S2 are connected in advance by the first sleeve 362 of the first Kiriura structure 360. Then, the connection of the first clutch C1 is released and the second clutch C2 is connected. At this time, similarly to the second speed, the connection between the gear 371 and the third switching gear S3 is maintained by the second sleeve 372 of the second cutting mechanism 370.
- the torque input to the second input shaft 20 via the second clutch C2 is the first gear pair 310, the countershaft 30, the second gear pair 320, the second gear
- the vehicle travels at the third speed by being transmitted to the output shaft 40 via the input shaft and the fourth gear pair 340.
- the first sleeve 362 of the first cutting mechanism 360 is used in advance.
- the helical gear 361 and the second switching gear S2 are connected.
- the connection of the second clutch C2 is released and the first clutch C1 is connected.
- the connection of the fourth switching gear S4 in the second shelf structure 370 is maintained.
- the torque input to the first input shaft 10 via the first clutch C1 is transmitted to the output shaft 40 via the third gear pair 330 and the countershaft 30.
- this transmission 2 can realize a forward six-speed shift with only four gear pairs and two gears. As a result, the transmission 2 can be reduced in axial dimension as compared with the prior art, and can be downsized. In addition, the overall size of the bag can be prevented from increasing. Further, the transmission 2 can reduce the step of the reduction ratio between the first forward speed and the second speed as shown in FIG. As a result, the transmission 2 can start by sliding the second clutch C2 at the second speed before the first clutch C1 finishes sliding at the first forward speed. As a result, in this transmission 2, the wear of the facing can be reduced by sharing the load at the time of starting with the first and second clutches Cl and C2.
- FIG. 8 (a) shows a configuration diagram of a transmission as a fourth embodiment of the present invention.
- the transmission 2 includes a first input shaft 10, a second input shaft 20, a counter shaft 30, an output shaft 40, a first gear pair 410, and a second gear pair.
- 420, the third gear pair 430, the fourth gear pair 440, the first switching mechanism 460, the second shelf structure 470, the third shelf structure 480, the casing (not shown) and the force are also configured. ing
- the first input shaft 10 is for receiving torque from the double clutch device 1, and is provided so as not to rotate relative to the first output shaft 50 of the first clutch C1.
- the second input shaft 20 is for receiving torque from the dual clutch device 1, and is provided so as not to rotate relative to the second output shaft 60 of the second clutch C2.
- the second input shaft 20 is a cylindrical member that is coaxially disposed on the outer peripheral side of the first input shaft 10.
- the secondary shaft 30 is arranged in parallel to the first input shaft 10.
- the output shaft 40 outputs torque from the transmission 2. And is arranged coaxially with the countershaft 30.
- the output shaft 40 is disposed on the engine side with respect to the auxiliary shaft 30.
- the auxiliary shaft 30 and the output shaft are arranged in parallel to the first and second input shafts 10 and 20. With this configuration, the transmission 2 can be used in a front-wheel drive vehicle.
- the first gear pair 410 is used to connect the second input shaft 20 and the countershaft 30 and includes a gear 411 and a gear 412.
- the gear 411 is fixed to the second input shaft 20.
- the gear 412 is fixed to the IJ shaft 30.
- the gear 411 and the gear 412 are intertwined with each other.
- the second gear pair 420 is for connecting the first input shaft 10 and the countershaft 30, and includes a gear 421 and a gear 422.
- the gear 421 is disposed so as to be rotatable relative to the first input shaft 10.
- the gear 422 is fixed to the countershaft 30.
- the gear wheel 421 and the gear wheel 422 are intertwined with each other.
- the third gear pair 430 is for connecting the first input shaft 10 and the countershaft 30, and is also configured with a gear 431, a gear 432, and a force.
- the gear 431 is arranged to be rotatable relative to the first input shaft 10.
- the gear 432 is fixed to the countershaft 30.
- the gear 431 and the gear 432 are intertwined with each other.
- the fourth gear pair 440 is for connecting the output shaft 40 and the countershaft 30, and includes a gear 441 and a gear 442.
- the gear 441 is disposed so as to be rotatable relative to the first input shaft 10.
- the gear 442 is fixed to the output shaft 40. And the gears 441 and 442 are mixed with each other!
- the first structure 460 is for selectively connecting and disconnecting the first input shaft 10 and the countershaft 30 at two different reduction ratios.
- the gear 461 and the first switching gear S1 And a second switching gear S2 and a first sleeve 462.
- the gear 461 is fixed to the first input shaft 10.
- the first switching gear S1 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 421.
- the second switching gear S2 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 431.
- the first sleeve 462 is a cylindrical member disposed on the outer peripheral side of the gear 461, and the inner peripheral side thereof meshes with the gear 461.
- the first sleeve 462 is movable relative to the first input shaft 10 in the axial direction, so that one of the first switching gear S1 and the second switching gear S2 is connected to and disconnected from the gear 461. Can be switched.
- the second switching mechanism 470 is for selectively connecting and disconnecting the first input shaft 10 and the output shaft 40.
- the second switching mechanism 470 includes a gear 471, a third switching gear S3, a second sleeve 472, and the like. It consists of The gear 471 is fixed to the first input shaft 10.
- the third switching gear S3 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 441.
- the second sleeve 472 is a cylindrical member disposed on the outer peripheral side of the gear 471, and the inner peripheral side thereof meshes with the gear 471.
- the second sleeve 472 is movable relative to the output shaft 40 in the axial direction so that the connection and release of the connection between the third switching gear S3 and the gear 471 can be switched.
- the third switching mechanism 480 is for selectively connecting and disconnecting the sub-shaft 30 and the output shaft 40.
- the third switching mechanism 480 is provided with a gear 481, a fourth switching gear S4, a third sleeve 482, and a force. It is configured .
- the gear 481 is fixed to the countershaft 30.
- the fourth switching gear S4 is provided so as not to rotate relative to the output shaft 40.
- the third sleeve 482 is a cylindrical member disposed on the outer peripheral side of the gear 481, and the inner peripheral side thereof meshes with the gear 481. The third sleeve 482 can move relative to the output shaft 40 in the axial direction so that the connection and disconnection of the fourth switching gear S4 and the gear 481 can be switched.
- the reduction gear ratio is generally the number of teeth on the driven side gear divided by the number of teeth on the driving side gear.
- each gear pair is switched between the driven side and the driving side.
- the gears on the first input shaft 10 and the second input shaft 20 side are assumed to be drive gears.
- the fourth gear pair 140 the drive side and the driven side are not interchanged, so the gear on the output shaft 40 side is the driven side gear.
- the reduction ratio of the first to fourth gear pairs is, for example,
- this transmission 2 can reliably realize a six-speed shift. Specifically, the condition of ⁇ 2> ⁇ 1> ⁇ 3 may be satisfied. [0091] (2) Operation of transmission
- FIG. 8 (b) is a schematic diagram of the torque transmission path of the transmission as the fourth embodiment of the present invention, and FIG. Indicates the reduction ratio.
- the dotted lines indicate the respective axes, and the solid lines indicate the torque transmission paths at the respective shift stages.
- the operating clutch is indicated by “C1” or “C2”.
- the clutches and the switching gears connected at the respective speeds are indicated by “ ⁇ ”, and the switching gears connected in preparation for upshifting and downshifting are indicated by “( ⁇ )”.
- the right side of FIG. 9 shows the reduction ratio of the entire transmission 2, the step of the reduction ratio of each shift stage, and the entire range.
- the connection of the first clutch C1 is released, the connection of the fourth switching gear S4 of the third switching mechanism 480 is released, and the third switching mechanism 470 The switching gear S3 is connected. Then, the second clutch C2 is connected. At this time, as in the third speed, the connection of the second switching gear S2 in the first switching mechanism 460 is maintained.
- the torque input to the first input shaft 10 via the first clutch C1 is the first gear pair 410, the countershaft 30, the third gear pair 430, and the first gear shaft 430. This is transmitted to the output shaft 40 via the four-gear pair 440, and the vehicle travels at the fourth speed.
- this transmission 2 can realize a forward six-speed shift with only four gear pairs and two gears.
- the transmission 2 can be reduced in axial dimension as compared with the prior art, and can be downsized.
- the overall size of the bag can be prevented from increasing.
- the transmission 2 can reduce the step of the reduction ratio between the first forward speed and the second speed as shown in FIG.
- the transmission 2 can start by sliding the second clutch C2 at the second speed before the first clutch C1 finishes sliding at the first forward speed.
- the wear of the facing can be reduced by sharing the load at the time of starting with the first and second clutches Cl and C2.
- FIG. 10 (a) shows a configuration diagram of a transmission as a fifth embodiment of the present invention.
- the transmission 2 includes a first input shaft 10, a second input shaft 20, a counter shaft 30, an output shaft 40, a first gear pair 510, and a second gear pair.
- the first input shaft 10 is for receiving torque from the double clutch device 1, and is provided so as not to rotate relative to the first output shaft 50 of the first clutch C1.
- the second input shaft 20 is for receiving torque from the dual clutch device 1, and is provided so as not to rotate relative to the second output shaft 60 of the second clutch C2.
- the second input shaft 20 is a cylindrical member that is coaxially disposed on the outer peripheral side of the first input shaft 10.
- the secondary shaft 30 is arranged in parallel to the first input shaft 10.
- the output shaft 40 is for outputting torque from the transmission 2 and is disposed coaxially with the first input shaft 10.
- the first gear pair 510 is for connecting the second input shaft 20 and the countershaft 30, and includes a gear 511 and a gear 512.
- the gear 511 is fixed to the second input shaft 20.
- the gear 512 is fixed to the ⁇ IJ shaft 30.
- the gear 511 and the gear 512 are intertwined with each other.
- the second gear pair 520 is for connecting the first input shaft 10 and the countershaft 30 and includes a gear 521 and a gear 522.
- the gear 521 is disposed so as to be rotatable relative to the first input shaft 10.
- the gear 522 is fixed to the countershaft 30.
- the tooth wheel 521 and the gear 522 are intertwined with each other.
- the third gear pair 530 is used to connect the first input shaft 10 and the countershaft 30 and includes a gear 531, a gear 532, and the like.
- the gear 531 is disposed so as to be rotatable relative to the first input shaft 10.
- the gear 532 is fixed to the countershaft 30.
- the gear 531 and the gear 532 are intertwined with each other.
- the fourth gear pair 540 is used to connect the output shaft 40 and the countershaft 30 and includes a gear 541 and a gear 542.
- the gear 541 is disposed so as to be rotatable relative to the output shaft 40.
- the gear 542 is fixed to the countershaft 30.
- the gear 541 and the gear 542 are intertwined with each other.
- the fifth gear pair 550 is for connecting the first input shaft 10 and the countershaft 30, and includes a gear 551 and a gear 552.
- the gear 551 is disposed so as to be rotatable relative to the first input shaft 10.
- the gear 552 is fixed to the countershaft 30.
- the gear 551 and the gear 552 are intertwined with each other.
- the first structure 560 is for selectively connecting and disconnecting the first input shaft 10 and the countershaft 30 with two different reduction ratios.
- the gear 561 and the first switching gear S1 And a second switching gear S2 and a first sleeve 562.
- the gear 561 is fixed to the first input shaft 10.
- the first switching gear S1 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 521.
- the second switching gear S2 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 531.
- the first sleeve 562 is a cylindrical member disposed on the outer peripheral side of the gear 561, and the inner peripheral side thereof meshes with the gear 561.
- the first sleeve 562 is movable relative to the first input shaft 10 in the axial direction, so that one of the first switching gear S1 and the second switching gear S2 is connected to and disconnected from the gear 561. Can be switched.
- the second shelf structure 570 includes either the first input shaft 10 or the auxiliary shaft 30 and the output shaft 40. This is for selectively connecting and disconnecting, and comprises a gear 571, a third switching gear S3, a fourth switching gear S4, and a second sleeve 572.
- the gear 571 is fixed to the output shaft 40.
- the third switching gear S3 is provided such that it can rotate relative to the output shaft 40 and cannot rotate relative to the gear 541.
- the fourth switching gear S4 is provided so as not to rotate relative to the first input shaft 10.
- the second sleeve 572 is a cylindrical member disposed on the outer peripheral side of the gear 571, and the inner peripheral side thereof meshes with the gear 571. The second sleeve 5 72 can be moved relative to the output shaft 40 in the axial direction, so that the connection and release of either the third switching gear S3 or the fourth switching gear S4 and the gear 571 can be switched. It is.
- the third cutting mechanism 580 is for selectively connecting and disconnecting the first input shaft 10 and the countershaft 30, and includes a gear 581, a fifth switching gear S5, a third sleeve 582, and the like. It consists of The gear 581 is fixed to the first input shaft 10. The fifth switching gear S5 is provided such that it can rotate relative to the first input shaft 10 and cannot rotate relative to the gear 551.
- the third sleeve 582 is a cylindrical member disposed on the outer peripheral side of the gear 581, and the inner peripheral side thereof meshes with the gear 581. The third sleeve 582 is movable relative to the first input shaft 10 in the axial direction, so that the connection between the fifth switching gear S5 and the gear 581 can be switched.
- the reduction gear ratio is generally the number of teeth on the driven side gear divided by the number of teeth on the driving side gear.
- each gear pair is switched between the driven side and the driving side.
- the gears on the first input shaft 10 and the second input shaft 20 side are assumed to be drive gears.
- the fourth gear pair 140 the drive side and the driven side are not interchanged, so the gear on the output shaft 40 side is the driven side gear.
- the reduction ratio of the first to fifth gear pairs is, for example,
- the transmission 2 can surely achieve an eight-speed shift. Specifically, it is only necessary to satisfy the following conditions: 0; 2> 0; 5> 0; 1> 0;
- FIG. 10 (b) is a schematic diagram of the torque transmission path of the transmission according to the fifth embodiment of the present invention, and FIG. And the reduction ratio.
- the dotted line indicates each axis
- the solid line indicates the torque transmission path at each gear stage.
- the clutch to be operated is indicated by “C 1” or “C 2”.
- the clutches and the switching gears connected at each gear stage are indicated by “ ⁇ ”, and the switching gears connected in preparation for upshifting and downshifting are indicated by “( ⁇ )”.
- the right side of FIG. 11 shows the reduction ratio of the entire transmission device 2, the step of the reduction ratio of each shift stage, and the entire range.
- the second clutch C2 is disconnected and the first clutch C1 is connected.
- the connection of the fourth switching gear S4 in the second Kiriura structure 570 is maintained.
- the torque input to the first input shaft 10 via the first clutch C1 is transmitted to the output shaft 40 via the second Kiriura structure 570, and The vehicle runs at the fifth speed.
- the second clutch C2 connection is released, and the first switching gear S1 of the first switching mechanism 560 and the fourth switching gear S4 of the second switching mechanism 570 are disengaged. Each is connected. Thereafter, the second clutch C2 is engaged again.
- the torque input to the second input shaft 20 via the second clutch C2 is transmitted via the first gear pair 510, the countershaft 30, and the second gear pair 520. Is transmitted to the output shaft 40, and the vehicle travels at the seventh speed.
- the speed change device 2 in this embodiment can further provide one shift speed (first forward speed 1 ′) between the first speed and the second speed in addition to the above seventh forward speed.
- first forward speed 1 ′ first forward speed
- the third switching gear S3 of the second switching mechanism 570 and the fifth switching gear S5 of the third switching mechanism 580 are connected, and the first clutch Connect C1 gradually.
- the torque input to the first input shaft 10 via the first clutch C1 becomes the fifth gear pair 550, the countershaft 30, and the fourth gear pair 540.
- this transmission 2 can realize a forward six-speed shift with only four gear pairs and two switching mechanisms. As a result, the transmission 2 can be reduced in axial dimension as compared with the prior art, and can be downsized. In addition, the overall size of the bag can be prevented from increasing. In addition, this transmission 2 reduces the forward first speed and the second speed as shown in FIG. The speed ratio step can be reduced. As a result, the transmission 2 can start by sliding the second clutch C2 at the second speed before the first clutch C1 finishes sliding at the first forward speed. As a result, in this transmission 2, the wearing of the facing can be reduced by sharing the load at the time of starting with the first and second clutches Cl and C2. In this gearbox 2, by selecting two starting speeds, it is possible to run with an emphasis on acceleration and fuel efficiency.
- the reduction ratio is exemplified, but the reduction ratio is not limited thereto. Other numerical values may be used as long as certain conditions are satisfied.
- the operation of the transmission 2 is described, but this does not limit the speed change operation of the transmission 2. Therefore, the transmission 2 can perform other speed change operations.
- each switching mechanism may be switched, or the fixed side and the relative rotation side of the gear may be switched.
- the above-described embodiment may adopt a conventional mechanism (such as a synchro mechanism) that does not specifically limit the type of the switching mechanism.
- the present invention can be used in a transmission, particularly a transmission corresponding to a double clutch device.
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Abstract
Description
Claims
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DE112005002697T DE112005002697T5 (de) | 2004-11-02 | 2005-10-28 | Getriebevorrichtung |
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JP2004-319208 | 2004-11-02 | ||
JP2004319208A JP2006132572A (ja) | 2004-11-02 | 2004-11-02 | 変速装置 |
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WO2009000414A3 (de) * | 2007-06-26 | 2009-03-19 | Daimler Ag | Zahnräderwechselgetriebe |
DE102007026405B4 (de) * | 2006-06-28 | 2015-02-05 | Ford Global Technologies, Llc | Mehrganggetriebe |
CN106884935A (zh) * | 2017-03-06 | 2017-06-23 | 同济大学 | 一种轻量化dct传动结构 |
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DE102007034553A1 (de) * | 2007-07-21 | 2009-01-22 | GM Global Technology Operations, Inc., Detroit | Stufengetriebe mit Doppelkupplung |
JP5147544B2 (ja) * | 2008-05-27 | 2013-02-20 | アイシン・エーアイ株式会社 | 変速機と変速機の制御方法 |
SE1350392A1 (sv) * | 2013-03-27 | 2014-09-28 | Scania Cv Ab | Växellåda, fordon med en sådan växellåda, förfarande för attstyra en sådan växellåda, datorprogram för att styra en sådan växellåda, samt en datorprogramprodukt innefattande programkod |
SE540700C2 (en) * | 2017-02-08 | 2018-10-16 | Scania Cv Ab | A gearbox for vehicles |
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JPS61274144A (ja) * | 1985-05-28 | 1986-12-04 | Mazda Motor Corp | 歯車式変速装置 |
JPS62204036A (ja) * | 1986-02-28 | 1987-09-08 | Hino Motors Ltd | 車輛の制動装置 |
JP2002340112A (ja) * | 2001-05-16 | 2002-11-27 | Aisin Seiki Co Ltd | 同期噛合い式歯車変速機 |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19921687C5 (de) | 1999-05-12 | 2016-06-09 | Borgwarner Inc. | Mehrfach-Kupplungssystem für ein Getriebe |
DE10360075A1 (de) | 2003-01-09 | 2004-07-22 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Parallelschaltgetriebe für Allradantrieb und Parallelschaltgetriebe für Quereinbau in ein Frontalantriebsfahrzeug |
-
2004
- 2004-11-02 JP JP2004319208A patent/JP2006132572A/ja active Pending
-
2005
- 2005-10-28 DE DE112005002697T patent/DE112005002697T5/de not_active Withdrawn
- 2005-10-28 WO PCT/JP2005/019884 patent/WO2006049096A1/ja active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61274144A (ja) * | 1985-05-28 | 1986-12-04 | Mazda Motor Corp | 歯車式変速装置 |
JPS62204036A (ja) * | 1986-02-28 | 1987-09-08 | Hino Motors Ltd | 車輛の制動装置 |
JP2002340112A (ja) * | 2001-05-16 | 2002-11-27 | Aisin Seiki Co Ltd | 同期噛合い式歯車変速機 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007026405B4 (de) * | 2006-06-28 | 2015-02-05 | Ford Global Technologies, Llc | Mehrganggetriebe |
WO2009000414A3 (de) * | 2007-06-26 | 2009-03-19 | Daimler Ag | Zahnräderwechselgetriebe |
CN106884935A (zh) * | 2017-03-06 | 2017-06-23 | 同济大学 | 一种轻量化dct传动结构 |
CN106884935B (zh) * | 2017-03-06 | 2019-04-02 | 同济大学 | 一种轻量化dct传动结构 |
Also Published As
Publication number | Publication date |
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DE112005002697T5 (de) | 2010-04-15 |
JP2006132572A (ja) | 2006-05-25 |
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