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WO2018109179A2 - Boîte à engrenages planétaires et boîte de vitesses commandée sous charge - Google Patents

Boîte à engrenages planétaires et boîte de vitesses commandée sous charge Download PDF

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Publication number
WO2018109179A2
WO2018109179A2 PCT/EP2017/083086 EP2017083086W WO2018109179A2 WO 2018109179 A2 WO2018109179 A2 WO 2018109179A2 EP 2017083086 W EP2017083086 W EP 2017083086W WO 2018109179 A2 WO2018109179 A2 WO 2018109179A2
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
shaft
valve
planetary
tank
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2017/083086
Other languages
German (de)
English (en)
Other versions
WO2018109179A3 (fr
Inventor
Robert Jan LIET
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Trioliet BV
Original Assignee
Trioliet BV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Trioliet BV filed Critical Trioliet BV
Priority to EP17816824.1A priority Critical patent/EP3555496A2/fr
Publication of WO2018109179A2 publication Critical patent/WO2018109179A2/fr
Publication of WO2018109179A3 publication Critical patent/WO2018109179A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01K—ANIMAL HUSBANDRY; AVICULTURE; APICULTURE; PISCICULTURE; FISHING; REARING OR BREEDING ANIMALS, NOT OTHERWISE PROVIDED FOR; NEW BREEDS OF ANIMALS
    • A01K5/00—Feeding devices for stock or game ; Feeding wagons; Feeding stacks
    • A01K5/001—Fodder distributors with mixer or shredder
    • A01K5/004—Fodder distributors with mixer or shredder with mixing or shredding element rotating on vertical axis
    • 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
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2066—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using one freewheel mechanism
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
    • F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms

Definitions

  • the invention relates to a planetary gearbox according to the preamble of claim 1 and a powershift transmission according to the preamble of claim 10.
  • the first clutch couples two of the three components while the second clutch is disengaged to set a gear ratio of 1: 1. If the second clutch is engaged, and the first clutch disengaged, then one of the components, here the sun gear is locked to the housing via the second clutch, so that the outer wheel driven by the first shaft via the planetary gears revolving on the sun gear the planet carrier and thus the second shaft drives, for example, with a reduction of 1: 1, 7.
  • the first and second clutches must be precisely engaged and disengaged alternately and intersecting in order to switch without interruption of traction.
  • a power shift transmission known from EP 1 561 971 A1 (FIG.
  • a planetary gear and a spur gear with bypass shaft are arranged in parallel in the housing, wherein overrunning clutches between spur gears and the shafts carrying them are provided.
  • a pure spur gear (Fig. 2) is provided from a hydraulic circuit hydraulically actuated clutch, and is provided between a gear on a bypass shaft and the bypass shaft an overrunning clutch.
  • the invention has for its object to provide a planetary gear or power shift that is structurally simple and reliable and very easy to switch, with only one clutch is hydraulically actuated when switching and no excessive bearing loads occur during the switching process. Another object is to enable the transmission regardless of the temperature-dependent varying viscosity of the hydraulic medium without interruption of traction precise switching operations.
  • the stated object is achieved with the features of claim 1 and with the features of claim 10.
  • the overrunning clutch as the second clutch automatically switches only depending on the respective direction of rotation of a component functionally associated with him between a coupling state and a free-running state, does not need during the switching operation of the overrunning clutch be operated externally and nevertheless the switching process takes place without interruption of traction.
  • the hydraulic circuit is generally useful for powershift transmission with at least one hydraulically actuated clutch, because it is not affected by the current viscosity of the hydraulic medium, and also the function of the pump is largely independent of the viscosity of the hydraulic medium.
  • the overrunning clutch works with pinch rollers or clamping pieces, which generate extremely low resistance in the free-running state, however, lock in the direction of rotation of a component with an exactly predeterminable transition.
  • Such overrunning clutches are known for example from the catalog "freewheel” the company Ringspann GmbH, 61348 Bad Homburg, DE, 2015/2016 edition (also www.ringspann.de).
  • the first clutch is a hydraulically actuated multi-plate clutch with mutually geared with two components slats with large friction surfaces.
  • the multi-plate clutch is spring-biased in the release direction to drain the release process as quickly as possible when relieving the hydraulic pressure.
  • the first component (the outer wheel) is rotatably connected to the first shaft
  • the second component (the planet carrier) is non-rotatably connected to the second shaft
  • is the third component (the sun gear) relative to the first and second components in a direction of rotation (eg the direction of rotation of the first and second shafts) in the overrunning clutch rotatable and mur fixed in the opposite direction of rotation on the housing.
  • the first clutch can be arranged either between the first and second, or between the first and third, or between the second and third components, depending on the space and the structural requirements in the planetary gearbox. This planetary gear allows switching between two ratios.
  • the first shaft is an input shaft and the second shaft is an output shaft that is connected to the mixer.
  • an angle gear can be provided to deflect the transmitted torque from the substantially horizontal gear train on the feed mixer to the usually about a vertical axis rotating mixing element.
  • this arrangement may be reversed, i. h., That the second shaft is an input shaft and the first shaft is an output shaft, wherein, preferably, also here before the second shaft or after the first shaft, an angle gear can be provided.
  • a simple shift operation of the first clutch from a tractor or from a drive complex with a hydraulic system is possible with a hydraulic circuit having a connected to a solenoid-operated multi-way valve inlet and outlet, in which between a flow control valve, and optionally a pressure accumulator connected to the hydraulic line , And the multi-way valve in the flow direction to the multi-way valve blocking, is arranged on the multi-way valve hydraulically releasable check valve or seat valve.
  • the multi-way valve can be a 4/3-way valve with blocking neutral position and solenoid operation, and be connected to a pressure source and a tank.
  • the multi-way valve is expedient the so-called tractor valve in the hydraulic system coupled to the feed mixer tractor, which drives a shaft of the planetary gear, for example via the PTO.
  • a hydraulic motor or an electric motor can serve as the drive source.
  • the advantage is given to a hydraulic circuit which reliably ensures the switching operations of the first clutch, irrespective of the viscosity of the hydraulic medium, by providing a hydraulic pump with either reversible conveying direction and two mutually conveying and sucking connections, which, preferably, with e.g. Tank formed by the housing of the planetary gearbox are connected via a shuttle valve system.
  • the pump can release it, so to speak, specifically during disengagement of the first clutch, in order to avoid a temporary and / or uncontrollable grinding state in the first clutch.
  • the disengagement of the first clutch can expediently be assisted by a biasing force, for example by return springs.
  • an inlet and outlet line to the respective first coupling is connected to a connection of the pump, in which a seat valve which can be hydraulically unlocked via an unlocking line from the other connection is arranged.
  • each connection of the pump is secured by a pressure relief valve to the tank, which when reaching z. B. the maximum clutch engagement pressure responds.
  • the poppet valve maintains the engagement pressure leaking, allowing the pump to shut off. It may be useful if a pressure sensor and / or a pressure accumulator is connected to the inlet and outlet line between the seat valve and the first clutch / are. As soon as the pressure sensor reaches the predetermined clutch engagement pressure, e.g. B.
  • the pump can be switched off. If the optional accumulator is connected, it can compensate for any leakage in the first clutch. If the pressure sensor uses a pressure drop, for example to 16 bar, starting from 25 bar, which corresponds, for example, to the minimum engagement pressure of the first clutch, the pump is switched on again until the pressure is again 25 bar. In this case, the pump via the shuttle valve system, the hydraulic medium, for example, from the housing of the planetary gear or suck from another tank. In order to disengage the first clutch, the conveying direction of the pump is reversed so that the pump sucks the first clutch, so to speak, or allows the hydraulic medium to reach the tank without appreciable throttling resistances.
  • a 3/2-way valve preferably with magnetic actuation, can be arranged in the hydraulic circuit in the inlet and outlet line between the pump and the seat valve, from which a separate discharge line leads to the tank.
  • the 3/2-way valve is in a switching position in which the inlet and outlet line to the seat valve is continuous, while the other drain line to the tank remains shut off.
  • the 3/2-way valve is simultaneously switched to its second switching position by reversing the conveying direction of the pump, in which the supply and discharge line is connected directly to the tank via the further discharge line, so that the hydraulic medium is very low in resistance flows out while the pump ensures that the seat valve remains hydraulically unlocked.
  • the planetary gearbox includes two or more sequentially connected planetary gear, each of which is switchable, leads for selectively switching the planetary gear or their first clutches from one port of the pump, a supply and Ab-line to each first clutch, in which At least the seat valve and the 3/2-way valve connected to the tank are included in the inlet and outlet pipes.
  • At least one Unlock line of the multiple Unlock lines can at least a third 3/2-way solenoid operated valve may be arranged, from which a drain line leads to the tank.
  • This third 3/2-way valve is used to relieve the Entsperrtechnisch to the seat valve reliably and quickly, as soon as this is necessary for example after engagement of the clutch.
  • at least one of the 3/2-way valves is blocked in a first switching position in the outflow direction to the pump by a check valve.
  • Fig. 1 is a side view, partly in section, of a non-limiting ⁇
  • Example mobile feed mixer coupled to a tractor, with as a non-limiting example two mixing devices in a mixing container
  • Fig. 2 is a longitudinal section of a first embodiment of a
  • Fig. 3 is a longitudinal section of another embodiment of a
  • FIGS. 4 is a block diagram of a hydraulic circuit for actuating a hydraulically shiftable first clutch in the planetary gear transmissions of FIGS. 2 and 3,
  • Fig. 5 is a block diagram of another embodiment of a hydraulic circuit, e.g. for powershift transmission,
  • Fig. 6 shows a detail variant of the hydraulic circuit of Fig. 5, and
  • Fig. 7 shows another embodiment of a hydraulic circuit for a planetary power transmission with two successively connected planetary gears.
  • a feed mixer F on a base 1 which is movable on wheels 2 and is coupled for example via a drawbar 3 to a terminal 4 of an associated tractor S.
  • the substructure 1 carries a mixing container 5, which delimits a mixing chamber 6, in which in the embodiment shown, two mixing elements M, for example, vertical mixing screws, are arranged rotatably drivable.
  • the feed mixer F could also have a plurality of mixing containers, a plurality of mixing chambers and even more mixing elements, or only a mixing container with a mixing chamber and a mixing element, but could also be designed in the manner of a horizontal mixer, a paddle mixer, or another mixer.
  • Fig. 1 a feed mixer F on a base 1, which is movable on wheels 2 and is coupled for example via a drawbar 3 to a terminal 4 of an associated tractor S.
  • the substructure 1 carries a mixing container 5, which delimits a mixing chamber 6, in which in the embodiment shown, two mixing elements M, for example, vertical mixing screws, are arranged
  • each mixing element M is driven by an angle gear or angle planetary gear 7 of a propeller shaft 8, which leads to a stationary built on substructure 1 planetary gear P, which is driven for example by a PTO shaft 9 of the tractor S, or by a hydraulic motor or another drive and that acts as a power shift transmission, that is switchable without interruption of traction. In a stationary embodiment of the feed mixer F this could have its own drive for the planetary gear P.
  • each mixing element M could be driven by a planetary gearbox P installed in front of the bevel gear 7, or the planetary gearbox P could be installed between the respective bevel gear 7 and the mixing element M.
  • the planetary gearbox P is switchable between two gear ratios without interruption to drive the mixing member M with high torque and relatively low speed or lower torque and higher speed.
  • Fig. 1 indicates an operation 1 1, which may be connected to an actuator 10 in the tractor S.
  • the actuating device 10 may be the actuation of the so-called tractor valve or, in the case of the hydraulic circuits of FIGS. 5-7, at least one electrical switch 12 or the like.
  • the actuating device 10 could also be provided directly on the feed mixer F.
  • the planetary gear P is set, for example, front anchorages in the base 1 of the feed mixer F in Fig. 1.
  • FIG. 2 and 3 illustrate two different embodiments of the planetary gear P.
  • two or more planetary gear which are each switchable, may be provided in series one behind the other.
  • 2 and 3 are in a housing 18 of the planetary gear P first and second coaxial shafts 14, 15 rotatably mounted.
  • the first shaft 14 may be connected to the PTO shaft 9, the second shaft 15, however, with the propeller shaft 8, in Fig. 1.
  • the second shaft 15 may be connected to the PTO 9, and the first shaft 14 with the propeller shaft 8 in Fig. 1.
  • a first component K1 of a planetary gear rotatably connected to the first shaft 14, which is an outer gear 16 with an internal toothing 17.
  • a second component K2 of the planetary gear namely a planet carrier 19, rotatably connected, which carries a plurality of planet gears 20 which mesh with the outer gear 16 and the inner teeth 17 and are rotatably mounted.
  • a third component K3 of the planetary gear is rotatably mounted in the housing 18, namely a sun gear 21, with the external teeth of the planet gears 20 also mesh.
  • the third component K3 or the sun gear 21 is rotatably mounted in Fig. 2 in rolling bearings 22, 23 on the planet carrier 19 and the second shaft 15.
  • a first hydraulically actuated clutch C1 is arranged, which is designed as a multi-plate clutch with a plurality of clutch plates 25, which alternately with the second and third components K2 and K3 are toothed, and which is engageable by a hydraulic piston 26 against a return spring 28 to connect the second and third components K2, K3 rotatably.
  • a second clutch C2 is also arranged in the housing 18, which is designed as a passing freewheel 24 and automatically switches depending on a reversal of the third component K3 between a blocking state and a free-running state.
  • the sun gear 21 sits in Fig. 2 in the overrunning clutch 24 outside.
  • the hydraulic piston 26 of the first clutch C1 is acted upon via hydraulic pressure in the cylinder chamber 27 by means of passages 27 provided in the second shaft 15 for relieving pressure on the first clutch C1, then e.g. supported by the return spring 28.
  • the channels 27 are connected to a hydraulic circuit H, which is explained for example with reference to FIGS. 4 to 7.
  • the clutch plates 25 are released from each other by pressure relief via the channels 27 and the return spring 28, so that the sun gear 21 could rotate relative to the planet carrier 19. Due to the rotational friction in the rolling bearings 22, 23 and acting on the planet carrier 19 holding torque on the second shaft 15, however, the outer wheel 16 rotates the planetary gears 20, which now try to rotate the sun gear 21 in the opposite direction and against the direction of rotation of the first shaft 14. In now reversed direction of rotation, however, the overrunning clutch 24 is automatically in the blocking condition, so that the sun gear 21 is blocked relative to the housing 18.
  • the embodiment of the planetary gear P in Fig. 3 differs from that of FIG. 2, characterized in that with slightly different internal structure of the first, second and third components K1, K2 and K3, the first clutch C1 as a multi-plate clutch 25 with hydraulic actuation by the hydraulic piston 26 and against return springs 28 operatively between the first and second components K1, K2, ie between the outer wheel 16 and the planet carrier 19, while the sun gear 21 rotatably supported in the rolling bearing 22 on the planetary carrier 19 as the third component K3 inside the second clutch C2, i. the overrunning clutch 24 of the housing 18 is arranged.
  • the overrunning clutch 24 automatically switches to the blocking state so that the sun gear 21 moves in the locked state Housing 18 is blocked, and the planetary gears 20 rolling on the blocked sun gear 21 drive the planet carrier 19 in the same direction of rotation as the first shaft 14, and thus rotate the second shaft 15 with the transmission ratio of, for example, 1: 1, 7.
  • the overrunning clutch 24 automatically resumes the free-running condition as soon as the sun gear 21 rotates in the "correct" direction of rotation of the first shaft 14.
  • Fig. 4 illustrates an exemplary embodiment of a hydraulic circuit H for the hydraulically actuated first clutch C1 of the planetary gear P of Fig. 2 and 3.
  • a multi-way valve 40 here a 4/3-way valve with blocking neutral position, connected to a pressure supply P 'and a tank T
  • an inlet and outlet line 41 extends via the channels 27 to the cylinder chamber of the piston 26 of the first clutch C1.
  • a check valve or seat valve 43 which can be activated hydraulically via an unlocking line 38 is provided downstream of the multiway valve 40 and blocks the multiway valve 40 in the flow direction.
  • a pressure accumulator 44 Downstream of the first clutch C1, a flow control valve 45 is optionally arranged in the supply and discharge line 41, which consists, for example, of a control diaphragm 46 for varying the flow cross section or the quantity and an immediate non-return valve 47, which is in the flow direction to the first clutch C1 locks.
  • the multi-way valve 40 is, for example, magnet-actuated and can be controlled via the actuator 10 shown in FIG. 1, for example a joystick or switch 12. In tractors S older types, the tractor valve can be operated, for example, with a lever in the cabin.
  • the first clutch C1 is, for example, under pressure from the pressure accumulator 44.
  • the seat valve 43 locks.
  • the supply and discharge line 41 is isolated from both the pressure supply P 'and from the tank T.
  • the first clutch C1 and the pressure accumulator 44 may be depressurized, so that the first clutch C1 is disengaged.
  • the multi-way valve 40 is placed in the lower switching position, then the supply and discharge line 41 is connected to the pressure supply P ', however, the Entsperr effet 38 with the tank T.
  • the upcoming pressure opens the seat valve 43, feeds the pressure accumulator 44 and generates Engagement pressure in the clutch C1, whose structure can be controlled by the flow control valve 45.
  • the clutch C1 is engaged.
  • the multi-way valve 40 is switched to the upper switching position, then the supply and discharge line 41 is connected to the tank T, while the Entsperr effet 38 with the pressure supply P '.
  • the seat valve 43 is unlocked, so that the hydraulic pressure via the then opening check valve 47 from the first clutch C1 degrades relatively quickly to the tank C.
  • the accumulator 44 can then empty.
  • the first clutch C1 is disengaged.
  • the multi-way valve 40 is expediently arranged and actuatable, the so-called tractor valve or, in the case of stationarily used feed mixer F, in a hydraulic system on the feed mixer wagon.
  • Fig. 5 illustrates another embodiment of the hydraulic circuit H, for example for actuating the first clutch C1 in the planetary gear P.
  • the hydraulic circuit H in FIG. 5 has as its core a pump 29 which is reversible in its conveying direction and has two mutually conveying and sucking connections 32, 33 which is driven by an electric motor 30 which is reversible in direction.
  • the speed of the pump 29 via the electric motor 30 is even controllable, as indicated by an arrow 31.
  • Nodes 34, 35 associated with ports 32, 33 are connected to tank T via a shuttle valve system 36, with shuttle valve system 36 automatically switching pressure-responsively to connect either node 34 or node 35 to tank T and the other node to block.
  • shuttle valve system 36 automatically switching pressure-responsively to connect either node 34 or node 35 to tank T and the other node to block.
  • nodes 34, 35 lead discharge lines 48 to the tank T, in which pressure relief valves 37 are arranged, which are for example set to a pressure value of 25 bar, which corresponds to the maximum clutch engagement pressure of the first clutch C1.
  • the tank T may be the housing 18 containing the hydraulic medium or oil.
  • the supply and discharge line 41 extends to the cylinder chamber of the hydraulic piston 26 of the first clutch C1, wherein in the supply and discharge line 41, the hydraulically releasable from the Entsperr Arthur 38 seat valve 43 is seated and optionally a pressure sensor 37 and / or the pressure accumulator 44 are connected, between the seat valve 43 and the cylinder chamber of the piston 26.
  • the unlock line 38 extends from the junction 33 associated node 35 to the seat valve 43rd If the pump 29 is driven so that the port 32 delivers and the port sucks 33, then the supply and discharge line 41 is pressurized, opens the seat valve 43 and the hydraulic piston 26 is acted upon to engage the first clutch C1. The pressure builds up, for example, until the response of the left in FIG.
  • the pressure relief valve 37 or by monitoring the pressure sensor 37 which turns off when a predetermined pressure value, the pump.
  • the unblocking line 38 is first relieved from the connection 33 before the connection 33 sucks from the tank T via the unidirectional open-loop valve system 36.
  • the pump 29 is driven in the opposite direction of conveyance, so that the port 33 delivers and the port sucks 32, then the seat valve 43 is unlocked via the unblocking line 38 and simultaneously the shuttle valve system 36 is switched to maintain the pressure in the unlock line 38, and to unlock the supply and discharge line 41 to the tank.
  • the hydraulic medium or oil is aspirated so to speak on the then released poppet valve from the cylinder chamber of the hydraulic piston 26, wherein the pushing out of the hydraulic medium is supported by the return spring 28.
  • the pressure accumulator 44 can compensate for any leakage, wherein the pressure sensor 37 registers a drop in pressure and at a predetermined pressure value, for. B. 16 bar, the pump 29 turns back in the conveying direction, with the pressure accumulator 44 recharged and the first clutch C1 is engaged or remains.
  • the illustrated shuttle valve system 36 could alternatively be composed of two mutually cooperating valves, or formed in a 3/2-way valve.
  • the embodiment of the hydraulic circuit H shown in FIG. 6 has a higher safety aspect, since in addition to Fig. 5 in the inlet and outlet line 41 between the pump 29 and the seat valve 43, a 3/2-way valve 49 with magnetic actuation 50 and a Return spring 51 is included, one port of which a further discharge line 52 leads directly to the tank T.
  • the 3/2-way valve 49 is simultaneously switched by the return spring 51, so that the seat valve 43 incoming supply and discharge line 41 is connected to the further discharge line 52 to the tank T, while the connection to the terminal 32 is blocked.
  • the hydraulic medium flowing out through the unlocked poppet valve 43 takes the direct, resistance-free path via the discharge line 52 to the tank T and / or is exhausted from the port 32 while the shuttle valve system 36 blocks to the node 35.
  • the first clutch C1 is disengaged.
  • the embodiment of the hydraulic circuit H shown in Fig. 7 is designed for a planetary gear P1 with here, for example, two series-connected planetary gears P1 between the first and second shafts 14, 15 in Figs. 2 and 3 on the basis of the hydraulic circuit H of FIG ,
  • the supply and discharge line 41 leads from the connection 32 of the pump 29, starting from the node 34, via branches 41 'to each first one Clutch C1, C1 ',
  • the 3/2-way valve 49, 49 'and the seat valve 43 are included, which is unlocked via connected to the terminal 33 and the node 35 Entsperr effet 38.
  • At least the 3/2-way valve 53 can lock in a switching position in the flow direction to the pump 29.
  • both first clutches C1, C1 ' may be engaged, with the engagement pressure being maintained by the poppet valves 43 (leak-free), while the release conduits 38 are depressurized, and also the 3/2-way valves 49, 53, 49' assume switching positions shown.
  • the pump 29 can be switched off. To disengage the right in Fig. 7 clutch C1, the pump 29 is turned on so that the port 33 promotes and the port sucks 32.
  • Shuttle valve system 36 blocks node 35 to the tank.
  • the 3/2-way valve 49 connects the poppet valve 43 to the tank T and / or the port 32 via the exhaust duct 52.
  • the right clutch C1 is disengaged.
  • the first clutch C1 'left in FIG. 7 is still engaged, for example.
  • the left first clutch C1 ' is the 3/2-way valve 49' in the switching position shown in Fig. 7, while the 3/2-way valve 53 is magnetically connected to the Entsperr effet 38 between the terminal 33 and the right Unlock seat valve 43.
  • the 3/2-way valve 49' is switched from the switching position shown magnetically to unlock the branch 41 'to the seat valve 43, and block the drain line 52 to the tank T.
  • the pump 29 is switched, the port 32 promotes; the connection sucks 33.
  • the Entsperr effeten 38 are depressurized.
  • the left clutch C1 ' is engaged.
  • the reversible in the conveying direction pump 29 has the advantage of a rapid and reliable pressure reduction, especially when disengaging the respective first clutch C1, C1 'regardless of, for example, temperature-dependent significantly varying viscosity of the hydraulic medium or oil, and for example in cold and tough hydraulic fluid or oil when disengaging to prevent a grinding condition of the clutch.
  • the pump 29 also offers the advantage of working in their promotion largely independent of the viscosity of the hydraulic medium.
  • a relatively high return pressure can prevail in the hydraulic system 39 of the tractor S when the hydraulic medium is cold, which can complicate the rapid disengagement of the clutch. Namely, no such influence can be exerted on the outflow of the hydraulic medium to the tank, but this is made possible by the concept of the hydraulic circuit H in FIGS. 5 to 7.

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Abstract

Selon l'invention, dans une boîte de vitesses à engrenages planétaires (7) comprenant des premier et deuxième embrayages (C1, C2), le premier embrayage (C1) peut être actionné de manière hydraulique depuis l'extérieur. En revanche, le deuxième embrayage (C2) réalisé sous la forme d'une roue libre de rattrapage (24) s'adapte de manière autonome en fonction du sens de rotation entre des états de couplage et en roue libre.
PCT/EP2017/083086 2016-12-16 2017-12-15 Boîte à engrenages planétaires et boîte de vitesses commandée sous charge Ceased WO2018109179A2 (fr)

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EP17816824.1A EP3555496A2 (fr) 2016-12-16 2017-12-15 Boîte à engrenages planétaires et boîte de vitesses commandée sous charge

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DE202016107084.8 2016-12-16
DE202016107084.8U DE202016107084U1 (de) 2016-12-16 2016-12-16 Planetengetriebe und Lastschaltgetriebe

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CN112470965B (zh) * 2020-12-02 2022-07-12 张慧勤 一种针对牲畜舔砖的旋转清洁式安装架

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0880890A1 (fr) 1997-05-30 1998-12-02 Trioliet Mullos B.V. Méthode et dispositif pour mélanger du fourage
EP1561971A2 (fr) 2004-02-06 2005-08-10 Trioliet Mullos B.V. Dispositif d'entraínement
DE202015104960U1 (de) 2015-09-18 2016-12-21 Trioliet B. V. Futtermischer

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL9401190A (nl) * 1994-07-20 1996-03-01 Applied Power Inc Hydraulische schakeling.
AT412113B (de) * 2002-10-02 2004-09-27 Hoerbiger Hydraulik Hyraulische betätigungsanordnung
WO2006002450A1 (fr) * 2004-06-30 2006-01-12 Magna Drivetrain Ag & Co Kg Systeme hydraulique pour commander deux embrayages d'une boite de vitesses
DE102010001259B4 (de) * 2009-07-30 2013-01-31 Zf Friedrichshafen Ag Getriebeölpumpe für ein Automatgetriebe
WO2012113368A2 (fr) * 2011-02-23 2012-08-30 Schaeffler Technologies AG & Co. KG Dispositif hydraulique pour actionner un embrayage
EP2584220B1 (fr) * 2011-10-20 2014-08-13 AIRBUS HELICOPTERS DEUTSCHLAND GmbH Engrenage planétaire pour transmission variable
DE102015200777A1 (de) * 2015-01-20 2016-07-21 Schaeffler Technologies AG & Co. KG Hydraulisches Kupplungsbetätigungssystem mit Senkbremsventil
US10344829B2 (en) * 2015-03-20 2019-07-09 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Electric axle drive for a motor vehicle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0880890A1 (fr) 1997-05-30 1998-12-02 Trioliet Mullos B.V. Méthode et dispositif pour mélanger du fourage
EP1561971A2 (fr) 2004-02-06 2005-08-10 Trioliet Mullos B.V. Dispositif d'entraínement
DE202015104960U1 (de) 2015-09-18 2016-12-21 Trioliet B. V. Futtermischer

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EP3555496A2 (fr) 2019-10-23
DE202016107084U1 (de) 2018-03-19

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