WO1995031655A1 - Unter last schaltbares, mehrgängiges wendegetriebe - Google Patents
Unter last schaltbares, mehrgängiges wendegetriebe Download PDFInfo
- Publication number
- WO1995031655A1 WO1995031655A1 PCT/EP1995/001748 EP9501748W WO9531655A1 WO 1995031655 A1 WO1995031655 A1 WO 1995031655A1 EP 9501748 W EP9501748 W EP 9501748W WO 9531655 A1 WO9531655 A1 WO 9531655A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- gear
- idler
- clutch
- countershafts
- fixed
- 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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0935—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple countershafts comprising only one idle gear and one gear fixed to the countershaft
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19233—Plurality of counter shafts
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19242—Combined gear and clutch
Definitions
- the invention relates to a multi-speed reversing gear which can be shifted under load, with an input shaft and countershafts, a reversing set and shifting clutches with idler gears arranged on the countershafts, which can be connected non-rotatably to one of the countershafts for gear and directional switching, and an output gear set with one Fixed gear on an output shaft.
- Gearboxes are used in the construction machines in use today, which can be divided into two groups.
- a group is characterized by the fact that a hydrostatic drive unit is connected upstream of the powershift transmission.
- the speed and torque matching of the upstream group is implemented via hydraulic or electro-hydraulic controls.
- the majority of the transmissions used belong to the further group of powershift transmissions with an upstream hydrodynamic torque converter.
- this drive unit With the help of this drive unit, a stepless and automatic increase in torque with increasing working resistance of the motor vehicle, for example a construction machine, can be achieved.
- gear drive torques can be generated which correspond approximately to three times the value of the engine torque. This is important because, unlike in the case of a car, the gearbox or converter is used.
- the bucket In the case of a wheel loader, for example, the bucket is pressed into the soil to be picked up. The filling is broken loose and raised. The vehicle is reversed for loading, the bucket is further raised and unloaded.
- the torque conversion is a great advantage especially at low speeds and large speed differences between the input and output.
- the converter can be supplemented with a converter lock-up clutch. With the aid of this clutch, considerable consumption savings can be achieved in the range of higher speeds within the gears.
- the power flow in the individual gears is produced by a combination of hydraulically switchable clutches.
- these clutches must be switchable for reversing under load and therefore take up a lot of energy.
- the design of the housing or the arrangement of the shafts of the gear unit must be specifically adapted to an application.
- Typical applications for a reversing gearbox are use in dumpers, wheel loaders, backhoe loaders and stackers, but also in vehicles that are operated on the road, for example in crane vehicles.
- a certain axis offset between the input and output shaft of the gearbox is required. Long center distances must be observed, for example, if the diffraction angles of cardan shafts have to be kept small. In this case, the reversing gear takes on an additional function as a transfer case.
- the reversing gearbox has only one output shaft. Because of the spatial conditions, a small center distance is required.
- At least one power take-off is required, for example for the hydraulics of the machine.
- a reversing gear which is characterized by a small axial length.
- a friction clutch is arranged between the loose and fixed wheels.
- the structural design of the friction clutches, in particular the arrangement of the disk packs, the mounting of the idler gears on the countershafts and also the indirect mounting of the countershaft itself on the idler gear side are relatively complex.
- a reversing gear is known from DE-A 25 35 700, in which the friction clutches are designed as double clutches.
- a relatively high number of gears can be achieved with this transmission, but a larger installation space is required in the axial direction, since up to four gearwheels and a double clutch must be accommodated on a countershaft.
- the object of the present invention is to improve a power shiftable reversing gear with a small axial length with regard to the design of the friction clutches and the bearing of the countershafts.
- the object on which the invention is based is achieved in that the turning set is formed from a fixed gear of the input shaft and idler gears mounted on the countershafts, that fixed gears of the countershaft and an idler gear arranged on the output shaft form a drive wheel chain and that Output gear set is formed from a fixed gear of the output shaft and an idler gear mounted on the countershaft.
- the proposed reversing gear is characterized by a number of advantages.
- the idler gears are arranged so that they do not rotate at a relative speed with respect to their countershafts under load.
- idler gears are also not used as idler gears, so that they are not subjected to the high load from two tooth meshings.
- the rolling bearings of which at least one is arranged below a disk set of a clutch, can therefore be dimensioned small.
- the idler gears only run under load if the relative speed between this idler gear and its countershaft is zero when the clutch is closed. If an intermediate wheel is required, this is formed by a fixed wheel.
- the gearbox is characterized by a compact design. A total of four roller bearings are provided for the bearing of a countershaft, two of which are comparatively small. In addition to a slight deflection of the countershaft, this saves costs.
- the gearwheel assigned to the clutch for the first gear is an idler gear.
- this idler gear rotates at a relatively high speed, it allows an advantageous assignment of the clutch. It meshes with a fixed gear on the output shaft.
- This fixed gear is also helically toothed. For its support is a large bearing base available, so that occurring tilting forces are easily absorbed.
- the gearwheel which can be connected in a rotationally fixed manner to the output shaft via a clutch for the second gear, is also designed as an idler gear.
- a particularly favorable arrangement of the clutches is given when the inner plates of the plate packs are connected to the idler gears, while the outer plates of the plate packs are accommodated in clutch housings which are part of the countershafts.
- the gears, which rotate at relatively high speeds, are thus designed as idler gears. They are not non-rotatably connected to the piston chamber of the hydraulic actuation and to the outer disk carrier. A high switching quality can be achieved with this arrangement. The risk of lamella wobbling is low. To be as large as possible
- each idler gear is mounted on its countershaft via two roller bearings.
- a rolling bearing is arranged below and approximately in the middle of a disk set, while the further rolling bearing lies approximately in the vertical plane of the tooth engagement.
- Piston slidably mounted in an annular space of the clutch housing.
- the clutch housing is rotatably connected to the respective countershaft.
- the piston is sealingly guided in the annular space via seals, for example O-rings.
- seals for example O-rings.
- Figure 1 is a two-speed reversing gear, shown as a gear scheme.
- FIG. 2 shows a longitudinal section through a clutch of the reversing gear according to FIG. 1.
- FIG. 1 shows a transmission diagram of a power shiftable reversing transmission 1. It is a two-speed reversing gear, which can be preceded by a hydrodynamic torque converter 2, which will preferably be the case with heavy construction vehicles.
- a pump wheel 3 of the hydrodynamic torque converter is in drive connection with a schematically indicated motor 4.
- a gear 6 is arranged on a driven shaft 5 of the pump wheel 3 in a rotationally fixed manner. This is in meshing drive connection with a gear 8 which is also arranged in a rotationally fixed manner on a countershaft 7, as is indicated by the dashed connection 9.
- the gears 6 and 8 and the countershaft 7 form a power take-off with which, for example, an oil pump or a PTO shaft can be operated depending on the engine speed.
- the turbine wheel 10 of the hydrodynamic torque converter is non-rotatably connected to an input shaft 11.
- a fixed gear 12 is arranged at the right end of the continuous input shaft 11 in the drawing (for reasons of clarity, the input shaft 11 is shown interrupted in the drawing).
- Fixed gear 12 is in meshing drive connection with idler gears 13 and 14.
- the idler gears 13 and 14 are each mounted on a countershaft 15 and 16.
- the idler gear 13 can be connected in a rotationally fixed manner to the countershaft 15 or the countershaft 16 via a clutch 17 and the idler gear 14.
- a turning set 19 is formed by the fixed gear 12 and the idler gears 13 and 14, which can be connected non-rotatably to the countershafts 15 and 16, respectively.
- the turning set 19, in conjunction with the shift clutches 17 and 18, allows the direction of rotation of an output shaft 20 of the reversing gear to be reversed. For this reason the clutches 17 and 18 are also referred to as directional clutches.
- the hydrodynamic torque converter 2 is completed by a stator 33 which is supported by a freewheel.
- the reverse gear of the countershaft type has, in addition to the countershafts 15 and 16 and the output shaft 20, a further countershaft 21.
- an idler gear 22 is rotatably mounted, which can be connected to the countershaft 21 in a rotationally fixed manner via a clutch 23.
- the clutch 23 is the gear clutch for the first gear.
- the idler gear 22 is in constant mesh with a fixed gear 24 of the output shaft 20 of the reversing gear 1.
- an idler gear 25 is rotatably mounted on the output shaft 20 and can be coupled to the output shaft 20 in a rotationally fixed manner by means of a clutch 26.
- the clutch 26 forms the gear shift clutch for the second gear.
- the arrangement is completed by fixed gears 27, 28 and 29.
- the fixed gear 27 is non-rotatably connected to the countershaft 15, the fixed gear 28 to the countershaft 16 and the fixed gear 29 to the countershaft 21.
- the fixed gear 29 is in meshing connection with the idler gear 25.
- the fixed gears 27, 28 and 29 and the idler gear 25 form a drive wheel chain 30.
- the idler gear 22 and the fixed gear 24 form an output gear set 31.
- the power flows via the countershaft 21 and the idler gear 22 (with the clutch 23 closed) to the fixed gear 24 of the output shaft 20.
- One of the clutches 17 or 18 is closed in the forward or reverse direction.
- the gear shift clutch for the second gear (shift clutch 26) is open.
- the transmission diagram explained above shows that on each of the countershafts 15, 16, 20 and 21 a single clutch 17 or 18 or 23 or 26, a single idler gear 13, 14, 22 and 25 and a single fixed gear 27, 28 , 29 and 24 is arranged.
- the limited number of components results in a very short axial length of each of the countershafts 15, 16, 20 and 21.
- the countershafts 15, 16, 20 and 21 are each supported by two roller bearings 32.
- the clutches 17, 18, 23 and 26 are arranged between the respective idler and fixed wheels in a common vertical plane. This measure also contributes significantly to the short axial length of the reversing gear.
- the idler and fixed gears 13, 14, 22, 25 and 27, 28 and 29 are helically toothed. Gears with large helix angles are preferably used. Due to the axially short design of the countershafts, there are no large bending loads.
- FIG. 2 shows a detail of the reversing gear 1 according to FIG. 1.
- 1 shows the clutch 17 located at the top in the transmission diagram according to FIG. 1 (directional clutch forward).
- the fixed gear 12 of the input shaft 11 can be seen in part.
- the countershaft 15 is mounted in a gear housing 34 via the roller bearings 32, In the area of the impeller 3, which is only indicated, the gear housing 34 is closed by a cover 35.
- the idler gear 13 is rotatably mounted on the countershaft 15 via two roller bearings 36 and 37. Both bearings, but especially the roller bearing 36, are of small dimensions.
- the roller bearing 36 lies below and in the center of a disk set 39.
- the roller bearing 37 supports the idler gear 13 in the vertical plane in which its toothing lies.
- a clutch housing 38 of the clutch 17 is part of the countershaft 15 and carrier of outer plates of a plate pack 39. The inner plates of this
- Disc packs are carried by a disc carrier of the ring gear 13.
- the plate pack 39 can be acted upon in the closing direction in a manner known per se by a hydraulically actuated piston 40.
- a channel 42 leads to an annular space 41 for supplying oil for actuation.
- An inner and an outer O-ring 44 and 45 are used to seal the piston 40 against the clutch housing 38.
- the drive wheel chain 30 is formed from the fixed wheels 27, 28 and 29. That the gang Clutch for the second gear (clutch 26) assigned gear is designed as an idler gear 25 which is in engagement with the fixed gear 29.
- the idler gear 22 assigned to the gear shift clutch for the first gear (clutch 23) meshes with the large fixed gear 24 of the output shaft 20.
- the idler gears 13 and 14 and 22 and 25 are advantageously arranged in such a way that they do not rotate under load at a relative speed with respect to the countershafts on which they are mounted. These loose wheels are also not used as idler gears, so that they are not subjected to the high load of two tooth meshes. Therefore, the rolling bearings, at least one of which is under the disk pack of the associated one
- Clutch is arranged to be small. These idler gears only run under load when the relative speed between one of the idler gears and the associated countershaft is zero. This is the case when the associated clutch is closed. If an intermediate wheel is required, this is formed by a fixed wheel, as is the case, for example, with fixed wheel 29 and shifted second gear.
- the advantage of smaller-sized rolling bearings for supporting the loose wheels has further advantageous effects in that the countershaft rotating under load can be supported in the gear housing 34 via the rolling bearings 32. The installation space is not limited here. Overall, this means a compact design, cost savings on two of the four bearings required for a countershaft and less deflection of the countershaft.
- the drive wheel chain 30 is coupled to the turbine wheel 10 of the hydrodynamic converter 2 and is consequently accelerated or accelerated together with the turbine wheel. hesitates. In the case of a reversing circuit, the acceleration of the drive wheel chain 30 with the turbine wheel is very strong.
- the clutch housing (for example clutch housing 38 of the clutch 17) including the pistons (for example 40 of the clutch 17) should not be affected by this acceleration for the following reasons: the acceleration of the piston due to the friction of the O-rings 44 and 45, an additional driving profile is saved, but there is a risk that the O-rings wear out relatively quickly, since the piston rotates in the clutch housing until it accelerates or brakes to the new direction of rotation or speed of the clutch housing is.
- an arrangement is proposed as follows:
- the gearwheels connected to the turbine are mounted as idler gears on the countershafts.
- the above-explained simple construction principle of driving the piston via the two O-rings can be realized without having to accept the disadvantages described here.
- the total mass of the strongly accelerated components is comparatively small, whereby the occurrence of large resulting forces is avoided.
- the step change in transmission between the first and second gears is realized by the driven gear set 31.
- the idler gear 22 assigned to the gear shift clutch for the first gear rotates at a relatively high speed when the second gear is engaged (clutch 26 closed).
- the choice of this gear of the driven gear set as an idler gear has the advantage that it is not connected to the clutch housing (piston chamber) of the clutch 23 and thus to the carriers of the outer plates of the plate pack. As a result, these components are not with the high Speed of idler gear 22 be ⁇ with second gear engaged.
- the pressure of the respective piston on the disk pack is determined by the hydraulic pressure in the annular space. In order to obtain a slow build-up of the torque, this pressure is precisely controlled. Due to the rotation of the pressure oil in the piston annulus, this controlled pressure is superimposed by the rotation pressure. In order to keep this unfavorable influence on the quality of the circuit small, the speed of the clutch housing should be kept as small as possible. In addition, the outer lamellae of the lamella package are more susceptible to lamellae than the associated inner lamellae. For this reason too, the speed of the clutch housing (as the carrier of the outer disks) should be low.
- Idler wheels trained. They are not non-rotatably connected to the clutch housing and thus to the respective annular space (piston space) and the corresponding carrier of the outer plates.
- the proposed reversing gearbox can meet the requirements placed on high shift quality. The risk of lamella wobble occurring is kept low.
- the output gear 20 is the fixed gear 24 in the output shaft 20.
- the arrangement, as it were, of the idler gear 25 and the fixed gear 24 of the output shaft 20 is not disadvantageous, as one might initially suspect, but is associated with the following advantages: With the relatively large diameter of the fixed gear 24, the tilting moments become resulting from the helical gearing selected because of the lower noise, large. With the selected wave-fixed design, the bearing base for the fixed gear 24 becomes large. These tilting moments can thus be supported very well. The connection of this fixed gear 24 to the output flange of the output shaft can be structurally simpler than would be the case with an idler gear. For these reasons, the clutch clutches 23 and 26, as described, are arranged crosswise.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
- Control Of Transmission Device (AREA)
- Soil Working Implements (AREA)
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1019960706386A KR100354184B1 (ko) | 1994-05-13 | 1995-05-09 | 동력변속가능한다단역전변속기 |
RU96123755A RU2144633C1 (ru) | 1994-05-13 | 1995-05-09 | Переключаемая при нагрузке многоступенчатая реверсивная передача |
BR9507870A BR9507870A (pt) | 1994-05-13 | 1995-05-09 | Mecanismo de inversão de marchas múltiplas acionável sob carga |
EP95919429A EP0759130B1 (de) | 1994-05-13 | 1995-05-09 | Unter last schaltbares, mehrgängiges wendegetriebe |
DE59503177T DE59503177D1 (de) | 1994-05-13 | 1995-05-09 | Unter last schaltbares, mehrgängiges wendegetriebe |
US08/737,263 US5743142A (en) | 1994-05-13 | 1995-05-09 | Multi-ratio power-shiftable reversing gear |
JP7529332A JPH10500196A (ja) | 1994-05-13 | 1995-05-09 | 負荷の下で切換可能な多段変速機 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4416929A DE4416929A1 (de) | 1994-05-13 | 1994-05-13 | Unter Last schaltbares, mehrgängiges Wendegetriebe |
DEP4416929.9 | 1994-05-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1995031655A1 true WO1995031655A1 (de) | 1995-11-23 |
Family
ID=6518077
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1995/001748 WO1995031655A1 (de) | 1994-05-13 | 1995-05-09 | Unter last schaltbares, mehrgängiges wendegetriebe |
Country Status (11)
Country | Link |
---|---|
US (1) | US5743142A (de) |
EP (1) | EP0759130B1 (de) |
JP (1) | JPH10500196A (de) |
KR (1) | KR100354184B1 (de) |
CN (1) | CN1147848A (de) |
AT (1) | ATE169728T1 (de) |
BR (1) | BR9507870A (de) |
DE (2) | DE4416929A1 (de) |
ES (1) | ES2122607T3 (de) |
RU (1) | RU2144633C1 (de) |
WO (1) | WO1995031655A1 (de) |
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CN100439754C (zh) * | 2004-01-21 | 2008-12-03 | 腓特烈斯港齿轮工厂股份公司 | 多挡变速器 |
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KR100503612B1 (ko) * | 1998-08-28 | 2006-08-30 | 두산인프라코어 주식회사 | 중장비용 변속기 |
DE10131329A1 (de) * | 2001-06-28 | 2003-01-09 | Zahnradfabrik Friedrichshafen | Lastschaltbares Wendegetriebe |
US6988426B2 (en) * | 2001-12-31 | 2006-01-24 | Caterpillar Inc. | Dual range countershaft transmission |
DE10201590A1 (de) * | 2002-01-17 | 2003-07-31 | Zahnradfabrik Friedrichshafen | Lastschaltgetriebe mit hydrodynamischem und optinalem mechanischen Leistungspfad |
DE10201837A1 (de) * | 2002-01-18 | 2003-07-31 | Zahnradfabrik Friedrichshafen | Lastschaltgetriebe mit hydrodynamischem und mechanischem Leistungspfad |
DE10330157A1 (de) * | 2003-07-04 | 2005-02-03 | Zf Friedrichshafen Ag | Lastschaltgetriebe für Baumaschinen, insbesondere für Baggerlader und Telehandler |
DE10330159A1 (de) * | 2003-07-04 | 2005-02-03 | Zf Friedrichshafen Ag | Lastschaltgetriebe für Baumaschinen, insbesondere für Baggerlader und Telehandler |
US7044014B2 (en) | 2004-05-25 | 2006-05-16 | Ford Global Technologies, Llc | Dual clutch automatic transaxle |
US7272986B2 (en) * | 2005-07-15 | 2007-09-25 | Ford Global Technologies, Llc | Dual input automatic transaxle |
US20060097006A1 (en) * | 2005-10-11 | 2006-05-11 | Erie County Plastics Corporation | Pour spout fitment with internal cut off |
CN101025217B (zh) * | 2006-02-20 | 2012-06-27 | 陕西法士特齿轮有限责任公司 | 多档组合式副箱三中间轴汽车变速器 |
CN101025218B (zh) * | 2006-02-23 | 2012-06-27 | 陕西法士特齿轮有限责任公司 | 多档组合式三中间轴汽车变速器 |
DE102010020856B4 (de) * | 2009-05-20 | 2016-12-01 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Siebengang-Doppelkupplungsgetriebe |
DE102010055643A1 (de) * | 2010-12-22 | 2012-06-28 | Volkswagen Ag | Automatisches, insbesondere automatisiertes Schaltgetriebe für ein Kraftfahrzeug |
US8522634B2 (en) * | 2011-01-31 | 2013-09-03 | Deere & Company | Powertrain comprising a three speed transmission |
CN103423385A (zh) * | 2013-08-02 | 2013-12-04 | 四川成都成工工程机械股份有限公司 | 一种矿用自卸车动力换挡变速箱 |
US20150158382A1 (en) | 2013-12-05 | 2015-06-11 | Avl Powertrain Engineering, Inc. | Two-speed transmission for electric vehicle |
US20170074393A1 (en) * | 2015-09-11 | 2017-03-16 | Nentor Marku | All Clutch Sequential (ACS) |
DE102016207299A1 (de) * | 2016-04-28 | 2017-11-02 | Zf Friedrichshafen Ag | Unter Last schaltbares mehrgängiges Wendegetriebe |
RU180492U1 (ru) * | 2018-02-02 | 2018-06-14 | Алексей Витальевич Амельченко | Коробка перемены передач |
RU181008U1 (ru) * | 2018-02-13 | 2018-07-03 | Алексей Витальевич Амельченко | Коробка перемены передач |
RU180285U1 (ru) * | 2018-03-13 | 2018-06-07 | Алексей Витальевич Амельченко | Коробка перемены передач |
RU187961U1 (ru) * | 2018-12-18 | 2019-03-26 | Алексей Витальевич Амельченко | Коробка перемены передач |
RU197813U1 (ru) * | 2020-02-10 | 2020-05-29 | Алексей Витальевич Амельченко | Коробка перемены передач |
CN111609096B (zh) * | 2020-05-14 | 2021-05-25 | 江苏汇智高端工程机械创新中心有限公司 | 一种模块化设计变速箱及挡位实现方法 |
CN111734793B (zh) * | 2020-06-22 | 2023-03-21 | 江苏汇智高端工程机械创新中心有限公司 | 一种多挡位动力换挡变速箱 |
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DE1129838B (de) * | 1960-04-23 | 1962-05-17 | Zahnradfabrik Friedrichshafen | In axialer Richtung geringe Baulaenge aufweisendes Zahnraederwechsel- und -wendegetriebe, insbesondere fuer Kraftfahrzeuge |
DE2535700A1 (de) * | 1975-08-09 | 1977-02-10 | Zahradfabrik Friechrichshafen | Unter last schaltbares mehrgaengiges wendegetriebe |
DE4242942A1 (de) * | 1992-12-18 | 1994-06-23 | Zahnradfabrik Friedrichshafen | Unter Last schaltbares, mehrgängiges Wendegetriebe |
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US4392391A (en) * | 1980-11-07 | 1983-07-12 | Cooper Industries, Inc. | Multispeed reversible power shift transmission |
US4549443A (en) * | 1983-12-07 | 1985-10-29 | Twin Disc, Incorporated | Multi-speed reversible transmission of countershaft construction |
US4726246A (en) * | 1986-10-01 | 1988-02-23 | Caterpillar Inc. | Countershaft transmission having two forward and two reverse speeds |
US5079965A (en) * | 1989-07-14 | 1992-01-14 | Zahnradfabrik Friedrichshafen Ag | Gearbox |
US5063793A (en) * | 1990-09-06 | 1991-11-12 | Deere & Company | Speed forward, 12 speed reverse powershift transmission |
US5249475A (en) * | 1992-08-31 | 1993-10-05 | Deere & Company | Eight- to sixteen-speed powershift transmission |
US5471892A (en) * | 1994-04-21 | 1995-12-05 | General Motors Corporation | Multi-speed parallel axis three countershafts and an output shaft power transmission |
US5557978A (en) * | 1995-03-07 | 1996-09-24 | Deere & Company | Countershaft power transmission |
-
1994
- 1994-05-13 DE DE4416929A patent/DE4416929A1/de not_active Withdrawn
-
1995
- 1995-05-09 BR BR9507870A patent/BR9507870A/pt not_active IP Right Cessation
- 1995-05-09 CN CN95192964A patent/CN1147848A/zh active Pending
- 1995-05-09 AT AT95919429T patent/ATE169728T1/de not_active IP Right Cessation
- 1995-05-09 US US08/737,263 patent/US5743142A/en not_active Expired - Lifetime
- 1995-05-09 KR KR1019960706386A patent/KR100354184B1/ko not_active IP Right Cessation
- 1995-05-09 ES ES95919429T patent/ES2122607T3/es not_active Expired - Lifetime
- 1995-05-09 EP EP95919429A patent/EP0759130B1/de not_active Expired - Lifetime
- 1995-05-09 RU RU96123755A patent/RU2144633C1/ru active
- 1995-05-09 JP JP7529332A patent/JPH10500196A/ja active Pending
- 1995-05-09 DE DE59503177T patent/DE59503177D1/de not_active Expired - Lifetime
- 1995-05-09 WO PCT/EP1995/001748 patent/WO1995031655A1/de active IP Right Grant
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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DE1129838B (de) * | 1960-04-23 | 1962-05-17 | Zahnradfabrik Friedrichshafen | In axialer Richtung geringe Baulaenge aufweisendes Zahnraederwechsel- und -wendegetriebe, insbesondere fuer Kraftfahrzeuge |
DE2535700A1 (de) * | 1975-08-09 | 1977-02-10 | Zahradfabrik Friechrichshafen | Unter last schaltbares mehrgaengiges wendegetriebe |
DE4242942A1 (de) * | 1992-12-18 | 1994-06-23 | Zahnradfabrik Friedrichshafen | Unter Last schaltbares, mehrgängiges Wendegetriebe |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN100439754C (zh) * | 2004-01-21 | 2008-12-03 | 腓特烈斯港齿轮工厂股份公司 | 多挡变速器 |
Also Published As
Publication number | Publication date |
---|---|
DE59503177D1 (de) | 1998-09-17 |
EP0759130A1 (de) | 1997-02-26 |
RU2144633C1 (ru) | 2000-01-20 |
JPH10500196A (ja) | 1998-01-06 |
DE4416929A1 (de) | 1995-11-16 |
KR100354184B1 (ko) | 2002-11-13 |
US5743142A (en) | 1998-04-28 |
KR970702972A (ko) | 1997-06-10 |
ATE169728T1 (de) | 1998-08-15 |
CN1147848A (zh) | 1997-04-16 |
BR9507870A (pt) | 1997-09-23 |
ES2122607T3 (es) | 1998-12-16 |
EP0759130B1 (de) | 1998-08-12 |
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