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
  • F16H41/00—Rotary fluid gearing of the hydrokinetic type
  • F16H41/24—Details
  • F16H41/26—Shape of runner blades or channels with respect to function
• • 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
  • F16H41/00—Rotary fluid gearing of the hydrokinetic type
  • F16H41/24—Details

Definitions

• the invention relates to a torque converter for a motor vehicle according to the preamble of claim 1, wherein the torus shape is to be further improved.
• Torque converters have been known since 1905 (DE 22 14 22 and DE 23 88 04).
• the inventor Foettinger here has a pump and a turbine housed between two shell halves, which are liquid-tightly connected to each other after installation.
• a stator is also arranged.
• the turbine and in the stator blades are arranged, which extend substantially radially.
• the force is introduced into the torque converter in a motor vehicle by the housing of the converter is rotatably connected to the crankshaft of an internal combustion engine.
• the output takes place via the turbine by the transmission input shaft of the following transmission - directly or indirectly - rotatably connected to the hub of the turbine.
• the oil Due to the rotation of the housing - and thus of the pump - the oil is thrown outward by the centrifugal force effect.
• the oil flow within the pump is arcuate. In the radially outer region of the pump, the oil flow is transferred in the axial direction and then flows into the turbine. Due to the power that the oil must perform, the oil flow slows down, as a result of which the flow cross-section in the turbine in the direction of flow must increasingly expand. Since the oil must be redirected to the inflow area of the pump, the outer wall of the turbine is bent towards the inflow area of the pump. Before the oil flow coming from the turbine can get back into the inlet openings of the pump, the oil also flows through the stator.
• the oil flow still undergoes a change in direction, so that the flow of the pump blades is as optimal as possible.
• the oil circuit can then start again. As long as the circuit is maintained and as long as the turbine rotates at a lower speed than the pump, a moment can be transmitted. The more the turbine speed but the pump speed approaches, the worse the efficiency.
• the described form of the pump, the turbine and the stator together form the Toms of a torque converter. The corresponding flow is then a torus flow.
• the term is derived from mathematics, since the rotating oil ring rotates off-axis at the same time about the axis of rotation of the torque converter.
• the lock-up clutch is an important improvement because it can be switched with poor efficiency.
• the power flow then takes place from the rotating housing - directly or indirectly - into the transmission input shaft.
• Another known improvement envisages that rotational irregularities of the crankshaft do not enter the transmission input shaft, that a torsional vibration damper - called damper for short - is installed in the power flow.
• the stator is designed as a diffuser. This means that the cross section between the vanes of the stator widens from the inflow opening in the direction of the outflow opening. This delays the oil in the stator. Since the extension can not be done circumferentially, because otherwise adjacent spaces (which are formed by the neighboring blades) would have to turn out smaller, the extension takes place in the radial direction. CFD simulations have shown that reducing the static pressure in the pump results in more torque converter performance. In order to achieve a reduction of the static pressure in the pump, the oil flow in the pump must be accelerated from the inlet opening to the outlet opening. As a result, the inlet opening of the pump is greater than the outlet opening of the pump.
• the prior art toric mold deviates from the prior art in that it undergoes shear.
• This shear is to be understood as described in the theory of strength shearing, except that in the shaping of the torus' not any shear stresses of importance, but only the deformation itself.
• the torus is designed in such a way that the torus flow is almost circular. This is achieved by using the inner diameter of the stator This is the diameter of the stator hub, which is 0.5 to 0.7 times the outside diameter of the pump.
• Figure 1 shows a prior art of a Toms'
• FIG. 2 shows a toms having outlets and inflow openings of the turbine or pump, which are extended towards the axis of rotation, in comparison to FIG. 1;
• FIG. 3 shows a prior art of a toms
• FIG. 4 shows a toms with enlarged pump diameter in comparison to FIG. 3;
• Figure 5 shows a prior art of a Tom '
• FIG. 6 shows a turbine-side "sheared" tom in comparison with FIG. 5;
• FIG. 7 shows a pump-side "sheared" tom in comparison with FIG. 5;
• Figure 8 shows a prior art of a toms'
• FIG. 9 shows a toms with a diffuser stator in comparison to FIG. 8.
• FIG. 10 shows a prior art of a tom
• the cross section through the toms shown in the figures essentially consists of a pump 1, a turbine 2 and a stator 3.
• the outer contour of the pump 1 is formed by the housing 4.
• the torus rotates about an axis of rotation 5, which is identical to the axis of rotation of the crankshaft of an internal combustion engine.
• the sectional view one sees at the same time also the contours of the arranged in the pump 1, the turbine 2 and the stator 3 blades.
• the blades are curved in space, but this is not recognizable because of the two-dimensional representation.
• the blades of the turbine 2 are arranged in a shell of the turbine, which also represents the outer contour of the turbine blades.
• FIG. 3 shows the state of the art for comparison.
• a step in the housing 4 of the converter and the outer diameter of the turbine 2 corresponds to that of the pump 1.
• the enlarged pump outer diameter 21 ' was possible because the outflow of the oil from the pump 1 into the turbine 2 of the 12 o'clock position in an about
• FIG. 7 a further embodiment of the invention is shown, wherein the figure 5 shows the prior art.
• the housings are shown here more realistically, than in the previous figures, but the indicated axial connection technology in the radially outer region is atypical for series products.
• the connection technology shown is used in the experimental area in order to replace installations of the converter faster and easier.
• the left and the right housing shell are welded together at the circumference. Also missing in these figures, the components lockup clutch and torsional vibration damper.
• FIGS. 6 and 7 the torus is sheared in each case.
• the torus is sheared towards turbine 2.
• the torus is sheared in the direction of the pump.
• the examples of FIGS. 6 and 7 do not show a tilted torus. If the torus were each tilted, instead of sheared, for example, the lowest point of Figure 5 (prior art) between the turbine outlet opening 8 and the stator inlet opening 9 in Figure 6 would be lower than the intersection of the vertical dotted line and the center line C.
• the vertical line is located at the center of the inner stator outlet diameter 14. This is illustrated by the distances a, b, which are both equal.
• the amount S represents the total amount of shear.
• the shear has the advantage that in the figure 6 for internals - for example, a torsional vibration damper - in the radially inner region more space and at the same time the overall length of the converter over the prior art is shorter.
• the maximum available axial space is increasingly a problem for the designers.
• space has been created in the radially outer region. This space is especially needed for a damper, which must accomplish a long travel on the largest possible effective diameter.
• DE 10081340 T1 Fig. 14 and US 4,129,000 Fig. 1 are known torus shapes, which are similar to the present invention, however, there is either no parallelism of the pump outlet opening 6 to the turbine inlet opening 7 disclosed or Parallelism is given, but this transition point is radially formed, but not sheared.
• the stator 3 is provided with a diffuser effect, that is, that when flowing through the oil, the oil is slowed down.
• a diffuser effect that is, that when flowing through the oil, the oil is slowed down.
• This is achieved by making the stator outlet opening 10 larger than the stator inlet opening 9. Since an extension of the cross section between the blades may not take place in the circumferential direction, because then the cross sections between the adjacent blades are reduced, the cross-sectional widening takes place in the radial direction. Therefore, the entry height 17 is smaller than the exit height 16.
• This design has the advantage that in a production of the stator 3 by die-casting, this can be removed from the mold axially.
• the design of the stator 3 as a diffuser also has hydrokinetic advantages.
• the outer ring - which is provided internally with the outer annular boundary surface 19 be designed as a separate ring. This ring can then be pressed by means of pressing on the outer diameter of the stator blades.
• this ring can also be secured by means of a shoulder, a notch or by caulking on the stator blades.
• FIG. 10 a final embodiment of the invention is shown, wherein the figure 10 for direct comparison, the prior art reproduces.
• the hatched narrow areas in the pump 1, the turbine 2 and the stator 3 arise because here the blades are drawn in and these are partially cut by the cutting plane.
• the horizontal lines are used to better compare the sizes.
• the inner stator diameter 14 is displaced radially to the stator diameter 14 '.
• the outer stator diameter 22 is displaced radially outwards to the outer stator diameter 22 '.
• the inner stator passage diameter (14) is preferably 0.5 to 0.7 times the pump outer diameter (21).
• Transducer performance data is typically plotted on a graph of "MP 2000 (Nm)” via “Speed Ratio".
• MP 2000 is the intake torque of the pump in Newton meters at 2000 rpm
• the “Speed Ratio” is the ratio of the turbine speed to the pump speed. Since the turbine speed without converter lock-up clutch is always smaller than the pump speed, this value is also always less in the case of an open lockup clutch.
• the pump torques are below for low speed ratios ( ⁇ 0.5) the values of the prior art. This is particularly advantageous when an internal combustion engine in its lower speed range initially should first be relieved, so it should not be charged to the full extent by driving power. This is particularly important for diesel engines.
• the present invention behaves differently.
• the pump torques are higher than those of the prior art.
• the turbine power is ultimately the power that is passed on to the transmission.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Control Of Fluid Gearings (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• General Details Of Gearings (AREA)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (2)

Family

ID=38175530

Family Applications (1)

Country Status (6)

Families Citing this family (1)

Family Cites Families (26)

• 2007
  • 2007-03-26 DE DE112007000788T patent/DE112007000788A5/de not_active Ceased
  • 2007-03-26 CN CNA2007800133459A patent/CN101421545A/zh active Pending
  • 2007-03-26 WO PCT/DE2007/000548 patent/WO2007118446A2/de not_active Ceased
  • 2007-03-26 KR KR1020087024829A patent/KR20080110804A/ko not_active Ceased
  • 2007-03-26 JP JP2009504558A patent/JP5216976B2/ja not_active Expired - Fee Related
  • 2007-04-12 US US11/786,607 patent/US7634910B2/en not_active Expired - Fee Related

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