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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
• • 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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H2045/007—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  comprising a damper between turbine of the fluid gearing and the mechanical gearing unit
• • 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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
• • 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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0215—Details of oil circulation
• • 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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
  • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
• • 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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
  • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
  • F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
• • 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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
  • F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping 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
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
  • F16H2045/0284—Multiple disk type lock-up clutch

Definitions

• the invention relates to a torque converter with a lock-up clutch, wherein this lock-up clutch is equipped with at least two axially displaceable blades.
• the torque converter is equipped with a three-channel system. To optimize the flow of oil, and thus for better cooling of the slats, measures are provided which force the flow of oil through the slats.
• the document DE 103 50 935 A1 is known from the prior art, in which it is described that the oil flow through the lamellae of a converter bridging clutch can be optimized by appropriate measures. For this purpose, in a region that is far from bridging, the flow resistance for the oil is increased. In a second independent measure, the flow resistance for the oil is reduced via the lock-up clutch.
• the object is achieved in that the circulating oil flow in the region of the hydrodynamic components (pump, turbine, stator) only on the fins of the lock-up clutch or can flow.
• This is achieved by an additional wall is mounted on the piston, this additional wall is mounted on the side of the piston, which faces away from the disk pack and thus the pressure chamber for the piston.
• the end of the additional wall, which is close to the disk pack is applied substantially oil-tight to the surface of the adjacent disk.
• the end of the additional wall, which is close to the transmission input shaft, in turn, is substantially oil-tight - but rotatable - connected thereto.
• the outer toothing region on the outer disk carrier is substantially oil-tight at its end facing the turbine. Furthermore, a channel is arranged in the outer toothing region, at the end remote from the turbine, which makes an oil inflow from the region of the hydrodynamic components substantially impossible. This always requires the oil in its circulation flow over the slats. If the lock-up clutch is closed, then the oil can not circulate unhindered, but then the torque is transferred exclusively via the clutch. In other words, the pump and the turbine run synchronously, so there is no work and thus no friction generated.
• the lock-up clutch is open, i. There is a high heat development by the Torusströmung in the pump, turbine and stator, so the circulation to and from the converter, take place in full.
• the outer toothing region on the outer plate carrier at its end facing the turbine is not closed.
• a sealing element is arranged in the area between the piston and the adjacent lamella which seals the radial area from the outer diameter of the lamella to axial bores through the lamellae.
• Figure 2 shows a detail of Figure 1 with the lock-up clutch open
• FIG. 3 shows a section from FIG. 1 with the lock-up clutch closed or slipping
• FIG. 4 shows a half section through a converter according to the second solution
• FIG. 8 shows a section from FIG. 4;
• FIG. 6 shows a half section according to the second solution with a continuous additional wall;
• FIG. 8 shows a half section according to the second solution, but with two-part additional wall.
• FIG. 1 shows a torque converter 1 which rotates about an axis of rotation 21.
• the converter 1 has in its housing 2 essentially a pump 9, a turbine 10, a stator 11 and an over-coupling 3.
• a damper 18 In the power flow between the lock-up clutch 3 and a hub 25 and a damper 18 is arranged.
• the transmission input shaft and the torque support for the stator 11 have been omitted from the drawing.
• the converter has a three-channel system. That is, there are three channels in total to realize oil circulation and the control of the lock-up clutch 3. It is hereby assumed that the flow of oil for the circulation can have two directions. The direction shown in FIG. 1 is thus to be understood only as an example and not by way of limitation. From a first channel 7, which can be seen between the sleeve-shaped extension at the right end of the converter and the torque arm, not shown, for the stator 11, the oil first flows into the pump 9. A portion of the oil then completes a continuation of the Torusströmung in the TurbinelO and the stator 11. The other part of the oil exits at the gap between the pump 9 and turbine 10 and pours into the remaining area of the first space eighth
• the slats 4 engage with their teeth alternately in the teeth of an outer disk carrier 5 or an inner disk carrier 6.
• a sealing element 15th This sealing element 15 makes an oil flow between the teeth of the outer disc carrier 5 and the teeth of the outer engaging blades 4 in Substantially impossible because it rests sealingly on both the front edge of the outer plate carrier and on the right plate - the so-called end plate.
• the sealing element 15 is configured in the embodiment as an annular spring, but it may also be formed in the context of the invention as an annular disc, in which case the annular disc can also serve as an axial stop 22 at the same time.
• the sealing element 15 may be attached by welding or caulking (a kind of rivets) to the outer plate carrier 5, to the housing 2 or to an output part of a radially outer damper.
• the invention also includes a third channel 17, which is connected to a space 16.
• This space 16 is formed, for example, by an additional wall 19 is arranged on the piston 14 by means of spacer rivets 24.
• the oil flow over the fins 4 is shown in detail. It can be seen in the figure 2 at the gap between the axial stop 22 and the adjacent thereto lamella 4 that here the lock-up clutch is not closed.
• the sealing element 15 is caulked radially outward with the outer plate carrier 5.
• the radially inner end of the sealing element 15 rests resiliently on the end plate and thus prevents the inflow of the oil in the outer toothing region. Therefore, the oil flows over the inner toothing region (that is, between the teeth of the inner disk carrier and the radially internally toothed disks 4.
• FIG. 3 differs from FIG. 2 only in that here the bridging clutch 3 is closed.
• the second inventive solution which is to be shown with the figures 4 and 5, is that not the outer gear portion is sealed at the outer plate carrier 5, but that the radially outer portion of the piston near the blade is well sealed, so that here no oil between the radially outer fin surface and the ring-nose of the piston can flow.
• the lamellae are provided with at least one axial bore 33.
• Boreholes 33 are preferably located in the radial middle region in the lamellae 4. If the oil has now taken its course in the manner described above and now reaches the bores, the oil then flows axially in the direction of the piston 14. As can be clearly seen in FIG. 5, the annular nose 26 of the piston 14 has recesses, so that the oil can flow into the third space 16.
• FIGS. 4 and 5 also show a push-in sleeve 28 which has to guide the third channel 17 about the toothing between the hub 25 and the transmission input shaft 29.
• This toothing area is made very precisely, whereby an oil flow is very difficult here.
• this insertion sleeve is not required because there the oil flow radially outward of the gearing hub / gear shaft to the right - ie towards the gearbox - is guided.
• FIG. 5 another inventive concept is also clearly visible:
• a rotation lock for the piston 14 can be seen, which is riveted to the housing and provided with slots radially on the outside, wherein webs 32 engage in these slots.
• this rotation lock 30 is designed as a plate spring.
• the riveting could also be on the piston and the connection by means of slots and corresponding webs 32, also on the housing wall 2.
• the illustrated rotation lock also has another advantage: Through its radial extent to the transmission input shaft 29, the rotation lock 30 is also used as a thrust washer - ie as an axial sliding bearing - between the housing 2 and transmission input shaft 29th
• the additional wall 19 is in turn connected sealingly with the slats.
• the peculiarity in this embodiment lies in the fact that the additional wall 19 extends into the outer toothing region of the lock-up clutch 3 and at the same time rests flat on the adjacent lamella. If the additional wall itself engages with teeth in the toothing of the outer disk carrier, then a rotation lock 30 - as shown in FIGS. 4 and 5 - is not necessary since the additional wall 19 with the piston 14 and the piston 14 are secured against rotation by the riveting 31 ,
• the additional wall 19 must also have a bore in the region.
• the piston has a recess 34.
• This recess 34 may for example consist of a blind bore and a radially inwardly adjoining groove (as shown in Figure 6). But also an arcuate groove is conceivable here.
• the additional wall 19 has been formed as a disk-shaped spring element. It should be emphasized that this spring element seals the left blade both radially outward, and radially inward by conditioning. Because of the small wall thickness of the additional wall 19 shown in Figure 7 is not clear enough to recognize that here is a hole in the additional wall 19 is present, through which the oil in the recess 34, and then in the third space 16 continue to flow can.
• FIG. 8 shows a further embodiment of the additional wall 19, which is designed in two parts.
• the radially inner region 19a of the additional wall 19 is provided with a thicker wall thickness than the radially outer 19b.
• the radially outer region 19b is preferably configured elastically and is also pressurized with a spring force, preferably with a plate spring 35.
• a plate spring 35 is advantageous because it allows the oil to drain through its slots in the third space 16 because of their partially radially slotted structure.
• the clear additional outflow 19b defines a clear outflow of the oil.
• the oil can not flow out of the space 8, without having flowed over the friction surfaces of the slats.
• the radially outer 19b and the radially inner portion 19a of the additional wall 19 - regardless of their current axial positions - remain sufficiently connected for their function, it is advantageous if both parts - at least rotationally fixed - are interconnected. This can be done for example by means of a shrink connection, riveting or caulking.
• the tightness between the radially outer 19b and the radially inner 19a portion of the additional wall 19 can be ensured by, for example, the portion 19b is pressed against a shoulder of the portion 19a, as shown in Figure 8.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Control Of Fluid Gearings (AREA)
• Mechanical Operated Clutches (AREA)
• Massaging Devices (AREA)
• Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Priority Applications (6)

Applications Claiming Priority (4)

Publications (2)

Family

ID=46045580

Family Applications (1)

Country Status (6)

Cited By (12)

Families Citing this family (11)

Citations (1)

Family Cites Families (11)

• 2006
  • 2006-12-27 DE DE202006020596U patent/DE202006020596U1/de not_active Expired - Lifetime
  • 2006-12-27 WO PCT/DE2006/002317 patent/WO2007079713A2/de not_active Ceased
  • 2006-12-27 EP EP06846948.5A patent/EP1977141B2/de not_active Ceased
  • 2006-12-27 JP JP2008549755A patent/JP5126067B2/ja not_active Expired - Fee Related
  • 2006-12-27 AT AT06846948T patent/ATE449273T1/de not_active IP Right Cessation
  • 2006-12-27 CN CN2006800508811A patent/CN101356389B/zh not_active Expired - Fee Related
  • 2006-12-27 DE DE112006003320T patent/DE112006003320B4/de not_active Expired - Fee Related

Patent Citations (1)

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