WO2010057456A1 - Fahrzeuggetriebe mit stufenlos veränderbarer übersetzung - Google Patents
Fahrzeuggetriebe mit stufenlos veränderbarer übersetzung Download PDFInfo
- Publication number
- WO2010057456A1 WO2010057456A1 PCT/DE2009/001486 DE2009001486W WO2010057456A1 WO 2010057456 A1 WO2010057456 A1 WO 2010057456A1 DE 2009001486 W DE2009001486 W DE 2009001486W WO 2010057456 A1 WO2010057456 A1 WO 2010057456A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- clutch
- vehicle transmission
- input shaft
- gear
- Prior art date
Links
Classifications
-
- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
-
- 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
- F16H57/00—General details of gearing
- F16H57/0018—Shaft assemblies for gearings
- F16H57/0031—Shaft assemblies for gearings with gearing elements rotatable supported on the shaft
-
- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H2037/023—CVT's provided with at least two forward and one reverse ratio in a serial arranged sub-transmission
-
- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H2037/025—CVT's in which the ratio coverage is used more than once to produce the overall transmission ratio coverage, e.g. by shift to end of range, then change ratio in sub-transmission and shift CVT through range once again
Definitions
- the present invention relates to a vehicle transmission with continuously variable transmission, with a arranged on a first shaft first conical disk pair and arranged on a second shaft second conical disk pair and arranged between the conical disk pairs belting and an input shaft and a rotatably mounted thereon, the input shaft optional can be brought into engagement with the first shaft or the second shaft and the output gear is rotatably engageable with the respective other shaft and between the input shaft and first and second shaft is provided in each case a multi-plate clutch for rotary power transmission and the output gear each by means of a dog clutch with the other Shaft can be brought into rotary engagement.
- the transmission is a so-called i 2 -red transmission, where "i” indicates the ratio of a variator of a belt pulley and the "2" indicates that the transmission range of the variator is passed twice.
- the transmission described above has already proven itself, it has the disadvantage of a relatively complex structure, since it has a total of five clutches, of which one clutch is assigned to the reverse drive range, however, four clutches are necessary for driving through the spread of the conical-pulley transmission twice , These clutches must be controlled accordingly, which leads to complicated switching operations.
- the four clutches are multi-plate clutches, each of which must be controlled by its own actuator.
- a transmission with a drive and output unit in which an output gear is rotatably mounted on a drive shaft, via which a can be introduced into the transmission gear.
- the driven gear is flanked on both sides by a coupling unit having a multi-plate clutch and a dog clutch, which can be selectively engaged with the driven gear, so that a torque transmission from the respective clutch unit can take place on the driven gear.
- the multi-plate clutches and jaw clutches are each driven by a separate actuator. It is in the nature of things that such a control is component-consuming and therefore expensive.
- the present invention is based on the object to simplify the generic vehicle transmission in terms of its structure and thus also the control of the individual rotational force transmitting components of the transmission.
- the invention provides a vehicle transmission with continuously variable transmission, with a arranged on a first shaft first conical disk pair and a second time arranged second conical disk pair and arranged between the conical disk pairs belt and an input shaft with a rotatably mounted thereon driven gear, wherein the input shaft optionally with the first shaft or the second shaft can be brought into rotary engagement and the output gear with the respective other shaft is rotatably engageable and between the input shaft and first and second shaft is provided in each case a multi-plate clutch for rotary power transmission and the output gear each by means of a dog clutch with the other shaft in Dreheeingriff can be brought, wherein the first multi-plate clutch and the first dog clutch by means of a first hydraulically operated device and the second multi-plate clutch and the second dog clutch by means of a second hydraulically operated device can be actuated.
- the vehicle transmission according to the invention therefore has a much simpler operation of the multi-plate clutches and jaw clutches, since in each case a multi-plate clutch and a dog clutch are combined to form a coupling unit which can be actuated by a hydraulically operated device.
- a hydraulically operated device For actuating the four clutches provided for passing through the forward driving range twice, therefore, only two hydraulically operated devices are required in the vehicle transmission according to the invention.
- the two hydraulically operated devices can be acted upon by pressurized fluid by means of two fluid lines extending coaxially along the input shaft.
- the pressurized fluid can be applied by means of two rotary inlets arranged in fluid communication with the input shaft. It can therefore be fed or discharged through the two rotary inlets pressurized fluid to the two devices or the pressure fluid present in the two devices and the fluid lines via the two rotary inlets are pressurized or brought about by the pressurization pressure in the two hydraulically operated devices and the Fluid lines are reduced via the rotary inlets.
- the two rotary inlets therefore only have to be connected fluidically via a fluid line or the like to a device which ensures the pressure buildup and the pressure reduction in the hydraulically operated devices.
- a pressure chamber which can act on a member for closing the multi-plate clutch against a spring means axially displaceable relative to the input shaft.
- the pressure build-up in the pressure chamber can provide an axial displacement of the component and the component close the multi-plate clutch for torque transmission. If the pressure in the pressure chamber is reduced, the spring device ensures an axial displacement of the component relative to the input shaft and thus an interruption of the torque transmission via the previously closed multi-plate clutch.
- the previously described component for closing the multi-plate clutch may be provided with an engagement portion and the engagement portion are brought to the output gear in a releasable rotationally positive form-fitting engagement and biased the engagement portion by means of a spring device in the direction of the driven wheel - A - to be.
- this means that the component is in a form-locking engagement with the output gear in a state of the pressure chamber that is not supplied with or with little pressure and can rotate together with the output gear.
- the spring device is supported against a gear which is rotatably arranged between the multi-plate clutch and the spring device on the input shaft.
- This gear can be in a rotationally fixed engagement with the multi-plate clutch, for example via an undercut axial toothing or quite simply via a welded joint, so that when the multi-plate clutch is closed, a torque transmission takes place on the gear and from this a torque transmission to one on the first or second shaft rotatably arranged gear can take place.
- the axial displacement of the component in the direction of action for closing the multi-plate clutch for opening the engagement position between the component and the driven wheel leads. Since the respective other multi-plate clutch is in the open state, the jaw clutch of this other multi-plate clutch is in positive engagement with the output gear, so that a corresponding torque transmission can take place from the arranged between the other multi-plate clutch and the dog clutch gear on the output gear.
- the gear is arranged in the axial direction of the input shaft between the component and the multi-plate clutch.
- the gearwheel has recesses in the axial longitudinal direction which are penetrated by jaws extending away from the component in the axial direction, which claws are designed to act on lamellae of the multi-disc clutch.
- the component is thus axially displaceable over the pressure chamber relative to the gear and the multi-plate clutch on the input shaft and the jaws can act on the slats of the multi-plate clutch to close the multi-plate clutch. If the pressure in the pressure chamber is reduced, then the spring device ensures an axial displacement of the component and thus its ner claws away from the slats of the multi-plate clutch and thus to an opening of the multi-plate clutch.
- the invention also provides a clutch arranged for transmitting rotational power from the second shaft to a turning step arranged in rotary engagement with the driven wheel. If this clutch is closed, a torque transmission takes place from the second shaft to the turning stage, which is in rotary engagement with the driven wheel. This driving position corresponds to the reverse position of the vehicle transmission according to the invention.
- Fig. 1 is a schematic representation of the structure of an embodiment of the vehicle transmission according to the invention and a matrix of the positions of provided in the vehicle transmission clutches;
- FIG. 2-4 representations of various driving ranges of the vehicle transmission according to the present invention.
- Fig. 5 is a perspective schematic representation of an embodiment of the vehicle transmission according to the invention.
- Fig. 6 is an exploded perspective view of a coupling unit
- FIG. 7 shows a partially sectioned representation of a drive and output unit of the vehicle transmission according to the invention in a neutral position
- FIG. 9 is a view similar to that of Figure 8 with the drive and Abtriebsein unit in the driving range "HIGH”.
- 10 is a view similar to that of FIG. 7 and FIG. 8 with the drive and output unit in the reverse drive range.
- FIG. 1 of the drawing shows a schematic representation of an embodiment of the vehicle transmission 1 according to the invention.
- the vehicle transmission 18 has a first conical disk pair 9 arranged on a first shaft 15 and a second conical disk pair 8 arranged on a second shaft 16. Between the two conical disk pairs 8, 9, a belt 17 is arranged in the form of, for example, a link chain.
- a drive torque originating from a drive motor not shown in detail can be introduced into the vehicle transmission 18.
- a gear 4 is rotatably arranged, via which a torque in a rotationally fixed to the first shaft 15 arranged gear 3 can be initiated.
- a gear 1 is rotatably arranged, via which a torque from the input shaft 11 to a second shaft 16 rotatably mounted gear 2 can be initiated.
- a driven gear 7 is rotatably mounted on the input shaft 11 and serves the torque output from the vehicle transmission 18 to a gear set shown in Fig. 5 of the drawing 10,13, 14, 14 ', which may be part of a non-illustrated drive train of a vehicle.
- a gear 5 is rotatably arranged, which can be coupled via a reverse clutch KR in the torque transmission.
- the gear 5 is engaged with a turning stage 6 and can transmit a torque from the second shaft 16 to the driven gear 7.
- the vehicle transmission 18 according to the invention is in the reverse position.
- the input shaft 11 is supplemented by the gears 1, 4, 7 and the clutches K1, K2, K3 and K4 to a drive and output unit 19.
- the vehicle transmission 18 can assume four switching positions or driving positions.
- the first driving position designated “R”
- the reverse clutch KR and the clutch K1 are closed.
- the neutral position “N” all clutches are open, in the driving position “LOW” the clutches K4 and K2 are closed and in the driving position "HIGH” the clutches K1 and K3 are closed.
- FIGS. 2, 3 and 4 of the drawing show the respective driving positions of the vehicle transmission 18 according to the invention.
- Fig. 2 shows the driving position "LOW", in which the power flow from the input shaft 11 via the closed clutch K4, the gear 1 takes place to the gear 2, from the second shaft 16 via the second cone pulley 8 to the belt 17, from there to first conical disk pair 9 and the gear 3 takes place and from gear 3 to the gear 4 and the closed clutch K2 to the output gear.
- Fig. 4 of the drawing shows the reverse position "Rev" of the vehicle transmission 18 of the invention.
- the registered in the input shaft 11 torque is transmitted to the gear 4 via the closed clutch K1, from there to the gear 2 and the first shaft 16.
- the rotational force is transmitted to the belt 17 and from there to the second cone pulley pair 8 and the second shaft 16.
- Fig. 5 of the drawing shows a perspective view of an executed vehicle transmission 18 according to the present invention.
- a multi-plate clutch K1 is rotatably fixed via a in Fig. 6 of the drawing apparent key 40.
- FIG. 6 of the drawing shows the respective structure of the multi-plate clutches K1 and K4.
- An axially slidable on the input shaft 11 claw ring part 31 has jaws 42, the recesses 41 of the gear 1 can prevail and 35 via a clutch outer ring 35 steel discs and blades 37 act so that between the steel discs 36 and the blades 37, a rotational force transmission takes place.
- the fins 37 have an internal toothing, which are in engagement with an external toothing of an inner coupling ring 39, which is fixed in a rotationally fixed manner via the key 40 on the input shaft 11.
- the structure of the clutch K1 corresponds to the structure of the clutch K4 explained with reference to FIG. 6 with the difference that instead of the gear 1, which is rotatably mounted on the input shaft 11 via a bearing 34, the gear 4 shown in FIG. 5 is provided is.
- Fig. 7 of the drawing shows the structure of the drive and output unit 19.
- the multi-plate clutch K1 rotatably disposed, which can be closed via the jaw ring member 31.
- the gear 4 is welded to the clutch outer ring 35, so that the rotational movement of the clutch outer ring 35 transmits to the gear 4 when the multi-plate clutch K1 is closed.
- a plate spring 32 biases the jaw ring part 31 in the direction of the output gear 7, and the claw ring part 31 has a toothing 43, which is in engagement with an internal gear formed on the output gear 7 and thus forms a first dog clutch K2 together with the internal toothing.
- the output gear 7 has a second internal toothing, which forms a second dog clutch K3 with a toothing 43 of the second jaw ring part 31.
- the clutch outer ring 35 of the second multi-disc clutch K4 can be acted upon to close this multi-disc clutch.
- the second plate spring 32 biases the claw ring part 31 in the direction of the drive wheel 7, so that the toothing 43 of the claw ring part 31 is in engagement with the toothing of the driven wheel 7.
- the input shaft 11 has two coaxial with each other arranged fluid lines 56, 57, which are separated by a provided with a seal pipe 55 from each other. Via the fluid line 56, pressure fluid can be fed into a pressure chamber 58. Similarly, pressure fluid can be fed into a pressure space 59 via the fluid line 57.
- FIG. 7 shows the position of the drive and output unit 19 in the neutral position of the vehicle transmission 18 according to the invention.
- two rotary inlets can be arranged, via which pressure fluid can be introduced into the fluid lines 56, 57.
- Fig. 8 shows the position of the drive and output unit 19 in the driving range "LOW".
- pressure is built up in the fluid line 57.
- This pressure build-up in the pressure chamber 59 ensures an axial displacement of the claw ring part 31 and thus for closing the multi-plate clutch K4.
- the rotational movement of the multi-plate clutch K4 is transmitted to the gear 1.
- the rotational force is transmitted to the gear 4 and from there via the closed dog clutch K2 on the output gear. 7
- Fig. 9 of the drawing shows the position of the drive and output unit 19 in the driving range "HIGH".
- the pressurization of the pressure chamber 59 is reduced via the fluid line 57 and the right in the plane of plate spring 32 displaces the associated claw part 31 in the left direction, so that on the one hand the multi-plate clutch K4 is opened and on the other hand, the dog clutch K3 is closed.
- the output gear 7 is in a rotational force transmitting engagement with the gear 1, so that adjusts the illustrated together with Fig. 3 power transmission path in the vehicle transmission 18 according to the invention.
- Fig. 10 of the drawing finally shows the position of the drive and output unit 19 in the driving range reverse drive of the vehicle transmission 18.
- the dog clutches K2 and K3 are opened by simultaneous pressurization of the pressure chambers 58, 59 and closed the multi-plate clutch K1 for torque transmission.
- the reversing clutch KR is closed for torque transmission to the turning stage 6.
- the vehicle transmission according to the invention is now characterized by the fact that a twofold traversing the spread of the conical pulley belt transmission with only two hydraulically operated devices is possible, having two pressure chambers, which are fed via two rotary inlets on the input shaft of the vehicle transmission with pressurized fluid.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112009002537T DE112009002537A5 (de) | 2008-11-19 | 2009-10-22 | Fahrzeuggetriebe mit stufenlos veränderbarer Übersetzung |
JP2011536735A JP2012509444A (ja) | 2008-11-19 | 2009-10-22 | 無段階に可変の変速比を有する車両変速機 |
US13/106,024 US8235848B2 (en) | 2008-11-19 | 2011-05-12 | Vehicle transmission having continuously variable transmission ratio |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008058081 | 2008-11-19 | ||
DE102008058081.3 | 2008-11-19 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/106,024 Continuation US8235848B2 (en) | 2008-11-19 | 2011-05-12 | Vehicle transmission having continuously variable transmission ratio |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010057456A1 true WO2010057456A1 (de) | 2010-05-27 |
Family
ID=41395946
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2009/001486 WO2010057456A1 (de) | 2008-11-19 | 2009-10-22 | Fahrzeuggetriebe mit stufenlos veränderbarer übersetzung |
Country Status (4)
Country | Link |
---|---|
US (1) | US8235848B2 (de) |
JP (1) | JP2012509444A (de) |
DE (2) | DE112009002537A5 (de) |
WO (1) | WO2010057456A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8771116B2 (en) * | 2008-06-17 | 2014-07-08 | Schaeffler Technologies Gmbh & Co. Kg | Vehicle transmission having continuously variable gear ratios |
US9169901B2 (en) * | 2012-09-14 | 2015-10-27 | Ford Global Technologies, Llc | Multiple speed transmission with integrated low range |
US9958044B2 (en) * | 2013-08-09 | 2018-05-01 | Honda Motor Co., Ltd. | Power transmission switching mechanism and transmission |
US9222560B2 (en) * | 2014-04-21 | 2015-12-29 | Gm Global Technology Operations, Llc | Two mode continuously variable transmission |
CN106015527A (zh) * | 2016-07-06 | 2016-10-12 | 洛阳天迈传动科技有限公司 | 一种变速器模块化分装及加工结构 |
JP6729615B2 (ja) * | 2018-03-02 | 2020-07-22 | トヨタ自動車株式会社 | 車両の制御装置 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE879350C (de) * | 1951-04-28 | 1953-06-11 | Patentverwertung W Reimers G M | Stufenlos regelbares Getriebe |
DE4119291A1 (de) * | 1991-06-12 | 1992-12-17 | Hoehn Bernd Robert Prof Dr Ing | Stufenloses getriebe |
US20090017959A1 (en) * | 2007-06-21 | 2009-01-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Vehicle transmission with continuously variable transmission ratio |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4630504A (en) * | 1985-08-22 | 1986-12-23 | Borg-Warner Corporation | Dual-pass continuously variable transmission |
JPS62228749A (ja) * | 1986-03-27 | 1987-10-07 | Mitsuboshi Belting Ltd | 動力伝動装置 |
US5031481A (en) * | 1989-12-08 | 1991-07-16 | Borg-Warner Automotive, Inc. | Electro-hydraulic control system for a dual-pass continuously variable transmission |
US5407394A (en) * | 1993-05-05 | 1995-04-18 | Borg-Warner Automotive, Inc. | Guide for an adjustable pulley in a continuously variable transmission |
JP5408627B2 (ja) * | 2007-06-21 | 2014-02-05 | シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト | Cvtバリエータを備えた動力分割式のオートマチックトランスミッション |
-
2009
- 2009-10-22 WO PCT/DE2009/001486 patent/WO2010057456A1/de active Application Filing
- 2009-10-22 DE DE112009002537T patent/DE112009002537A5/de not_active Withdrawn
- 2009-10-22 JP JP2011536735A patent/JP2012509444A/ja not_active Withdrawn
- 2009-10-22 DE DE102009050350A patent/DE102009050350A1/de not_active Withdrawn
-
2011
- 2011-05-12 US US13/106,024 patent/US8235848B2/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE879350C (de) * | 1951-04-28 | 1953-06-11 | Patentverwertung W Reimers G M | Stufenlos regelbares Getriebe |
DE4119291A1 (de) * | 1991-06-12 | 1992-12-17 | Hoehn Bernd Robert Prof Dr Ing | Stufenloses getriebe |
US20090017959A1 (en) * | 2007-06-21 | 2009-01-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Vehicle transmission with continuously variable transmission ratio |
Also Published As
Publication number | Publication date |
---|---|
US8235848B2 (en) | 2012-08-07 |
DE112009002537A5 (de) | 2013-10-10 |
DE102009050350A1 (de) | 2010-05-20 |
JP2012509444A (ja) | 2012-04-19 |
US20110244998A1 (en) | 2011-10-06 |
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