US3797243A

US3797243A - Hydraulic torque converter

Info

Publication number: US3797243A
Application number: US00269781A
Authority: US
Inventors: S Trusov
Original assignee: Individual
Current assignee: Individual
Priority date: 1971-07-08
Filing date: 1972-07-07
Publication date: 1974-03-19
Anticipated expiration: 1991-03-19
Also published as: DE2230545A1; DE2230545C3; GB1394874A; FR2145271A5; IT963117B; SU390747A1; PL78100B1; DE2230545B2

Abstract

A hydraulic torque converter is disclosed with a wide passage area and specially selected parameters of the blading of the individual converter wheels which increases considerably the efficiency and power capacity of said converter.

Description

United States Patent 11 1 1111 3,797,243 Trusov Mar. 19, 1974 [54] HYDRAULIC TORQUE CONVERTER 2,663,149 12/1953 2616161 61 a]. 60/362 2,963,867 12/1960 A ia d [76] Inventor serge 11 3,125,857 3/1964 Sc hne ider 60/361 Parkovaya, 44, Korpus 4, kv. 28, Moscow, USSR.

22 Filed; July 7 1972 Primary Examiner-Edgar W. Geoghegan Attorney, Agent, or Firm-Holman & Stern [21] App]. No.: 269,781

[30] Foreign Application Priority Data July 8. 1971 U.S.S.R 1679758 [57] ABSTRACT [52] US. Cl. 60/361, 60/362 A hydraulic torque converter is disclosed with a wide [51] Int. Cl. Fl6d 33/20 passage area and specially selected parameters of the [58] Field of Search 60/361, 362, 330 blading of the individual converter wheels which increases considerably the efficiency and power capac- [56] References Cited ity of said converter.

UNITED STATES PATENTS 2.663.148 12/1953 Jandasek 60/362 10 Claims, 29 Drawing Figures PAIENIEDMAR 19 Ian SHEET 1 0F *8 PAIENIEDMAm m4 SHEET 3 BF 8 NNQQ PATENTEU MAR l 9 i974 SM] 5 BF 8 R mt PAIENIEDMR 1 s 2974 SHEET 7 [1F 8 VF/G100 p ll.

1 HYDRAULIC TORQUE CONVERTER BACKGROUND OF THE INVENTION The present invention relates generally to hydraulic transmissions and more specifically, it relates to the hydraulic torque converters used in the power transmissions of transport vehicles.

The hydraulic torque converter according to the invention can be used most successfully in the power transmissions of automobiles. It ensures optimum working conditions of the engine and is simple in design and reliable in operation.

The hydraulic torque converter is a bladed machine for converting torque. Usually, it comprises an impeller wheel secured to the engine drive shaft, a turbine wheel connected with a driven shaft, and one or two stator wheels.

The impeller, turbine and stator wheels form a closed flow duct or a circulation ring for the moving fluid.

Known in the art are hydraulic torque converters comprising an outflow impeller, an inflow turbine wheel and at least one stator wheel arranged in such a way that a fluid circulating in a closed volume during their rotation forms a flow, the outer boundary of the meridional section of said flow describing an outer torus, while its inner boundary describes an inner torus.

The fluid flows consecutively through the converter wheels, forming a closed hydrodynamic circuit, wherein the flow turns through 360. The wheel blading systems are arranged in immediate proximity to one another so that the fluid inlet conditions of each blading system depend on the outlet flow conditions of the preceding blading system.

The hydrodynamic properties of the hydraulic torque converter depend on the direction and value of velocities in the fluid flow which, in turn, depend on the pa rameters of the flow duct.

A considerable proportion of hydraulic losses in the hydraulic torque converter falls to the vortex formation losses which depend on a number of factors, particularly on the angles of attack measured between the direction of the fluid flow and that of the blade.

The annular shape of the flow duct and the curvature of the blading systems increase the irregularity of the flow.

Any separation boundary is a source of vorticity. The separation boundaries in the flow duct of the hydraulic torque converter are constituted by the exit edges of blades. At the boundaries between the wheels, the conditions of the fluid flow are sharply changed so that the characteristics of the inlet and outlet elements of individual wheels must be coordinated if losses are to be decreased.

The hydraulic torque converters that are in widest use comprise an outflow impeller whose outlet is located on the maximum radius of the circulation ring, an inflow turbine wheel whose inlet is also located on the maximum radius of the circulation ring, and a stator wheel located on the minimum radius of the circulation ring, i.e., nearest to the axis of revolution.

The stator wheel of such hydraulic torque converters is usually installed on an overrunning clutch in order to ensure efficient operation under fluid coupling conditions.

The known hydraulic torque converters of this type, widely used in automobiles and other transport facilities, have comparatively narrow passage areas (see US. Pat. No. 2,410,185 and No. 2,663,148).

In these hydraulic torque converters, the relation of the developed length of the blade along the outer torus (for turbine and impeller wheels) to the developed length of the blade-along the inner torus is from 1.8 to 2.15.

Besides, the blade angle at the impeller inlet in these converters changes from the inner torus to the outer one within comparatively narrow limits, i.e., from 0 to 20. Such characteristics of the blading systems prevent the possibility of increasing the power capacity of the converter, i.e., increasing the power-it transmits at the given dimensions of the hydraulic transmission.

In some cases, it becomes possible to step-up the power capacity of the hydraulic torque converter by selecting the corresponding blade angles in the impeller and stator wheels; however, this reduces efficiency and impairs converting properties owing to increased relative velocities in the blade channels of the hydraulic torque converter.

Also known in the art are hydraulic torque converters with an outflow impeller whose blade edges at the inlet make an angle of 40 to with the axis of revolution in the meridional plane, an inflow turbine wheel whose blade edges at the outlet make an angle of 40 to 60 with the axis of revolution in the same plane, and at least one stator wheel.

The employment of the hydraulic torque converter with such blade angles of the impeller and turbine wheels in the meridional plane is accounted for by the fact that the angles exceeding 60 increase considerably the restriction at the turbine wheel outlet and impeller wheel inlet within the zone adjoining the outer torus which increases losses. At angles smaller than 40, the relative velocities at the impeller and stator wheel inlets grow under the basic operating conditions which also leads to heavier losses.

It follows from the above that the existing blading systems of hydraulic torque converters prevent increasing their power capacity and efficiency at the same dimensions.

SUMMARY OF THE INVENTION An object of the present invention is to provide a hydraulic torque converter capable of transmitting a higher power than the prototype, at a higher efficiency.

Another object of the invention is to provide a hydraulic torque converter which would be adapted for use with engines of various power ratings which is achieved by changing the shape of the converter wheel blades without changing the dimensions of the converter.

These and other objects are accomplished by providing a hydraulic torque converter, comprising an outflow impeller, an inflow turbine wheel and at least one stator wheel, allot these arranged in such a manner that the fluid circulating in a closed volume during their rotation forms a circular flow whose outer boundary'of the meridional section describes an outer torus and the inner boundary of this flow describes an inner torus.

According to the invention, the ratio of the developed lengths of the impeller and turbine wheel blades along the outer torus to the developed lengths of the same blades along the inner torus is from 2.15 to 2.85.

These hydraulic torque converters have wider passage areas.

Such a ratio of the developed lengths of blades along the inner and outer tori proves to be most effective when the entrance edges of the impeller blades and the exit edges of the turbine wheel blades form an angle of 40 to 60 with the axis of revolution in the meridional plane.

It is practicable that the surfaces of the impeller and turbine wheel blades would be generated by the movement of a line along the inner and outer tori so that the relation between the lengths of the sections cut by this generating line on the developed lengths of the blades along the outer torus and the lengths of the sections cut on the developed lengths of the blades along the inner torus would be equal to the relation between the developed length of a blade along the outer torus and its developed length along the inner torus.

Such a design of the impeller and turbine wheel blading systems improves the conditions of the fluid flow which contributes to a reduction in hydraulic losses.

It is also practicable that the relation of the blade angle along the inner torus at the inlet of the converter impeller to the blade angle along the outer torus should be from 1.15 to 1.45.

Correct selection of the blade angles ensures smooth,

impact-free entrance of the flow into the blades which cuts down hydraulic losses.

In one embodiment of the invention, the blade angle at the impeller outlet is fixed while the blade angle at the turbine wheel outlet increases from the outer torus to the inner torus by 5l 0 which is an optimum figure for the flow moving from one wheel into another.

In another embodiment of the invention the relation of the blade angle along the inner torus at the turbine wheel inlet to the blade angle along the outer torus is from 0.5 to 0.9.

Such an arrangement is conductive to a smoother entrance of the flow into the turbine wheel.

The hydraulic torque converter can be realized with the outer torus of the circulation ring in the meridional plane having the shape of a circumference whose ra' dius is 0.317 of the maximum radius of the circulation ring and the inner torus is formed by three arcs whose center coordinates relate to the maximum radius of the circulation ring along the axes of abscissae and ordinates, respectively, as O and 0.733; 0.00809 and 0.742; 0 and 0.757 while the relations of the radii of said arcs to the maximum radius of the circulation ring are 0.115; 0.126; 0.106.

These parameters are selected because the meridional section of the flow duct must have a smooth outline because each sharp transition interferes with the smooth flow of the fluid and involves additional losses.

In another embodiment of the invention, the blade angles of the torque converter along the middle line of the stream may be within the following limits: entrance angle 80 150, exit angle 75150 for the impeller wheel; entrance angle 35-60, exit angle 140- 160 for the turbine wheel, the number of the impeller and turbine wheel blades being 36 and 15-35, respectively.

The minimum losses in the hydraulic torque converter can be obtained at certain blade angles and number of blades in the converter wheels and at a certain arrangement of these blades because these factors influence the fluid flow around the blade profiles.

In still another embodiment of the invention, the relation between the developed lengths of the stator wheel blades along the outer torus to the developed lengths of said blades along the inner torus is from 1.4 to 2.9. I

In the hydraulic torque converter with one stator wheel, the stator wheel blade angles in the middle line of the stream may be 60-l 10 at the inlet and l540 at the outlet, the number of blades ranging from 9 to 23.

A hydraulic torque converter with two stator wheels may have the following blade angles in the middle line of the stream: 115 135 at the inlet and at the outlet of the first stator wheel, 65 90 at the inlet and l540 at the outlet of the second stator wheel, the number of blades in the first and the second stator wheels being 21 35 and 17 33, respectively.

Correct selection of the blading system parameters within the above-mentioned limits ensures a considerable change in the power capacity of the hydraulic torque converter at a sufficiently high efficiency.

BRIEF DESCRIPTION OF THE DRAWINGS Given below is a detailed description of the invention by way of examples with reference to the accompanying drawings in which:

FIG. 1 is a diagrammatic view of the flow duct of a hydraulic torque converter with one stator wheel, meridional section;

FIG. 2 same, with two stator wheels;

FIG. 3a shows the circulation ring of a hydraulic torque converter with one stator wheel, meridional section;

FIG. 3b shows the developed blade lengths of individual converter wheels along the inner torus;

FIG. 30 same, along the middle line of the stream;

FIG. 3d same, along the outer torus;

FIG. 4a shows the circulation ring of a hydraulic torque converter with two stator wheels;

FIG. 4b shows the developed blade lengths of individual converter wheels along the inner torus;

FIG. 4c same, along the middle line of the stream;

FIG. 4d same, along the outer torus;

FIG. 5a is a chart showing the zone of optimum blade angles at the impeller inlet;

FIG. 5b same, at the turbine wheel inlet;

FIG. 6 shows the circulation ring of a hydraulic torque converter, meridional section, an example of implementation;

FIG. 7a shows an impeller blade, a projection on the meridional plane;

FIG. 7b same, a view along arrow A in FIG. 7a;

FIG. 70 same, a development along the outer torus;

FIG. 7d same, a development along the inner torus;

FIG. 8a is a projection of a turbine wheel blade on the meridional plane;

FIG. 8b same, a view along arrow A in FIG. 8a;

FIG. 8c same, a development along the outer torus;

FIG. 8d same, a development along the inner torus;

FIG. 9a shows a blade of the first stator wheel, a projection on the meridional plane;

FIG. 9b same, a view along arrow A in FIG. 9a;

FIG. 9c same, a development along the outer torus;

FIG. 9d same, a development along the inner torus;

FIG. a shows a blade of the second stator wheel, a projection on the meridional plane;

FIG. 10b same, a view along arrow A in FIG. 10a;

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A three-wheel hydraulic torque converter comprises an impeller 1 (FIG. 1), a turbine wheel 2 and a stator wheel 3 installed on an overrunning clutch 4. A four wheel hydraulic torque converter comprises an impeller 1 (FIG. 2), a turbine wheel 2, a first stator wheel 5 and a second stator wheel 6. The impeller 1 is connected with the engine (not shown in the drawing) via the input shaft 7, while the turbine wheel 2 is connected to the output shaft 8.

The impeller l, the turbine wheel 2 and the stator wheel 3 form a closed flow duct or a circulation ring in which the fluid moves, being limited by the outer torus 9 (FIG. 3a) and the inner torus 10.

The impeller l and turbine wheels 2 rotate around an axis 11. In the meridional section of the circulation ring, there is a middle line of the stream 12.

The hydraulic torque converter is characterized by the parameters whose symbols are shown in FIG. 3a.

R maximum radius of circulation ring;

r minimum radius of circulation ring;

angle between direction of blade edge at the inlet of impeller 1 and axis of revolution 11 in the meriodional plane;

115 angle between the direction of blade edge at the outlet from turbine wheel 2 and axis of revolution 11 in the meridional plane;

B blade angle measured between the direction of the blade and the peripheral component of absolute velocity.

If the blade has a curved edge, the angle is measured between the tangent to the blade edge along the middle line of the stream and the axis of revolution in the meridional plane.

The position of the middle line of the stream can be found from the formula \/r,, r where.

r, radius of circulation ring along the inner torus;

radius of circulation ring along the outer torus.

Said radii r and n, can be determined as follows. Draw a line through the meridional section normally to the outer torus 9 and inner torus 10. The distances from the points of intersection of the normal line with the inner and outer tori to the axis of revolution 11 are designated by r and r, respectively.

The blade developments along the inner torus 10, the

middle line of the stream 12 and. the outer torus 9, the blade angles B and the angle designation system are shown in FIGS. 3 and 4. The blade angle B is measured between the direction of the blade and a tangent to the circumference whose center is located on the axis of revolution 11 which means that the blade angle B is measured between the directions of the transfer velocity u and relative velocity w. The blade angles B along the middle line of the stream 12 are designated in accordance with the following system. The first digit denotes the wheel of the hydraulic torque converter: 1 impeller; 2 turbine wheel; 3 stator wheel. The second digit denotes the inlet or outlet part of the wheel: digit 1 stands for the inlet and digit 2, for the outlet. In case of two stator wheels the angles of the first wheel are additionally denoted by a single prime and those of the second wheel, by a double prime. For example, the blade angle B at the inlet of the impeller 1 on the middle line of the stream is designated as B The blade angles along the inner and

outer tori

10 and 9 are denoted by three digits. Two of the digits have been explained above and the third digit indicates the outer or inner torus. Letter a stands for the inner torus and b for the outer one. For example B denotes the blade angle at the inlet of the impeller 1 along the inner torus and B denotes the same angle along the outer torus.

The impeller blade is designed in such a way that the inlet angle B increases from the outer torus b to the inner torus a, the relation of the blade angle B along the inner torus to the blade angle B along the outer torus being B /B 1.15 1.45 where B the blade angle at the inlet of the impeller wheel along the inner torus and B is the same angle along the outer torus.

At the outlet from the impeller 1 the blade angle B changes throughout the height of the blade within narrow limits or remains unchanged.

The entrance angle of the turbine wheel blade B decreases from the outer torus b" to the inner torus a" in accordance with the relation. B /B 0.5 -0.9 where B blade angle at the inlet of the turbine wheel along the inner torus and B blade angle at the inlet of the turbine wheel along; the outer torus. At the outlet from the turbine wheel the blade angle grows from the outer torus to the inner one by 5- 10.

Shown in FIG. 5a and 5b is the zone of optimum blade angles B along the outer torus b" and inner torus a for the impeller l and turbine wheel 2 in accordance with the blade angles B of these wheels along the middle line of the stream 12.

The blades with the characteristics selected within the above-mentioned limits ensure a satisfactory flow not only in the middle line of the stream 12, but also along the extreme lines owing to smaller losses for vortex formation.

Another feature of these blades lies in that their surfaces are developable and generated by the movement of a line, e.g. Aa (FIG. 7a) along two directrices one of which passes along the inner torus l0 and th other one, along the outer torus 9, the relation of the lengths of the sections cut by the directrix on the developed length of th blade along the outer torus 9 to the lengths Y and turbine wheel blades along the outer torus to the developed lengths of the blades of the same wheels along the inner torus 10 is l /l to 2.15 2.85 where:

1,, developed length of the blade along the outer torus;

l developed length of the blade along the inner torus.

The selection of the above-mentioned relationships between the developed lengths of the impeller and turbine wheel blades is based on the following consideration.

At l /l, 2.l the hydraulic torque converters with wide passage areas have an unsatisfactory shape of the flow duct which is accounted for by the impossibility of obtaining the above-mentioned relations between the blade angles at the inlets and outlets of the impeller 1 and turbine wheel 2.

At l /l, 2.85 the flow pattern is irregular and characterized by large velocity gradients which may cause breakway of the flow and increased losses for vortex formation.

The circulation ring of a hydraulic torque converter with wider passage areas and rational parameters is shown in FIG. 6.

The outer torus in the meridional section has the shape of a circumference with a relation of its radius r to the maximum radius R of the circulation ring being equal to 0.317.

The inner torus 9 is formed by the arcs of the circumferences described by three radii. The part of the torus located closest to the axis of revolution 11 is described by the radius r whose relation to the maximum radius R of the circulation ring is equal to 0.1 the middle part is described by the radius r whose relation to the maximum radius R of the circulation ring is equal to 0.126. The part of the inner torus which is farthest from the axis of revolution 11 is described by the radius r whose relation to the maximum radius R of the circulation ring is 0.106 which means that the radius of curvature decreases from the middle of the inner torus 9 to its periphery. The relation of the coordinates of the centers of these radii r r and r., to the maximum radius R of the circulation ring is determined by the values specified below. The axis of abscissae coincides with the axis of revolution 11, whereas the axis of ordinates coincides with the vertical axis (on the drawing) which at the same time is the axis of symmetry of the hydraulic torque converter.

The relations of the coordinates of the centers of these arcs to the maximum radius R along the axes of abscissae and ordinates fo the arcs with radii r r and r are, respectively, 0 and 0.733; 0.00809 and 0.742; O and 0.757.

The hydraulic torque converter realized in this manner features a higher power capacity and its torque coefficient A, is 15-25 percent higher on an average than that of the known converters. Here the torque coefficient A is found from the equation:

M i/7 a "1 J where M torque on the impeller wheel, kgfm;

volumetric weight of the fluid, kgf/m;

D 2R effective diameter of the hydraulic torque converter, m;

n speed of the impeller 1, rpm.

Owing to a high power capacity the hydraulic torque converter is capable of transmitting a power 15-25 percent higher than known converters of the same dimensions and of fixed blade angles at the outlet from the impeller 1 and the stator wheel 3.

To use one and the same hydraulic torque converter (with a fixed circulation ring) with engines of different power ratings, it is necessary to change the converter power capacity which can be achieved by modifying the shape of the blades of its individual wheels.

To solve this problem, the blade angles on the middle line of the stream 12 and the number of blades are selected from the ranges specified in Table 1 below.

TABLE 1 Number Enof trance Exit No. Type of wheel blades angle angle Remarks 1. Impeller 15-36 -150 75-150 2. Turbine wheel 15-35 35-60 140-160 3. Stator wheel 9-23 60-1 10 15-40 Three wheel version 4. 1st stator wheel 21-35 115-135 -1 10 Fourwheel version 5. 2nd stator wheel 15-31 65-90 l540 ditto rsrasmsisyifie maximum efficieii y h of a hydraulic torque converter with an effective diameter D, 340 mm is from 87 to 90; the maximum torqueconversion coefficient K M /M to 2.5-3.2, where M is the torque on the turbine wheel.

With the effective diameter increased to D, 470

mm, the converter efficiency increases by 1.5 to 2 percent and K by 5 to 10 percent.

Existing hydraulic torque converters have different torque coefficients A; which change from 1.8'10 to 4- .010 min /m.rev at i= 0.7, where i= n /n (n speed of turbine wheel 2, rpm).

An example of realization of the blading system of a four-wheel hydraulic torque converter according to the invention with an effective diameter 0,, 340 mm is illustrated in FIGS. 7 through 10. Shown in FIG. 7a is a projection of an impeller wheel 1 superposed on the meridional plane. The angle do; of the blade entrance edge in the meridional plane to the vertical axis is 41 or 49 to the axis of revolution. Shown in FIG. 7b is another projection of the blade, L.H. view (on the drawing) along arrow A. Table 2 gives the coordinates of the blade profile points along the inner 9 and outer l0 tori.

The surface of the blade is developable and is formed by the straight lines passing through the points which divide the developed lengths of the blades along the outer 9 and inner l0 tori so that the generating line cuts such sections on the developed lengths of the blade that the relation 9 l TABLE 2 PointNo- 0 1 2 4 5 5 7 s 0 11 12 of'the lengths of said sections along the outer9 and inner 10 tori is equal to the relation of the total developed length of the blade along the outer torus 9 to the total developed length of the blade along the inner and 8d illustrate the developed lengths of the blade along the inner 10 and outer 9 tori. The blade surface is developable and made by the above-described method. The coordinates of the blade profile points on torus l0. the inner 10 and outer 9 tori, the coordinates of the The coordinates of the points A, B, C, etc. and a, b, points belonging to the generating lines Aa, Bb, etc. as c, etc. which determine the lines forming the blade well as the blade profile thicknesses (b) are summaprofile are given in Table 3. rized, respectively, in Tables 5, 6 and 7.

TABLE 5 PointNo 0 1 2 3 4 5 5 7 8 9 10 TABLE 5 Point symbol A B C D E a b c d e Point Symbol A B C D E a b c d e PomtNm-.. 0 1 2 a 4 5 5 7 8 9 10 11 X 19 19 253 2&7 2% M5 1 2&5 27 m3 6 -.4 5.2 6.5 7.7 8.7 9.5 10 10.2 9.5 7-6 6.25 4.4 Y 5- 155 3 17- 95.7 144.4 139.5 132 124.5 115.3 i tN 2 13 4 15 16 7 1 19 20 21 The thicknesses of the blade profiles are determined by the dimension which is laid off along the chord of the are passing through the coordinated points with the center in point 0 The values of are summarized in Table 4.

Shown in FIGS. 70 and 7d are the developed lengths of the impeller blades along the inner l0 and outer 9 tori, in this case the relation of the blade developed.

length 1,, along the outer torus 9 to the blade developed length 1,, along the inner torus 10 being equal to I /l 2.38.

The blade angles along the middle line of the stream at the inlet and outlet are equal, respectively, to

B

112 and 3, 124. The blade angles at the impeller inlet along the inner 10 and outer 9 tori are equal, respectively, to B 124, B 100 and their relation bine wheel 2 in the meridional plane is inclined at 41 to the vertical axis or at 49 to the axis of revolution.

7115515115 angles along 15511110515555 of the stream 12 at the inlet and outlet are equal, respectively, to B 41 and [3 153. The blade angles along the inner l0 and outer 9 tori at the inlet and outlet are equal to B 34 and B 48; their relation B /B 0.71. The blade angles on the inner l0 and outer 9 tori vat the outlet are equal, respectively, to [3, 157 and Point N0 0 1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 The blade angle at the outlet from the impefier 1'15 constant in height, i.e. B0 2 512 12 124. The number of impeller blades 2. 28.

In FIG. 8a is illustrated a projection of the blade of the turbine wheel 2 superposed on the meridional plane. FIG. 8b shows another projection of the blade, L.l-l. view (on the drawing) along arrow A. FIGS.

""'fri"iiib dl5i1ii torque converter according to the invention, the blade angle at the outlet increases from the outer torus 9 to the inner torus 10 by 5to 10.

The relation of the blade developed length along the outer torus to its developed length along the inner torus is 2.31.

The number of turbine wheel blades 2 24.

Shown in FIG. 9a is a projection of a blade of the 1st stator wheel 3 superposed on the meridional plane. FIG. 9b shows a view along arrow A, while FIGS. 9c and 9d illustrate the developed lengths of the blades The characteristic parameters of the blade are as follows. The blade angles along the middle line of the stream 12 at the inlet and outlet are equal, respectively, to 8 =80 and 3" 24.

blade profiles are summarized, respectively, in Tables 11,12". l3.

along h outer 9 d inner 10 n 5 The inlet angle is constant along the height of the The blade has a developable urface formed the blade, at the outlet diminishes from the Outer abovedescribed h d torus 9 to the inner torus 10, so that [W 26 and i The coordinates of the blade profile points along the "532 The relation of the blade developed length inner l and outer 9 tori, the coordinates of the points along the Outer torus 9 to the Same length along the belonging to the generating lines Aa, Bb, etc. as well 10 inner toms 101$ as the blade profile thicknesses are summarized, re- The number of blades of the 2nd Stator Wheel is spectively, in Tables 8, 9 and 10. The thicknesses b '3 of the blade profiles of the stator wheels are laid off in The functioning of the above'desel'tbed hydraulic. the direction parallel to X-axis. torque converter is identical to that of the known coni TABLE 3 X 0 0.7 1.5 3 4.5 5.5 3.5 11.5 15 17.7 10.3 8.3 7 5 5.5 5 4,5 z 1 7.5 12 17 21.5 26 30 34 3s 41 15 13.3 11.3 8.8 5.3 4.5 1

k TKELE 9 T T verters; however, due to the utilization of the blading Point system parameters according to the invention, it has A B C D E a b c d 6 become possible to reduce considerably the hydraulic x 1 2.8 5.5 9 13.2 5 5.5 6.2 7.3 9 losses and to increase the rate offlow of the fluid in the Z ms 24 36 25 circulation ring at the constant dimensions of the TABLE 10 PointNo "012345678910 111213141515 The characteristic parameters of the blade have the torque converter. This increases the efficiency and following values. The blade angles along the middle power capacity of the hydraulic torque converter acline of the stream 12 at the inlet and outlet are equal cording to the invention. to 8' =125 and [3' 100. The blade angle at the What we claim is: wheel inlet is constant in height, i.e..B'5a1=B'5:n=B'.-n 1- A hydraulic torque converter comprising an out- 125. The blade angle at the outlet is also constant, flow impeller wheel, an inflow turbine wheel and at i.e., 3', B5, [3' 100. The relation of the blade least one stator wheel arranged in such a manner that developed length along the outer torus 9 to that along a fluid circulating in a closed volume during the rotathe inner torus is equal to 2.86. The number of 1st station of said wheels forms a fl ow, the outer bouncE'y tor wheel blades z.'1=26. 40 of the meridional section having a middle line of the In FIG. 10a is shown a projection of a blade of the stream of said flow describing an outer torus while 2nd stator wheel superposed on the meridional plane. its inner boundary describes an inner torus; and blades FIG. 9b shows the blade as viewed along arrow A. The of said impeller and turbine wheels in which the reladeveloped lengths of the blades along the outer 9 and tion of their developed lengths along the outer torus inner 10 tori are illustrated in FIGS. 9c and 9d. The to the developed lengths of the same blades along the surface of the blade is developable and realized by the inner torus i f 2 15 to 2 85 7 method described above. The coordinates of the blade 2. A hydraulic torque converter, according to claim pr fil Points along the inner 10 and Outer 9 tori, the 1, wherein the relation of the blade angle along the ord of the P' belonging to the generating inner torus at the inlet of the impeller wheel to the lines Aa, 317, etc., as Well as the thicknesses b Of the ame angle along the outer torus ranges from to 3. A hydraulic torque converter according to claim TABLE 11 TABLE 12 2 wherein 1115114151155 of the blade angle along the Point inner torus at the inlet of the turbine wheel to the blade symbol-"m A B C D E a b c d 6 angle along the outer torus ranges from 0.5 to 0.9. x 1.3 5.8 13 21 30.4 7 H 16 11 r ue onverter accordin to claim Z 11.2 20.3 27.5 33.3 37.5 5.2 3.5 11.3 12.7 14 4 A l e to 1 e g 3, wherein the blade angle at the outlet from the 1m- TABLE 13 PoimNo 0 1 2 3 4 5 5 7 s 11 10 11 12 13 14 15 10 peller wheel is quite close to constant, while the blade angle at the outlet from the turbine wheel increases from the outer torus to the inner torus by to 5. A hydraulic torque converter according to claim 4, wherein the relation of the developed lengths of the stator wheel blades along the outer torus to the developed lengths of the same blades along the inner torus is from 1.4 to 2.9.

6. A hydraulic torque converter comprising an outflow impeller wheel, an inflow turbine wheel and at least one stator wheel arranged so that a fluid circulating in a closed volume during the rotation of said wheels forms a flow, the outer boundary of the meridional section of said flow describing an outer torus while its inner boundary describes an inner torus; blades of said impeller and turbine wheels are generated by the movement of a line along the inner and outer tori so that the relation of the lengths of the sections cut by this generating line on the developed lengths of the blades along the outer torus to the lengths of the sections cut off on the developed lengths of the blades along the inner torus is equal to the relation of t l 1 e t otal blade developed length along the outer torus to its developed length along the inner torus.

7. A hydraulic torque converter comprising an outflow impeller and an inflow turbine wheel arranged so that a fluid circulating in a closed volume during the rotation of said wheels forms a flow, the outer boundary of the meridional section of said flow describing an outer torus while its inner boundary describes an inner torus; said outer torus of the circulation ring shaped in the meridional plane as a circumference in which the relation of its radius to the maximum radius of the circulation ring is 0.317; said inner torus formed by three arcs in which the relations of their center coordinates to the maximum radius of the circulation ring along the axes of abscissae and ordinates are, respectively: 0 and 0.733; 0.00809 and 0.742; 0 and 0.757 while the relations of the radii of said arcs to the maximum radius of the circulation ring are 0.115,. 0.126 and 0.106.

8. A hydraulic torque converter according to claim 5 wherein the blade angles along the middle line of the stream are within the following limits: inlet angle for the impeller wheel -l50; outlet angle 75-150"; inlet angle for the turbine wheel 3560. outlet angle l40l60 and the numbers of blades of the impeller and turbine wheels are 15-36 and 15-35, respectively.

9. A hydraulic torque converter with one stator wheel according to claim 5 whose blade angles along the middle line of the stream are within the following limits: inlet angle 60-] 10, outlet angle l5-40, the number ofblades 9-23. V l g 10. A hydraulic torque converter with two stator wheels according to claim 5, wherein the blade angles along the middle line of the stream are within the following limits: ll5-l35 and -1 10 at the inlet and outlet of the 1st stator wheel, respectively: 6590 and l5-40 at the inlet and outlet of the 2nd stator wheel, respectively; the numbers of blades of the lst and 2nd stator wheels are 21-35 and 17-33, respectively. g 1 l

Claims

1. A hydraulic torque converter comprising an outflow impeller wheel, an inflow turbine wheel and at least one stator wheel arranged in such a manner that a fluid circulating in a closed volume during the rotation of said wheels forms a flow, the outer boundary of the meridional section having a middle line of the stream of said flow describing an outer torus while its inner boundary describes an inner torus; and blades of said impeller and turbine wheels in which the relation of their developed lengths along the outer torus to the developed lengths of the same blades along the inner torus is from 2.15 to 2.85.

2. A hydraulic torque converter, according to claim 1, wherein the relation of the blade angle along the inner torus at the inlet of the impeller wheel to the same angle along the outer torus ranges from 1.15 to 1.45.

3. A hydraulic torque converter according to claim 2 wherein the relation of the blade angle along the inner torus at the inlet of the turbine wheel to the blade angle along the outer torus ranges from 0.5 to 0.9.

4. A hydraulic torque converter according to claim 3, wherein the blade angle at the outlet from the impeller wheel is quite close to constant, while the blade angle at the outlet from the turbine wheel increases from the outer torus to the inner torus by 5* to 10*.

5. A hydraulic torque converter according to claim 4, wherein the relation of the develoPed lengths of the stator wheel blades along the outer torus to the developed lengths of the same blades along the inner torus is from 1.4 to 2.9.

6. A hydraulic torque converter comprising an outflow impeller wheel, an inflow turbine wheel and at least one stator wheel arranged so that a fluid circulating in a closed volume during the rotation of said wheels forms a flow, the outer boundary of the meridional section of said flow describing an outer torus while its inner boundary describes an inner torus; blades of said impeller and turbine wheels are generated by the movement of a line along the inner and outer tori so that the relation of the lengths of the sections cut by this generating line on the developed lengths of the blades along the outer torus to the lengths of the sections cut off on the developed lengths of the blades along the inner torus is equal to the relation of the total blade developed length along the outer torus to its developed length along the inner torus.

7. A hydraulic torque converter comprising an outflow impeller and an inflow turbine wheel arranged so that a fluid circulating in a closed volume during the rotation of said wheels forms a flow, the outer boundary of the meridional section of said flow describing an outer torus while its inner boundary describes an inner torus; said outer torus of the circulation ring shaped in the meridional plane as a circumference in which the relation of its radius to the maximum radius of the circulation ring is 0.317; said inner torus formed by three arcs in which the relations of their center coordinates to the maximum radius of the circulation ring along the axes of abscissae and ordinates are, respectively: 0 and 0.733; 0.00809 and 0.742; 0 and 0.757 while the relations of the radii of said arcs to the maximum radius of the circulation ring are 0.115, 0.126 and 0.106.

8. A hydraulic torque converter according to claim 5 wherein the blade angles along the middle line of the stream are within the following limits: inlet angle for the impeller wheel 80 - 150*; outlet angle 75 - 150*; inlet angle for the turbine wheel 35-60*, outlet angle 140- 160*and the numbers of blades of the impeller and turbine wheels are 15- 36 and 15 - 35, respectively.

9. A hydraulic torque converter with one stator wheel according to claim 5 whose blade angles along the middle line of the stream are within the following limits: inlet angle 60 - 110*, outlet angle 15- 40*, the number of blades 9 - 23.

10. A hydraulic torque converter with two stator wheels according to claim 5, wherein the blade angles along the middle line of the stream are within the following limits: 115- 135* and 90 - 110* at the inlet and outlet of the 1st stator wheel, respectively: 65- 90* and 15 - 40* at the inlet and outlet of the 2nd stator wheel, respectively; the numbers of blades of the 1st and 2nd stator wheels are 21 - 35 and 17 - 33, respectively.