US3677004A - Hydrodynamic reversing gear - Google Patents

Hydrodynamic reversing gear Download PDF

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Publication number
US3677004A
US3677004A US87835A US3677004DA US3677004A US 3677004 A US3677004 A US 3677004A US 87835 A US87835 A US 87835A US 3677004D A US3677004D A US 3677004DA US 3677004 A US3677004 A US 3677004A
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Prior art keywords
flow
work
hydraulic liquid
circuit
blades
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Expired - Lifetime
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US87835A
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English (en)
Inventor
Helmut Muller
Gustav Pistl
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Voith Getriebe KG
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Voith Getriebe KG
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    • 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
    • F16H41/04—Combined pump-turbine units
    • F16H41/22—Gearing systems consisting of a plurality of hydrokinetic units operating alternatively, e.g. made effective or ineffective by filling or emptying or by mechanical clutches

Definitions

  • the invention relates to a hydrodynamic reversing gear, more particularly for railway locomotives and is of the type that has at least one pair of hydrodynamic work circuits with toroidal work chambers including bladed impeller and runner wheels. Each circuit of a pair is associated with a different direction of travel.
  • Gears of this type are installed mostly in locomotives intended for shunting or switching service which involves frequent reversals of the direction of travel and traction.
  • This reversal can be achieved more easily, more rapidly and at long term, with greater reliability and with a smaller outlay for maintenance, in a completely hydraulic manner i.e. by filling and emptying corresponding Foettinger work circuits than by mechanical means such as jaw clutches.
  • Locomotives which operate in large marshalling yards, and which are repeatedly required to attain high travelling speeds during service also may profit from the completely hydraulic mode of reversal. They are therefore equipped with a total of four Foettinger convertors, two of which are used for starting and two for continuous travel in the forward and backward direction.
  • the success of this principle-first in fairly small locomotives has resulted in the use for increasingly more powerful locomotives of similar, fully hydraulic, two-speed reversing gears equipped with a total of four convertors.
  • At least that pair of gear work circuits, in which the wheels attain the highest peripheral speed in service, is provided with flow obstructing members movable into the work chamber, and operable at will or automatically by control and/or actuating means.
  • the flow obstructing members are moved into the work chamber associated with the work circuit after the latter has been emptied of hydraulic liquid, and are retracted only when the hydraulic liquid is readmitted to said work circuit.
  • FIG. 1 is an axial sectional view of a two-speed turbo reversing gear incorporating an embodiment of the invention
  • FIG. 2 is an enlarged view of a detail of FIG. 1;
  • FIG. 3 is a fragmentary view taken along line III-III of FIG.
  • FIG. 4 is an enlarged view of a detail of FIG. 2 identified by a dash-dot circle;
  • FIG. 5 is a view similar to that of FIG. 3 showing components in a different arrangement
  • FIG. 6 is an axial sectional view of a convertor incorporating another embodiment of the invention.
  • FIG. 7 is a view similar to FIG. 6, depicting another embodiment of the invention.
  • FIG. 8 is a schematic sectional view taken along line VIII- VIH of FIG. 7;
  • FIG. 9 is a schematic view of a power means associated with the structure according to FIG. 7;
  • FIG. 10 is a view similar to FIG. 8 and depicts a modification of that embodiment
  • FIG. 11 is a schematic sectional view taken along a plane normal to the convertor axis and illustrating still a further embodiment of the invention.
  • FIG. 12 is a fragmentary axial sectional view of a convertor incorporating the embodiment according to FIG. I 1;
  • FIG. 13 is a fragmentary axial sectional view of a convertor incorporating still another embodiment of the invention and FIG. 14 is a fragmentary sectional view along line XIV XIV of FIG. 13.
  • the driving shaft 1 drives, through two spur gears 2 and 3, the central pump wheel shaft 4 on which there are keyed the pump wheels 5 and 8 of the two flow convertors I and II.
  • the two turbine wheels 6 and 9 are rigidly connected to one another by means of a hollow shaft 11 carrying a spur gear 12.
  • the central pump wheel shaft 4 is connected through two spur gears 13 and 14 to a second central pump wheel shaft 15 which carries, in addition to a spur gear 24 for the filling pump drive, the pump wheels 16 and 19 of the flow convertors III and IV.
  • the respective turbine wheels 17 and 20 of the convertors IV and III are rigidly connected to one another by means of a hollow shaft 22 which is integral with a spur gear 23.
  • the two spur gears 12 and 23 on the hollow turbine wheel shaft 11 and 22 mesh with the spur gear 25 mounted on the output shaft 26.
  • the convertors I and III are the low-speed or Starting convertors, while the convertors II and IV are the high-speed or cruising convertors. At any time only a single convertor is filled with hydraulic liquid to thus transmit an output torque.
  • the convertors are provided with flow obstructing means formed of elastic flaps 29 movable in and out of an operative position in the work chamber. These flaps 29 are shown in profile in FIGS. 1-5.
  • FIG. 2 illustrates the use of the flow obstructing elastic flaps 29 in a hydrodynamic convertor having a pump wheel 30 exposed to a throughgoing centrifugal flow, a radially outwardly adjacent turbine wheel 31 and a guide blade ring 32 exposed to a throughgoing centripetal flow.
  • the hydraulic liquid which, when working, circulates meridionally, is guided within the blade rings and in the bladeless spaces by an outer and an inner core ring wall; more particularly, the guide wheel cover disc 33 is drawn well forward at the inlet and outlet and forms a major wall section of the core ring.
  • a wall section located radially outwardly of the cover disc 33 is axially oriented and merges with a large radius into a radial wall section, which is the guide wheel cover disc proper (FIG. 4).
  • thin steel plates 29 are secured to the outer face of the aforenoted wall section in front of the entry into the fin channels by electric spot welds 28.
  • these plates 29 project axially as far as the opposite housing wall and prevent the air, thrown outwardly by the rotating pump wheel, from passing through the guide wheel.
  • the air strikes the plates of flaps 29 projecting into the meridional cross section of the toroidal work chamber and is thus halted in its flow. Due to the stagnation of the air, the otherwise usual air circulation within the work chamber does not occur and consequently no energy is consumed therefor.
  • those areas of the cover disc 33 which are contacted by the deflected flaps 29 should preferably be smooth and curved only unidimensionally. Such areas are indicated in FIGS. 3 and 4 with dashed lines which also designate the inoperative (i.e. flow transmitting) deflected position of flaps 29.
  • FIG. 5 shows how the unidimensional curvature and the smooth surface of the blades themselves are utilized as a contact area for the flaps 29.
  • straight rectangular spring steel plates are electrically spot welded along one side, similarly as shown in FIG. 4, to the rounded head portion of the blades so that the flaps extend tangentially from the rounded head portion and abut against the surface of the opposite blade across the blade channel. Thus, the latter is blocked by the extended flaps.
  • the flaps are deflected out of the blade channel in the flow direction and rest smoothly against the associated blades.
  • the aforedescribed structure constitutes a particularly simple embodiment of the invention, since no separate actuating means are required. Thus, there is virtually no additional weight and the structural outlay is increased only to a very small degree.
  • the flow obstructing means is formed of a cylindrical sleeve 45 surrounding the convertor axis and slidably guided in the convertor housing.
  • the sleeve 45 is held by a plurality of small hydraulic power assemblies disposed in a circular array in the convertor housing about the convertor axis.
  • Each power assembly comprises a hydraulic cylinder 46 and a piston 49 reciprocable therein.
  • Each piston 49 is rigidly secured to the cylindrical sleeve 45.
  • each cylinder 46 there is disposed a spring 47 urging piston 49 into a position in which the sleeve 45 is substantially withdrawn from the work chamber of the convertor.
  • Each hydraulic cylinder is connected in parallel with the pressure chamber of the filling and voiding (emptying valve 48, 50 associated with the convertor.
  • the air flow obstructing means are formed by a rotary plug-like structure constituted by the guide wheel itself.
  • the blades of the guide wheel 52 are divided into a head part 53 and a tail part 54.
  • the tail parts 54 of the guide wheel blades are afi'lxed to the convertor housing.
  • the head parts 53 are combined in a guide blade head ring 55 which is movable with respect to the blade tails in the peripheral direction by at least half a blade pitch.
  • a pin 56 is passed through the guide wheel housing through a slot 60 extending in the peripheral direction.
  • a hydraulic power assembly formed of a cylinder 58 attached to the guide wheel housing at 59, a piston 58" reciprocably held therein, and a piston rod 57 attached to piston 58" at one end and to pin 56 at the other end.
  • the piston 58" may be displaced by a spring 58 disposed in cylinder 58 into a terminal position of rest, setting the guide wheel structure into an air flow blocking position.
  • the piston 58" By applying pressure through conduit 61, to the piston 58", the latter is displaced into another end position in which the air flow obstructing structure of the guide wheel opens so that the latter may perform its normal function associated with the flow of hydraulic liquid.
  • the head parts 53 are shown in a staggered position with respect to the tail parts 54.
  • the head parts which form the flow obstructing means according to the invention, are in their operative (air flow blocking) position.
  • the actuating means for the head parts 53 is in a position shown in FIG. 9.
  • the head parts 53 are aligned with associated tail parts. This is achieved by a rotary motion of small angle of the head parts 53 about the convertor axis, caused by the piston assembly 57, 58" which moves, upon pressurization of conduit 61, the pin 56 to an opposite end of slot 60.
  • conduit 61 Since the conduit 61 is in communication with the work chamber of the convertor, it is pressurized only when the convertor is filled with hydraulic liquid. Thus, the operation of the flow obstructing means is automatic.
  • blade sections from the central part of the blade-divided along concentric dividing lines and combined into pivotable rings- may be slid out of the blade into the adjacent blade channel cross section. If the blade channel is wider in the peripheral direction than the maximum blade thickness, two adjoining movable central blade sections are provided which are mutually independent and pivotable into the adjacent blade channel in the manner illustrated in FIG. 10.
  • the guide wheel blades are identified at 62. Every other blade 62 is pivotally held in an eccentric manner by pin 63 passing through the guide wheel housing. As well seen in FIG. 11, when the pivotable blades 62 are inclined with respect to the non-pivotable blades (position shown in solid lines), the blade channels are blocked. In this position the pivotable blades 62 function as air flow obstructing members. If, on the other hand, the last-named blades assume a position shown in dotted lines, no obstruction to flow exists.
  • a hydraulic motor 64 adapted to turn ring gear 65 arranged coaxially with the convertor axis.
  • a segment gear 66 which meshes with the ring gear 65.
  • FIGS. 13 and 14 the flow obstructing structure shown therein is similar to the embodiment illustrated in FIGS. 1-5 insofar as no separate actuating means are needed to move the flow obstructing members into their operative or inoperative positions.
  • the flow obstructing members according to the embodiment shown in FIGS. 13 and 14 are formed of rigid flaps 70 hingedly secured in the zone of the blade head of the guide blades 71 inside of the converter.
  • each flap 70 there is associated a hinge pin 72 which passes axially parallel through the converter housing and is held rotatably in the housing wall 73 and in the core ring wall 74.
  • Each flap surrounds its associated hinge pin 72 closely with a sleeve-like bent end which-turned inward at an acute angleextends in an axial groove of the hinge pin. In this manner it is ensured that the flap 70 and hinge pin 72 will rotate as a unit.
  • each spiral spring is secured to the ring wall 74 at locations 76.
  • the direction of winding of the spiral spring and the circumferential position of the location 76 are, with respect to the pivotal axis of the hinge pin 72, chosen in such a manner that the spring exerts on the hinge pin a clockwise torque when viewed in FIG. 14. This torque, in turn, tends to rotate the flap 70 in an arc indicated with broken lines in FIG. 14.
  • the advantages of the invention reside in the act that by simple means which have no adverse effect upon the efficiency of the individual convertor, the efficiency of the entire reversing gear is increased since the losses of the empty convertors which rotate in mutually opposite direction on the primary and secondary sides are eliminated. Furthermore, due to the elimination of the windage losses according to the invention, the fully hydraulic reversing gears may be designed for heavier duty which they are capable to perform without inadmissible heating.
  • a hydrodynamic reversing gear particularly for railtype vehicles, said reversing gear being of the type that includes (A) at least one pair of hydrodynamic work circuits, one circuit of each pair being operational for one direction of travel, the other circuit of each pair being operational for the other, opposite direction of travel; each circuit includes a work chamber formed of a circular array of blades of an impeller wheel and a circular array of blades of at least a runner wheel, and (B) means for introducing hydraulic liquid into said work circuits to render them selectively operational and withdrawing hydraulic liquid from said work circuits to render them selectively inoperational, the improvement comprising A.
  • flow obstructing means formed of a plurality of flaps secured in said work chamber, said flow obstructing means being associated with at least one of said circuits and movable into an operative or flow blocking position in the work chamber of said last named circuit and into an inoperative or flow transmitting position and B.
  • resilient means associated with each flap for urging the latter into said flow blocking position; the force of said resilient means being so designed that each flap yields to the flow of hydraulic liquid in the work circuit and moves into the flow transmitting position and each flap, when the work circuit is void of hydraulic liquid, withstands the flow of air in said work circuit and remains in said flow blocking position.
  • a hydrodynamic reversing gear particularly for railtype vehicles, said reversing gear being of the type that includes (A) at least one pair of hydrodynamic work circuits, one circuit of each pair being operational for one direction of travel, the other circuit of each pair being operational for the other, opposite direction of travel; each circuit includes a work chamber formed of a circular array of blades of an impeller wheel and a circular array of blades of at least a runner wheel, and (B) means for introducing hydraulic liquid into said work circuits to render them selectively operational and withdrawing hydraulic liquid from said work circuits to render them selectively inoperational, the improvement comprising A.
  • flow obstructing means formed of at east one portion of at last some of the blades associated with a wheel, said flow obstructing means being associated with at least one of said circuits and movable into an operative or flow blocking position in the work chamber of said last-named circuit and into an inoperative or flow transmitting position, each blade of the wheel containing said flow obstructing means being divided along at least one dividing circle into at least two portions movable with respect to one another in a circumferential direction to an extent equalling approximately one-half the distance between two adjacent blades and B. actuating means for moving said flow obstructing means into the flow blocking position when said work chamber is voided of hydraulic liquid and into the flow transmitting position upon introducing hydraulic liquid into said work circuit.
  • a hydrodynamic reversing gear particularly for railtype vehicles, said reversing gear being of the type that includes (A) at least one pair of hydrodynamic work circuits, one circuit of each pair being operational for one direction of travel, the other circuit of each pair being operational for the other, opposite direction of travel; each circuit includes a work chamber formed of a circular array of blades of an impeller wheel and a circular array of blades of at least a runner wheel, and (B) means for introducing hydraulic liquid into said work circuits to render them selectively operational and withdrawing hydraulic liquid from said work circuits to render them selectively inoperational, the improvement comprising A.
  • flow obstructing means formed of at least some of the blades associated with a wheel, said flow obstructing means being associated with at least one of said circuits and movable into an operative or flow blocking position in the work chamber of sad last-named circuit and into an inoperative or flow transmitting position, each blade forming said flow obstructing means being pivotable in the circumferential direction and abutting, in its flow blocking position, two immediately adjacent blades in said wheel and B. actuating means for moving said flow obstructing means into the flow blocking position when said work chamber is voided of hydraulic liquid and into the flow transmitting position upon introducing hydraulic liquid into said work circuit.
  • a hydrodynamic reversing gear particularly for railtype vehicles, said reversing gear being of the type that includes (A) at least one pair of hydrodynamic work circuits, one circuit of each pair being operational for one direction of travel, the other circuit of each pair being operational for the other, opposite direction of travel; each circuit includes a work chamber formed of a circular array of blades of an impeller wheel and a circular array of blades of at least a runner wheel, and (B) means for introducing hydraulic liquid into said work circuits to render them selectively operational and withdrawing hydraulic liquid from said work circuits to render them selectively inoperational, the improvement comprising A.
  • flow obstructing means formed of a cylindrical sleeve axially slidably held coaxially with said wheels, said flow obstructing means being associated with at least one of said circuits and movable into an operative or flow blocking position in the work chamber of said last-named circuit and into an inoperative or flow transmitting position and B.
  • actuating means for moving said flow obstructing means into the flow blocking position when said work chamber is voided of hydraulic liquid and into the flow transmitting position upon introducing hydraulic liquid into said work circuit, said actuating means including 1. spring means urging said cylindrical sleeve into one of said positions, 2. power means overcoming, when energized, the force of said spring means to move said cylindrical sleeve into the other of said positions and 3. means for energizing and de-energizing said power means simultaneously with the introduction of hydra ulic liquid into and the withdrawal of hydraulic liquid from the work circuit.
  • each flap is made of a resilient material, the resiliency of which constitutes said resilient means.
  • said actuating means includes A. spring means urging said portions constituting said flow obstructing means into said flow blocking position and B. means operatively connected with said means for introducing hydraulic liquid into and withdrawing the same from the work circuit, for moving said flow obstructing means into said flow transmitting position against the force of said spring means automatically when hydraulic liquid is introduced into the work circuit, and allowing said flow obstructing means to move into said flow blocking position under the force of said spring means automatically when hydraulic liquid is withdrawn from said work circuit.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Fluid Gearings (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Hydraulic Motors (AREA)
  • Hydraulic Turbines (AREA)
US87835A 1969-11-08 1970-11-09 Hydrodynamic reversing gear Expired - Lifetime US3677004A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1956244A DE1956244C3 (de) 1969-11-08 1969-11-08 Hydrodynamisches Wendegetriebe

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US3677004A true US3677004A (en) 1972-07-18

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US87835A Expired - Lifetime US3677004A (en) 1969-11-08 1970-11-09 Hydrodynamic reversing gear

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US (1) US3677004A (de)
JP (1) JPS4948910B1 (de)
DE (1) DE1956244C3 (de)
FR (1) FR2066174A5 (de)
GB (1) GB1319843A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4099426A (en) * 1975-08-22 1978-07-11 Voith Getriebe Kg Hydrodynamic transmission for vehicles
US4184330A (en) * 1977-09-12 1980-01-22 Voith Getriebe Kg. Hydrodynamic reversing transmission
US4255957A (en) * 1978-11-16 1981-03-17 Davydov Vadim A Machine for multidie nonslip drawing of wire products
US6408621B1 (en) * 2000-09-11 2002-06-25 Engineered Dynamics Corporation Fluid coupling assembly
WO2005039952A1 (en) * 2003-09-24 2005-05-06 Express Service Ood Locomotive for shunting of rolling stock
US20070000349A1 (en) * 2005-05-04 2007-01-04 Maguire Alan R Drive arrangement
US9267591B2 (en) * 2011-06-24 2016-02-23 Honda Motor Co., Ltd. Torque converter stator structure

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3702548A1 (de) * 1987-01-29 1988-08-11 Ford Werke Ag Hydrodynamischer drehmomentwandler, insbesondere fuer kraftfahrzeuge
DD292424B5 (de) * 1990-03-12 1996-09-05 Smi Stroemungsmaschinen Indust Stroemungswendegetriebe fuer Lokomotiven insbesondere fuer Rangier-Diesellokomotiven

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2063471A (en) * 1932-02-01 1936-12-08 Stedefeld Curt Multistage hydraulic coupling
US2347121A (en) * 1939-06-09 1944-04-18 Chrysler Corp Fluid coupling
US2464215A (en) * 1946-01-05 1949-03-15 Ralph L Copeland Adjustable hydraulic turbine transmission
US2627724A (en) * 1950-05-20 1953-02-10 Frederick W Seybold Rotary, multiple turbine hydraulic coupling
US2835470A (en) * 1956-02-17 1958-05-20 Piessey Company Ltd Fluid turbines
US3029902A (en) * 1957-07-31 1962-04-17 Heenan & Froude Ltd Hydro-kinetic brakes and couplings

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2063471A (en) * 1932-02-01 1936-12-08 Stedefeld Curt Multistage hydraulic coupling
US2347121A (en) * 1939-06-09 1944-04-18 Chrysler Corp Fluid coupling
US2464215A (en) * 1946-01-05 1949-03-15 Ralph L Copeland Adjustable hydraulic turbine transmission
US2627724A (en) * 1950-05-20 1953-02-10 Frederick W Seybold Rotary, multiple turbine hydraulic coupling
US2835470A (en) * 1956-02-17 1958-05-20 Piessey Company Ltd Fluid turbines
US3029902A (en) * 1957-07-31 1962-04-17 Heenan & Froude Ltd Hydro-kinetic brakes and couplings

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4099426A (en) * 1975-08-22 1978-07-11 Voith Getriebe Kg Hydrodynamic transmission for vehicles
US4184330A (en) * 1977-09-12 1980-01-22 Voith Getriebe Kg. Hydrodynamic reversing transmission
US4255957A (en) * 1978-11-16 1981-03-17 Davydov Vadim A Machine for multidie nonslip drawing of wire products
US6408621B1 (en) * 2000-09-11 2002-06-25 Engineered Dynamics Corporation Fluid coupling assembly
WO2005039952A1 (en) * 2003-09-24 2005-05-06 Express Service Ood Locomotive for shunting of rolling stock
US20070000349A1 (en) * 2005-05-04 2007-01-04 Maguire Alan R Drive arrangement
US7533526B2 (en) * 2005-05-04 2009-05-19 Rolls-Royce Plc Drive arrangement
US9267591B2 (en) * 2011-06-24 2016-02-23 Honda Motor Co., Ltd. Torque converter stator structure

Also Published As

Publication number Publication date
GB1319843A (en) 1973-06-13
DE1956244B2 (de) 1973-06-20
DE1956244C3 (de) 1974-01-10
FR2066174A5 (de) 1971-08-06
DE1956244A1 (de) 1971-05-13
JPS4948910B1 (de) 1974-12-24

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