WO1991012442A1 - Wandler-wechselgetriebe, insbesondere für schlepper - Google Patents
Wandler-wechselgetriebe, insbesondere für schlepper Download PDFInfo
- Publication number
- WO1991012442A1 WO1991012442A1 PCT/EP1990/000248 EP9000248W WO9112442A1 WO 1991012442 A1 WO1991012442 A1 WO 1991012442A1 EP 9000248 W EP9000248 W EP 9000248W WO 9112442 A1 WO9112442 A1 WO 9112442A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- converter
- clutch
- change
- gearbox according
- clutches
- 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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H35/10—Arrangements or devices for absorbing overload or preventing damage by overload
Definitions
- Converter change gearbox especially for tractors
- the invention relates to a converter change transmission, in particular for tractors, comprising an input shaft connected to a drive door, an output shaft, and between the input shaft and output shaft: - a manual transmission with at least two switching stages, a converter, in particular a chain converter, for stepless change in ratio in the respective switching stage and at least one clutch for uncoupling the output shaft from the input shaft.
- Stepless converter transmissions have been known for a long time.
- chain converters egReimers chain converter or Van Dorne (DAF) chain converter with thrust link chain
- DAF Van Dorne
- the adjustment range of such transducers is relatively limited (eg 1: 5).
- the adjustment range required is often larger. For example, there is an adjustment range between 2.2 km / h for tractors. and 40 km / h required.
- the converter can be combined with a shift transmission with at least two shift stages to divide the required adjustment range into several reduced sub-ranges , the possible adjustment range of the converter. Since the proposed, in particular mechanically operating, transducers have no clutch function, a clutch for decoupling the output shaft from the input shaft must be provided The drive motor can be started when the output shaft is at rest and when the manual transmission is shifted during operation.
- converters in particular chain converters
- tugs with converter change gearboxes of the type mentioned at the outset have not yet appeared on the market, which may be due to the fact that these converters often become prematurely defective in harsh operating conditions.
- torque peaks which are about 5 times the engine torque can occur, for example, when the clutch is suddenly engaged ("let jump"). Since the converter slips, for example, at 4 times the engine torque, momentary slipping of the converter is unavoidable, which leads to damage to the converter after a short time.
- a clutch for example a clutch for the manual transmission
- the converter is immediately set in motion by the input shaft when the engine is started.
- the converter is not yet prepared for this, especially if the converter is to be supplied with oil pressure via a hydraulic system connected to the converter change gearbox, in order to ensure perfect functioning.
- This oil pressure may be necessary, for example, in order to press the conical chain wheel halves against one another and in this way to ensure a reliable, non-positive connection with the converter chain. Accordingly, if the oil pressure at the start of the drive engine is currently too low, there is a risk of the converter slipping.
- the invention has for its object a mechanically heavy-duty converter gearbox with large -3- Translation range, especially for a tractor, to be provided, which ensures reliable operation with a simple structure.
- a converter change gear of the type mentioned at the outset in that at least one clutch is provided on both sides of the converter in the power flow for uncoupling the converter from the input shaft and from the output shaft, and in that both clutches can be actuated simultaneously. Due to these couplings on both sides, the converter can be completely decoupled from both the input shaft and the output shaft in any operating states. When the converter is later coupled, instantaneous torque peaks that occur in one of the two clutches can be absorbed by the other clutch. Due to the fact that the two clutches can be operated at the same time, the converter change gearbox is relatively easy to control.
- one of the two-sided clutches can only be moved from its disengaged position into its engaged position with a predeterminable time delay. Due to this measure, it is particularly reliably prevented that when the other of the two-sided clutches is suddenly engaged, the resulting torque peak is absorbed by the other clutch, since the latter is still between its disengagement position and its engagement position due to the predeterminable time delay located.
- At least one of the two-sided clutches can only be moved from its disengaged position into its engaging position when the oil pressure of a hydraulic system connected to the converter change gearbox exceeds a predeterminable value. This measure ensures when starting the engine that the converter can only be loaded when it is supplied with sufficient oil pressure by the hydraulic system. It can also be provided that the drive motor can only be started when the two-sided clutches are in their disengaged positions. When starting the converter is therefore at rest with certainty, so that it can not be damaged in spite of initially low oil pressure.
- a part of the gear stages of the gearbox is formed by preferably co-rotating gearwheels which can optionally be connected to a gearbox shaft in a rotationally fixed manner by means of at least one clutch, in particular a multi-plate clutch.
- This at least one clutch, in particular a multi-plate clutch is used both for switching between two gear stages and for decoupling the converter from the corresponding shaft.
- the gearbox could be provided between the input shaft and the converter; however, the converter change-speed transmission is preferably characterized in that the input shaft in the power flow is followed in turn by a first clutch, in particular a starting clutch, the converter and the manual transmission with at least one clutch for selecting the respective shift stage and the output shaft.
- the constantly rotating gears together with the clutch are arranged on a common auxiliary shaft, and that a manual transmission Input shaft is preferably arranged in alignment behind a manual transmission output shaft.
- a crawler gear shift stage is provided, which can be selectively switched into the power flow of the gearbox by means of a sliding sleeve, the sliding sleeve preferably rotatingly but axially on a hollow shaft encompassing the gearbox input shaft slidably, is arranged.
- the output side of the clutch between the input shaft and converter is rotatably coupled to a motor PTO.
- the engine PTO consequently rotates independently of the respective rotational state of the output shaft, ie independently of the respective driving state, if the output shaft is connected to a drive axle, in particular tractor drive axle.
- some attachments are preferably operated depending on the respective ⁇ driving condition.
- An optional coupling of a corresponding output PTO shaft to the engine PTO shaft or to the output shaft of the manual transmission enables a sliding sleeve according to the invention.
- the output shaft is permanently connected to a first drive axle and that a clutch is provided for the optional connection of the output shaft to a second drive axle.
- the converter change-speed transmission according to the invention can be controlled in a variety of ways, but preference is given to manual control with a shift lever which can be moved along a shift path and which has at least two shift paths which are each associated with a shift stage comprises, the respective switching stage being changed during the transition of the shift lever from one shift path to the next shift path, and a movement of the shift lever along the shift path results in a corresponding, possibly stepless, change in the ratio of the converter.
- these measures result in a robust, reliable type of manual control.
- a transition lock is proposed according to the invention when the shift lever is moved from one displacement path to the other, which can only be released by disengaging the clutches on both sides of the converter. This in turn protects the converter from damage.
- To release the transition lock preferably only the clutch pedal is to be depressed.
- the shift lever is provided with a shift button for selectively actuating the clutch at least on one of the transducers. If, for example, the vehicle is to be stopped immediately, it is sufficient to press the switch button to disengage it - this saves having to press the clutch pedal until the converter is moved back using the switch lever and the switch lever has been moved to a neutral position between adjacent displacement paths. This reversing can take up to 2 seconds.
- a converter change gear control can be provided to control the clutch.
- the hydraulically or pneumatically disengageable clutches can be solenoid-controlled with the solenoid valves optionally operable by means of the shift lever.
- the shift lever actuates a switch assigned to one of the solenoid valves when moving along the respective displacement path.
- a proportional valve which can be controlled by the control, be arranged in a pressure fluid line connected to the clutches via the solenoid valves. This delay, already mentioned at the beginning, prevents the build-up of torque peaks which could damage the converter.
- control closes the proportional valve as soon as the clutch pedal is pressed, and the proportional valve opens with a time delay as soon as the clutch pedal is released.
- the proportional valve be opened by the control only when the oil pressure upstream of the proportional valve also exceeds a predetermined value.
- a starter lock for the drive motor which acts when the clutch pedal is not depressed. This measure also helps prevent accidents that could occur when starting with the clutch accidentally engaged.
- a rotary potentiometer coupled to the clutch pedal is proposed corresponding change in the control voltage or the control current for the proportional valve.
- FIG. 1 shows a simplified transmission diagram of a converter change transmission according to the invention for a tractor
- Fig. 2 is a circuit diagram of the control of the transmission according to Fig. 1;
- Fig. 3 shows a shift lever with shift gate for actuating the control according to Fig. 2 and
- Fig. 4 is a timing diagram to explain the function of the transmission according to the invention.
- the converter change-speed gearbox to be described below with reference to the figures, generally designated 10, is intended for use in a tractor, in particular a tractor, even if it is also possible to use it in other vehicles.
- the converter change gear is characterized by a compact design and reliable, low-wear function with the decisive advantage that an infinitely variable speed selection is possible over a large speed range divided into overlapping areas.
- the forward driving range V is subdivided into a slow driving range L and a fast driving range S, the first driving range also being designated VL and from 2.2 to 11 km / h. ranges and the second range, designated VS, from 7.9 to 40 km / h. enough.
- a reverse driving range labeled R ranges between 3.9 and 19.5 km / h.
- a crawl gear designated KR can be engaged at a standstill with a speed range between 0.47 and 2.56 km / h. (forward) or 0.83 and 4.12 km / h (backwards).
- a crankshaft 12 of a drive motor (not shown) (here with an output of 55 kW at 2,200 revolutions / min.) Is connected to a first clutch 14, which as a starting clutch is connected directly by a conventional clutch pedal can be actuated mechanically or hydraulically.
- clutch 14 On the output side, clutch 14 is connected in a rotationally fixed manner to a motor PTO shaft 16 and at the same time to a gearwheel 18, which in the example shown is seated on a hollow shaft 20 encompassing shaft 16 and has 45 teeth.
- the clutch 14 can be designed as a multi-plate clutch, in which case one of the rotating shaft disks is connected to the shaft 16 and another to the hollow shaft 20 in a rotationally fixed manner.
- the gear wheel 18 meshes with a gear wheel 22 (34 teeth) which is connected in a rotationally fixed manner to an input shaft 24 of a stepless converter 26.
- the converter is designed as a chain converter, for example the PIV type from Reimers, Bad Homburg.
- a converter chain designated 28 runs over a hydraulically adjustable drive wheel 30 as well as over a hydraulically adjustable driven wheel 32.
- Both wheels 30, 32 each consist of conical disks 34, which can be approached or separated from one another, in particular by means of oil pressure, for appropriate enlargement or Reduction of
- the converter 26 is followed by a manual transmission 40 with the two switching stages “forward slow” (V-L), “forward fast” (V-S), “reverse” (R) and “creeper gear” (KR).
- An input shaft 38 connected in a rotationally fixed manner to the wheel 32 of the converter 26 is aligned with a manual transmission output shaft 42.
- the power flow from the input shaft 38 to the output shaft 42 takes place via an auxiliary shaft 50.
- auxiliary shaft 50 On this auxiliary shaft 50, three clutches 52, 54 and 56 are arranged for the optional rotationally fixed connection of corresponding gear wheels 58 (41 teeth), 60 (65 teeth). and 62 (59 teeth) with the shaft 50.
- the gear 58 in the area of the clutch 52 meshes continuously with a gear 64 (41 teeth) which is fixed on the input shaft 38 and is additionally marked with S in FIG. 1.
- the gear 60 of the clutch 54 meshes continuously with a gear 66 (18 teeth), which is additionally marked with L in FIG. 1.
- This gearwheel 66 is mounted in a rotationally fixed manner on a hollow shaft 68 encompassing the shaft 38.
- This hollow shaft 68 can be coupled in a rotationally fixed manner to the input shaft 38 via a sliding sleeve 70, for which purpose it has to be moved from the middle neutral position shown to the left into a normal position indicated by dashed lines. In this switching position of the sliding sleeve, the driving range VL is obtained if the clutch 54 is moved into its engagement position.
- the shift sleeve 70 couples the hollow shaft 68 to a gear wheel 72 (40 teeth) rotatably mounted on the hollow shaft, weldhes constantly to a gear wheel 74 (26 teeth) combs.
- the latter is part of a double toothed wheel 76, which serves to engage the "creeper gear” and is additionally designated by KR in FIG. 1.
- the other gear 78 of the double gear 76 with 49 teeth constantly meshes with a gear 80 (17 teeth), which is non-rotatably seated on the input shaft 38.
- the clutch 56 In order to engage the reverse gear, the clutch 56 has to be moved into its engagement position, in which the gear 62 meshes with an intermediate gear 82 (39 teeth), which in turn meshes with a gear 84 (R), which is arranged on the hollow shaft 68 in a rotationally fixed manner, R (27 Teeth) engages.
- the normal reverse driving range (3.9 to 19.5 km / h) results; in the switch position "creeper gear" of the sliding sleeve 70, the driving range is 0.82 to 4.12 km / h (reverse).
- this is formed with a gear 86 (53 teeth) which constantly meshes with a gear 88 (29 teeth) of the auxiliary shaft 50.
- the latter gear wheel is connected directly or via an intermediate gear wheel to a gear wheel 90 (67 teeth), which can be selectively rotatably connected to a shaft 94 leading to the front axle by means of a further clutch 92.
- all-wheel drive can be optionally implemented.
- the manual transmission 40 described above is quite compact since all the gears (without creeper gear) are only arranged on two adjacent shaft axes. Synchronizations are not necessary.
- a second sliding sleeve 96 allows the optional coupling of a shaft 100 to the engine PTO (left position, labeled “engine PTO”); in the right-hand position labeled “PTO shaft”, the sliding sleeve 96, which is arranged on the shaft 100 so as to be non-rotatable but axially displaceable, couples a gear wheel 102 (27 teeth) attached to the sliding sleeve to the gear wheel 86 on the output shaft 42.
- the shaft 100 is optionally connected to a coaxial double gear 106 via a further sliding sleeve 104
- Gears 108 (18 teeth) and 110 (28 teeth) can be connected and alternatively with a double gear 112, one of which gear 114 (28 teeth) meshes with a gear 116 (21 teeth) of the sliding sleeve 104 and the other gear 118 (31 teeth) constantly meshes with the gear 108.
- a manual control is provided with a shift lever 130 indicated in FIG. 3, which can be moved along a shift link 132.
- Three displacement paths 134, 136 and 138 are provided, which are each assigned to the switching stages VS, VL and R of the manual transmission 40.
- the three displacement paths run parallel and at a distance next to each other at the same height.
- the displacement path 134 is assigned to the switching position VS and therefore allows the vehicle speed to be varied continuously between 7.9 and 40.0 km / h, as can be seen from the scale provided on the shifting gate.
- the displacement path 136 is assigned to the switching stage VL with a speed variation range between 2.2 and 11.0 km / h.
- the displacement path 138 is finally assigned to the switching stage R with a speed range of 3.9 to 19.5 km / h. (backward).
- the two lower ends of the displacement paths 136 and 138 are connected to one another by a horizontal transition path 140.
- the displacement path 136 goes in the range of about 7.9 km / h.
- a step-like transition path 142 which opens into the lower end of the displacement path 134.
- the respective switching stage is activated when the desired displacement path is selected by means of appropriate switches to be actuated by the switching lever.
- switches to be actuated electromagnetically they trigger a corresponding control pulse.
- the clutches 52, 54, 56 are actuated hydraulically - in this case, these clutches are assigned solenoid valves 152, 154 and 156, which control the oil pressure applied to the clutch clutches and which can be controlled via electrical switches 162, 164, 166 .
- Switch 162 which controls clutch 52 via solenoid valve 152, is closed when shift lever 130 is in displacement 134.
- the switch 164 controlling the clutch 54 via the solenoid valve 154 is actuated by the shift lever 130 in the displacement 136.
- the switch 166 is actuated by the shift lever 130 in the displacement path 138 in order to restrict this Clutch 56 assigned to reverse gear via the solenoid valve 156.
- the switch 173 In its upper position, the switch 173 connects a line section 176 to a voltage terminal 178 labeled D +, to which a voltage generated when the engine is running is present.
- line 176 there is a double switch 180, which is oil pressure-actuated and only changes to a contact closing position when a predeterminable oil pressure value of the hydraulic system supplying the converter change gear 10 with pressure oil is exceeded.
- Further pressure oil consumers such as the all-wheel clutch 92 and possibly a differential lock 193, are connected to the 18 bar output connection 198 of the unit 190 and are controlled by solenoid valves 194, 196.
- a proportional valve 200 is also connected to the connection 198 of the unit 190, the output oil pressure of which can be varied between 0 and 18 bar in proportion to an electrical control current or an electrical control voltage.
- the electrical actuating part 202 of the proportional valve 200 is provided with an input terminal 204, at which an electrical control line 206 ends; an output terminal 208 is connected to ground 211 via a line section 210.
- each solenoid valve 154, 152, 156 is connected to their pressure oil inlet at corresponding branch points 214 and 216; On the pressure delta output side, each solenoid valve 154, 152, 156 is exclusively with the associated clutch 54 or 52 baw. 56 connected.
- the electrical control line 206 connects the connection 204 of the valve 200 to a connection terminal 218, to which the battery voltage, for example of + 15V, is constantly present.
- Terminal 218 is followed in line 206 by an electromagnetically actuable switch 220, which receives its control voltage from line 176.
- the electrical control part of the switch 220 is in the , "_, _,” PCT / EP90 / 00248
- the switch 220 is followed by a further switch 226, which is normally in its closed position indicated by dashed lines in FIG. 2 with a continuous line 206.
- the switch 226, on the other hand, is opened when a special switch is actuated, in particular in the form of a switch button 228, at the upper end of the shift lever 130.
- a branch line 232 leads from a supply a branching point 230 of the line 206, which leads to the individual, already mentioned switches 162,164,166 for actuating the solenoid valves 152,154,156.
- a branching potentiometer 233 which can be actuated by clutch pedal 174, follows branching point 230 in line 206, so that when the clutch is “released”, an increasingly greater voltage at the proportional valve and thus an increasingly higher oil pressure at couplings 52, 54 , 56 results.
- the function of the control according to the figures 2 and 3 are briefly explained below, unless already apparent from the foregoing.
- a starter lock 240 connected to the switch 173 ensures that the engine can only be started when the clutch pedal 174 is depressed. Since all of the clutches 14, 52, 54, 56 are in their disengaged position when the clutch pedal 174 is depressed, the converter 26 is decoupled on the input and output sides, so that it remains at rest even when the engine is starting. The converter can therefore not be damaged by low system oil pressure.
- Switch 220 assumes its open position. There is therefore no control voltage at connection 204 of the proportional valve, so that the output oil pressure of the proportional valve 200 is also zero bar. All of the clutches 52, 54, 56 are therefore disengaged, so that the converter 26 is never operated under load when the oil pressure is too low.
- the switch lever 30 must be moved from one of the two neutral positions denoted by N in FIG. 3 to the respectively desired displacement path.
- the shift lever 130 is blocked in the respective neutral position N by means of the lock 170 or 172, which is only released when that
- Clutch pedal 174 is fully depressed.
- the two locks 170, 172 receive corresponding ones Control voltage, namely starting from the connection 178 via the switch 173 in its lower switching position and via the lower switch 250 of the oil pressure-operated double switch 242 (see also FIG. 2).
- the shift lever 130 is moved into the desired displacement path, e.g. pushed the displacement path 136, in which it closes the switch 164.
- the switch 173 goes into its upper switch position, so that the control voltage is applied to the relay of the switch 220 and the switch closes. Since the switch 226 is also normally closed, a control voltage corresponding to the rotary potentiometer position and thus the clutch pedal position is now present at the proportional valve 200.
- the clutch pressure P of the clutch 14 is plotted against the time in the upper half A and the clutch pressure of the clutch 52, 54, 56 in each case also plotted against the time in the lower half. It is assumed that both clutches are in their engagement position with maximum clutch pressure P.
- the clutch pedal 174 is pressed with a corresponding drop in the clutch pressure in the clutch 14.
- the respective clutch 52, 54, 56 is also immediately moved into its disengaged position with a minimum clutch pressure, since depressing the clutch pedal 174 interrupts the line 176 through the appropriate
- the switch 220 also opens and the control voltage at the solenoid valve 152, 154, 156 in question immediately becomes zero. The corresponding valve closes - the clutch opens.
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FI923658A FI923658A0 (fi) | 1990-02-15 | 1992-08-14 | Variatorvaexellaoda isynnerhet foer traktorer. |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19893901229 DE3901229A1 (de) | 1989-01-17 | 1989-01-17 | Wandler-wechselgetriebe, insbesondere fuer schlepper |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1991012442A1 true WO1991012442A1 (de) | 1991-08-22 |
Family
ID=6372242
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1990/000248 WO1991012442A1 (de) | 1989-01-17 | 1990-02-15 | Wandler-wechselgetriebe, insbesondere für schlepper |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0515363A1 (de) |
DE (1) | DE3901229A1 (de) |
WO (1) | WO1991012442A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004045314A1 (de) * | 2004-09-17 | 2006-03-30 | Piv Drives Gmbh | Nutzfahrzeug mit stufenlos verstellbarem Fahr- und/oder Zapfwellenantrieb |
GB2433299A (en) * | 2005-12-17 | 2007-06-20 | Agco Gmbh | Power take-off with dual integral multi-disc clutches engaged simultaneously |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4116389C2 (de) * | 1991-05-18 | 2000-12-28 | Agco Gmbh & Co | Antrieb für Fahrzeuge, insbesondere für Ackerschlepper |
DE4234629C2 (de) * | 1991-10-25 | 2002-07-18 | Volkswagen Ag | Stufenloses Getriebe für Kraftfahrzeuge |
DE102007062457A1 (de) | 2007-12-22 | 2009-06-25 | Deere & Company, Moline | Getriebeanordnung eines landwirtschaftlichen oder industriellen Nutzfahrzeugs |
DE102009026781A1 (de) | 2009-06-05 | 2010-12-09 | Zf Friedrichshafen Ag | Traktorgetriebe |
DE102016220130A1 (de) * | 2016-10-14 | 2018-04-19 | Deere & Company | Zapfwellengetriebe |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1159872A (en) * | 1966-02-22 | 1969-07-30 | Zahnradfabrik Friedrichshafen | Improvements in or relating to Driving Installations for Motor Vehicles, more particularly for Agricultural Vehicles |
US4606446A (en) * | 1983-04-08 | 1986-08-19 | Toyota Jidosha Kabushiki Kaisha | Apparatus for controlling a magnetic particle clutch for use in a vehicle |
FR2622517A1 (fr) * | 1987-11-03 | 1989-05-05 | Steyr Daimler Puch Ag | Mecanisme de transmission pour vehicule automobile utilitaire agricole |
-
1989
- 1989-01-17 DE DE19893901229 patent/DE3901229A1/de not_active Withdrawn
-
1990
- 1990-02-15 EP EP19900903803 patent/EP0515363A1/de not_active Ceased
- 1990-02-15 WO PCT/EP1990/000248 patent/WO1991012442A1/de active Search and Examination
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1159872A (en) * | 1966-02-22 | 1969-07-30 | Zahnradfabrik Friedrichshafen | Improvements in or relating to Driving Installations for Motor Vehicles, more particularly for Agricultural Vehicles |
US4606446A (en) * | 1983-04-08 | 1986-08-19 | Toyota Jidosha Kabushiki Kaisha | Apparatus for controlling a magnetic particle clutch for use in a vehicle |
FR2622517A1 (fr) * | 1987-11-03 | 1989-05-05 | Steyr Daimler Puch Ag | Mecanisme de transmission pour vehicule automobile utilitaire agricole |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004045314A1 (de) * | 2004-09-17 | 2006-03-30 | Piv Drives Gmbh | Nutzfahrzeug mit stufenlos verstellbarem Fahr- und/oder Zapfwellenantrieb |
GB2433299A (en) * | 2005-12-17 | 2007-06-20 | Agco Gmbh | Power take-off with dual integral multi-disc clutches engaged simultaneously |
Also Published As
Publication number | Publication date |
---|---|
EP0515363A1 (de) | 1992-12-02 |
DE3901229A1 (de) | 1990-08-16 |
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