DE2210543A1 - Hydrodynamic torque converter - Google Patents

Description

Dipl.-Ing. W.Heyer Dipl.-Wir bsch. -ing. Ii. JQ «hom

Ο FrankL'urt am Main Freiherr-vom-Stoin-Str.

In matters:

SRM Hydromekanik AB
Stockholm-Vällingby
Sweden

Hydrodynamic torque converter

The invention relates to hydrodynamic torque converters with four in a toroidal flow circle Blade rings arranged within a Vandler chamber, namely a pump blade ring, a first and a second turbine vane ring and one between this arranged guide vane ring, wherein the second turbine blade ring and / or the pump blade ring of a radial section of the flow circuit in the transition section following in the direction of flow reach in or reach in.

Hydrodynamic torque converters are now very sophisticated Gear units, both in terms of their performance and the refined processes for their manufacture. Make a blond problem however, the high manufacturing costs incurred on a large number of different tools and devices still remain to produce the many different ones corresponding to the various conditions of practice Converter designs are based. Attempts have been made to improve the performance and the area in which the converter works with good efficiency, to widen and changes to the paddle system for adaptation in the practical individual case to as few as possible

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SRH 8188 / 3.3.1972

Restrict parts. Nevertheless, the task remained until now unsolved, not just the mm once to adjust the converter changes required to specified operating conditions of the shovel system to the smallest possible extent limit, but also at the same time the production costs for these changes to be reduced to a minimum value.

Changes to the blade system of hydrodynamic torque converters are problematic in that any change to one blade ring affects the flow throughout Has circulation. It is therefore often necessary to make several changes at the same time. On the other hand, you can also changes at a specific point in the paddle system Help eliminate errors in a completely different place. This is explained below using an example:

In order to reduce manufacturing costs, efforts are made to use as wide a Ms range as possible (Hs = specific moment) to use the same pump wheel and only change it by removing the outer circumference of the pump blade ring, the the position of the pump outlet determines more or less far is turned off. The width of the area within which the same impeller can be used depends on how far the pump outlet can protrude into the outer transition section of the toroidal working chamber without the higher losses normally caused by this at the inlet of the first turbine stage reduce the efficiency unacceptably permit.

The flow conditions at the pump blades and at the inlet the first turbine stage can be adjusted by changing the outflow angle to match the position of the pump outlet influence the second turbine stage in a favorable manner in such a way that the pump outlet without greater reduction the efficiency can be advanced further to the first turbine stage. However, the desired © Correction of the flow mostly only through an individual case adapted double curvature of the blades of the second door SRH 8188 / 3.3.1972? r9838/0855

BATH

Achieve bine level, \ -: ns high manufacturing costs with π: i yields. Rich avoided these for the individual blades by using precision casting in the wax casting process. Because of the still required ^e ftontage however, turbine wheels, in which the blades are integrally formed with a support ring or flange, preferable "Such work would be for lost wax too large to be made to more economically to.

Production by machining is also uneconomical. Casting processes in which mold cores are used are ruled out because the accuracy required is different can not be reached in this way. In the case of blade systems with only single curved blades, it is also already known manufacture the paddle wheels by injection molding or pressure molding, removing them without destroying the shape of this can be. The advantage of the simpler and cheaper manufacturability of paddle wheels with only single curved ones Blade blades, however, have the disadvantage that a second turbine stage designed in this way does not as well as one with double-curved blades can be modified to accommodate a change in the diameter of the Compensate for the pump outlet.

In addition to the aforementioned compensation for the effects of a displacement of the pump outlet, a change in the outflow angle of the second turbine stage adapted to the specific individual case is basically suitable for favorably influencing losses in the flow circuit, which can have various causes. Irregularities in the flow and thus losses are z. B-. also due to the fact that the flow velocity is usually greater near the core of the converter chamber than at its periphery, where the flow path for the working fluid is greater. Also this eyt the flow cross section related non-uniformity of flow velocity can by proper selection of the ex-

SRH 8188 / - 3.3.1972 2 0 9 8 3 8/0 8 S S

counteracted flow angle of the second turbine stage are, for which, however, their blades usually have to be double-curved.

With the change in the speed ratio between ^ pump and turbine when starting up as well as during operation until the maximum speed is reached, the angle changes, under which the flow in the converter meets the first turbine stage. It is generally true that the losses The greater the angle of incidence deviates from its optimum value. This deviation range is but now with a flow velocity which is uneven over the flow cross-section, it is naturally much greater than in the case of a steady flow, whereby it remains to be seen what the unevenness is due to is, for example, an unfavorable position that has not been compensated for by inadequate adaptation of the second turbine stage of the pump outlet.

Finally, in some cases, the flow conditions in the converter chamber and thus improve the efficiency and performance of the converter in that not only is the pump outlet displaced by the known turning off of the blade ends, but also the outflow angle the pump blades is changed.

On the basis of the foregoing, the inventor set himself the task of developing a torque converter of the initially to create the type mentioned, which largely influences the flow conditions in the converter chamber Change of the outflow angle on the second turbine blade ring and / or on the pump blade ring when using only relatively easy and cheap to manufacture parts of the blade system allowed.

The above object is achieved according to the invention in that the blades at least one in the transition section reaching blade ring are executed divided and made

SRH 6188 / 5.3.1972 _{203838 / 08S5} ;

One each per week within the. radial circulation; -section front, singly curved blade part and one located essentially in the transition part exist rear Gschaufeltell, the outflow angle changes along the transverse extent of the blades in the flow circuit. In an advantageous embodiment of the invention the rear blade parts are curved twice.

The invention enables a very simple production of both blade parts of each one executed in a divided manner Blade ring even with three-dimensional or double-curved blades with the same success in loading, on influencing the flow as with a one-piece paddle wheel. The front ones are used for this Blade parts primarily for torque transmission, while the rear blade parts influence the flow. Given this distribution of tasks, they are more advantageous Further development of the invention, the front, only simply curved blade parts, as in the case of one-piece Known paddle wheels, preferably formed in one piece with a wheel body carrying them. The production such paddle wheels can be injection or pressure molding, So cheap without the use of mold cores and yet very precisely using one and the same mold for a large one A number of converter designs that meet the most varied of conditions are made, whereby it is advantageous the front blade parts creating a draft to be conical in the direction of the blade axes.

In contrast, the rear blade parts are after a Another feature for the advantageous embodiment of the ■ invention expediently made in one piece with an inner and / or an outer support ring, and the various for modification the shovel system required embodiments accordingly in smaller numbers as well

SRH 8188 / 3.3.1972

20 98 38/0 8B 5 «ettNAUN» Ki »

manufactured as a cast workpiece, the manufacture for example in precision casting using the wax exchange melSH Procedure can be done. Such a design of the rear blade parts and one is particularly advantageous such an arrangement of the same on the ring carrying them b ^ sw. the rings that support it so that it is projected onto a plane normal to the Vandler axis, because then the production of this part is even possible in a divided permanent mold by injection molding or die casting This is still proportionate, even if there is a need for subsequent machining cheap component is the only one that is different in the special application case for modifying the blade system must be shaped.

The more or less wide turning of the pump blades falls practically negligible, due to the simplified possibility of changes in the flow conditions Correcting pump blades of different lengths in profile, and the large scope made possible by the invention such a correction can according to a special feature for an advantageous development of the invention of the Pump vane ring at least partially with a part of the inner core of the transducer chamber and the toroidal one The flow circuit can also be designed in one piece in the side ring delimiting the outer transition section

The invention thus provides a torque converter that without changes to the greater part of its components, covers a wide field of application and in all cases of application as a result of the optimally adjustable flow conditions With the dimensional accuracy of the blades, an excellent level of efficiency under all operating conditions Has. The opened up by the division of the blades at the same time precise and yet cheap manufacturing processes in connection with the now opened possibility of most of the üchaufelcy .'- itomü in large pieces-

209838/0855 _t

Figures to manufacture lead to a far better drainage expensive tools and devices and with one no considerable lowering of the porti gunyrjkor.ton i "wr rion cinwoinen Converter

The invention is explained in more detail below with reference to the drawing. It show: ♦

Pig · 1 shows an axial section through one according to the invention trained hydrodynamic torque converter,

Pig 2 the upper half of an axial section through the Turbine wheel of the converter with the front part of the blades of the second turbine stage,

Pig. 2A is a front view of a quadrant of the turbine wheel in the direction of arrow 2 A in Fig. 2,

FIG. 3 shows the individual representation of a front blade part from FIG. 2, with those drawn therein Longitudinal and cross-sectional lines,

Fig. 3A longitudinal and cross sections through the front

u 3B

Blade part according to FIG. 3 according to the there

Cutting lines,

Fig. 4 in a front view of a sector of the share of the second blade of the second. Stage turbine vane ring formed, ^-

4A shows an axial section through such a blade ring, .

SRH 8188 / 3.3.1972

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Fig. 4B, sections along line BB, CC or DD according to ^{4C U} - ^4D Fig. 4,

Fig. 5, sections through two blades each of the puftipen

5A 5B

'cp, blade ring, of the first turbine blade

ring, the vane ring and the second turbine blade ring according to the correspondingly designated cut lines in Fig. I ₁ wherein the blades of the second turbine blade ring are integrally formed in a conventional manner,

Fig. 6 show simplified sectional views similar to Fig. ^U * Fig. 5A, in a further enlargement to illustrate the flow conditions, and

7 shows a diagram to illustrate the at the various angles of attack on the blades losses of flow energy occurring in the first turbine stage.

The transducer shown in axial section in FIG. 1 has a rotatable, divided housing 1 which encloses a toroidal chamber 2 for a working fluid. The converter chamber thus encloses a flow circuit with a radially outwardly directed part 2Λ, an outer transition section 2B, a radially inwardly directed part 2C and an inner transition section 2D, as the correspondingly labeled arrows in FIG. 1 illustrate. The arrows indicate the direction of flow of the working fluid, but not the exact extent of the aforementioned sections, which of course merge into one another without a sharp boundary. A spline IA is used to couple the housing 1 to a drive machine (not shown).

SRH iron / 3.5.1972 _{209838 / m6}

Inside the transducer chamber are located in the radia] nach outward part 2Λ of the flow circuit Pump blade ring P and in the radially inwardly directed Part IC of the flow circuit is a first turbine blade ring Tl, ei ^ guide vane ring G and a second Turbine blade ring, its blades from front Blade parts T2M and rear blade parts T2ft put together.

DLe bucket blades of the pump bucket crane P are in one Piece cast with the front half IB of the converter housing 1 and by means of screws 2E with a ring part 3A inner core connected.

The blades of the first turbine blade ring Tl are cast in one piece with a ring element TlA, and Ln similar .Weise are the blades of the guide vane ring G and the front parts of the airfoils of the second turbine blade ring T2M in one piece with they cast bearing wheel bodies GA or T2A. The information sheets of the first turbine blade ring Tl are means Screws TlB attached to another ring part 3B of the inner core, which in turn is attached to the front airfoil parts T2M of the second turbine stage is screwed. In the end are the blades of the vane ring G on a third ring part 3C of the inner core by bolts attached.

Hear dlo in front of it. '! Eh. mi "ο I hl .iil.l fill ο T. ' ¹ H <l <! R.: '. WoiUmi turbine blade sick; Lr.Hjoiulo wheel body TPA ί>' ιΙ. ·, · .1. Mil: a viol "nut connection 4 non-rotatably on a wear life shaft O, which, among other things, by means of a roller bearing ^ is mounted in a (not shown) stationary housing. The output shaft O is enclosed by a hollow shaft 6, on which the wheel body CA for the guide vane ring G by means of a multi-groove connection

SRH 8188 / 30. 12.

6A is attached. The free ends of the guide vane}! are by a further RLngteil ^ D de; Core.s connected to each other. On the hollow shaft 6 sits a roller bearing 7, the outer race, the rear half 1G of the split housing 1 carries. Furthermore, there is a ring gear 8 with teeth 8A against the outside of the rear housing half 1C screwed and sealed against the hollow shaft 6 by means of suitable seals.

As FIG. 1 further shows, the front airfoil parts T2M extend the second turbine airfoil in the radially inwardly directed part 2C of the flow return circuit, and their end edges are in a plane perpendicular to the axis of rotation of the Abtricbswello 0. The rear Airfoil parts T2N are in one piece with an outer ring T2 and an inner ring T2- cast. The inner surface of the, Outer ring T2 and the outer surface of inner ring T2-fit the shape of the toroidal flow circuit within the converter chamber 2.

The design and arrangement of the front and rear airfoil parts T2M or T2N of the second turbine blade ring 2, 2A, 3, 3A and B and 4-, 4A, 4B, 4-C and 4-D in detail.

Fig. 2 shows in longitudinal section one half of the wheel body T2A of the second turbine blade ring with the front Blade parts Τ2ΓΊ, on which pins T2M 'for riveting are integrally formed with the ring part 3B of the inner core · The Wheel body T2A has on its hub an annular surface T2R delimited by a flat shoulder surface to accommodate the rear airfoil parts T2N connecting inner ring T2 ^ (See also Figs. 4- and 4-A). The front view on the wheel center T2A in Fig. 2A leaves the two-dimensional shape of the anterior Blade parts T2M, which are also known as simple curvature can recognize. Figures 3, 3A and 3B illustrate the shape of the two-dimensional front blade

SRII 8188 209838/0855

- li -

Leaf parts T2M with the help of the various sectional views even clearer.

FIGS. 4 - 4D show the rear part T2N of the second turbine blade ring in detail. In the sectional views 4B, 4C and 4D corresponding to the section lines BB, CC, DD in Fig. 4, the outflow angle od and the small distance b between adjacent blades or, in other words, the narrowest part of the flow channel between the blades are shown. Both V / er te ⁰ ^ and b are different at the considered interfaces. For example, the angle oL at the interface BB (FIG. 4B) is 55 °, at the interface CC (FIG. 4C) 58 ° and the interface DD (FIG. 4D) is 63 °.

In FIGS. 5-5C, in which, as already mentioned, the second turbine blade ring is shown with one-piece blade blades, the outflow angles OC and the small distances b between the adjacent blade blades of the individual blade boundary are shown again. In addition, in FIGS. 5A, 5B and 5C the directions of flow of the working fluid are shown with I, the suffixes rrb representing the direction of flow when the two interconnected turbine blade rings are at a standstill and sh when the turbine blade rings are synchronized with the pump blade ring. The angle ι * between the directions of flow at a standstill and in synchronism thus denotes the operating range within which the direction of flow varies when the converter is started up until synchronism is reached, in which the converter is usually switched to direct drive. Furthermore, the optimal direction of flow is drawn with Io, for which the respective blade

SRH 8188 / December 30, 1971

209838/0855

leaf profile is designed and in connection with the outflow direction determined by the outflow angle ex the so-called Characterized deflection angle of the airfoil profile.

In the figures explained last, especially FIG. 5A, the directions of flow shown are only valid in a special sectional plane through the blade, as indicated in FIG. 1, for example aa, bb or cc. In reality, the directions of flow, viewed over the transverse extent of the blades, vary considerably in the previously known converters without correcting the flow through the second turbine blade ring, as is shown in FIG. 6 for. deh first turbine blade wreath illustrated. There, the directions of flow with dom suffix _st are at standstill and - in contrast to the designation in FIGS the sectional planes aa, bb and cc of FIG. 1 are shown. The angles y between the respective direction of flow are also provided with the indices a, b, c at a standstill and in synchronism. Since the flow directions at standstill or in synchronism are different in the individual cutting planes, an angle γ results for the airfoil profile of the first turbine blade ring in question between the flow direction which deviates the most from the optimum value and the flow direction which deviates the most from the optimum value in synchronism " total, which is much larger than the individual angles y , jx and y .

The diagram in Fig. 7 illustrates the losses of flow energy occurring on such a blade ring as a function of the angle of attack / 3 , which the flow direction to the tangent on the circumference of the blade.

20 9 8 38/0855

includes wreath on the flow inlet side. As the drawn angle range J>. . , shows, are these losses are very large immediately after start-up and increase again considerably before synchronization is reached at. »

As a result of the correction of the flow conditions Ln of the converter chamber made possible in a simple manner according to the invention, the angular range If,. , are significantly reduced by the fact that the extreme rushing directions, both at a standstill and in synchronism, are almost comparable over the entire transverse extent of the blades. Like Pig. As can be seen, the losses of flow energy drop considerably immediately after starting up and before reaching synchronization.

209838/0855

Claims (13)

Expectations Hydrodynamic torque converters with four »in a toroidal flow circuit within a converter chamber arranged blade rings, namely a pump blade ring, a first and a second turbine blade ring and one between this arranged guide vane ring, v / above the second turbine blade ring and / or the pump blade ring from a radial section of the flow circuit in the following overflow in the direction of flow; pass in or reach into the gangsabschni.tt, characterized in that the blades at least one into the transition section (2D) reaching blade ring (T2) are executed divided and each one essentially within of the radial circuit section (2C) located front, simply curved blade part (T2M) and a substantially in the transition part (2D) located rear blade part (T2N) exist, the outflow angle (o * ·) along the transverse extension the blade changes in the flow circuit. 2. Torque converter according to claim 1, characterized in that the rear Blade parts (T2N) are double curved. 3. Torque converter according to claim 1 or 2, characterized in that the outflow angle (ot) of the rear blade parts (T2N) changes in such a way that the entry angle of the flow (entry direction I) over the transverse extent of each leading edge in the flow. cycle with the various blade rings (P, Tl, G, T2) is at least approximately the same as SRH 8188 / December 30, 1971 209838/0855 4. Torque converter according to one of claims 1 - 3 _f, characterized in that the front blade parts (T2M), seen in the flow direction, in \ i / essential within a radial part (2C) of the flow circuit and the rear blade parts (T2N) in the i Extend essentially only within a transition section (2D) of the flow circuit. 5 · Torque converter according to claim 4, characterized in that the front Blade parts (T2M) in one piece with a they carry, the wheel body (T2A) are formed. 6. Torque converter according to claim 5, characterized in that the front Blade parts (T2M) with the creation of a draft for production in the casting in the direction the blade axes are conical 7 · Torque converter according to one of claims 4-6, characterized in that the outlet edges of the rear vane parts (T2N) at the radially innermost or radially outermost point of the relevant transition section (2D) of the flow circuit are arranged. 8. Torque converter according to one of the preceding claims, characterized in that that the rear blade parts (T2N) are integral with an inner and / or an outer ring (T2. Or T2) are formed. 9. Torque converter according to claim 8, characterized in 'SRH 8188 / 30. 12. 1971 209838/0855 marked that the rear Blade parts (T2N) and the ring or the rings carrying them (T2., T2) are cast l a pieces are. 10 · Torque converter according to claim 9 »thereby characterized in that the rear blade parts (T2N) are formed in such a way and in one such a circumferential distance on the ring or the rings (T2., T2) carrying them are arranged so that they lie on a normal to the transducer axis Projected plane, not covering it. 11. Torque converter according to claim 5 and claim 9 or 10, characterized in that the rear blade parts (T2N) via their support rings (T2-, T2,) between the associated front blade parts (T2M) bearing wheel center (T2A) and a ring part (JB) of the inner core of the transducer chamber running around it in this way are braced that the leading edge of the rear blade parts (T2N) the end edges of the front blade parts Cover (T2M) in pairs. 12. Torque converter according to claim 11, characterized characterized in that the rear blade parts (T? N) are integral with them Support rings (T2 ^, T2) both with the associated front blade parts (T2M) carrying wheel body (T2A) as with the core ring part rotating with this (3B) are non-rotatably connected. 13. Torque converter according to one or more of the preceding claims, characterized in that the pump blade ring (P) at least partially with a part of the inner SRH 8188 209838/0855 The side ring (3Λ) which forms the core of the converter chamber and which delimits the toroidal flow circuit also in the outer transition section v'2B) are formed in one piece. * 2 0 9 8 3 «/ d y t) υ At Blank page