US3792585A - Hydraulic coupling - Google Patents

Hydraulic coupling Download PDF

Info

Publication number
US3792585A
US3792585A US00220249A US3792585DA US3792585A US 3792585 A US3792585 A US 3792585A US 00220249 A US00220249 A US 00220249A US 3792585D A US3792585D A US 3792585DA US 3792585 A US3792585 A US 3792585A
Authority
US
United States
Prior art keywords
guide wheels
accordance
pair
vane ring
hydrodynamic coupling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00220249A
Other languages
English (en)
Inventor
S Eisenmann
H Harle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FURSTLICH HOHENZOLLERNSCHE HUTTENVERWALTUNG DT
HOHENZOLLERN HUETTENVERWALT
Original Assignee
HOHENZOLLERN HUETTENVERWALT
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by HOHENZOLLERN HUETTENVERWALT filed Critical HOHENZOLLERN HUETTENVERWALT
Application granted granted Critical
Publication of US3792585A publication Critical patent/US3792585A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S60/00—Power plants
    • Y10S60/912—Cooling means

Definitions

  • ABSTRACT This invention relates to an improvement in a hydrau lic coupling operating according to the Foettinger principle, with a turbine vane ring and a pump vane ring mounted axially adjacent thereto within a housing, and wherein there is assigned to each of the two vane rings a reversing wheel rotating concomitantly therewith and being open toward the other vane ring, the improvement comprising means for varying the distance between the two vane rings.
  • the present invention relates to a hydraulic coupling operating in accordance with the Foettinger principle, comprising a turbine vane or bucket ring, and a pump vane ring mounted axially adjacent thereto, both being accommodated within a single housing, wherein there is assigned to each of the two vane rings a reversing wheel rotating therewith and being open toward the other vane ring.
  • reversing wheels which are separate structural elements with respect to the housing.
  • Couplings of this type are known, for example, from the Lueger Lexikon der Energytechnik and Kraftmaschinen (The Lueger Encyclopedia for Energy Technics and Power Engines), Deutsche Verlagsweg (German Publishing House) Stuttgart, 1965.
  • the two reversing wheels have the shape of two semi-toroidal surfaces which complement each other to form a complete torus.
  • the vanes extend in both wheels in planes through the common axis of the vane rings and reversing wheels,at least this is preferred in connection with the present invention.
  • the present invention provides a coupling of the type described hereinabove which is capable ofthe broadest possible arbitrary controllability of the ratio of driven speed to driving speed and which, in addition thereto, has a simple construction, is virtually maintenancefree, is safe in operation, and can be made with very small dimensions.
  • the coupling of the present invention is suitable for many purposes where a coupling is desired that has the controllability described above
  • the preferred field of application of the present invention is the use of the coupling between the fan wheel of a motor vehicle engine and the drive mechanism for this fan wheel, which consistsas a rule of a belt pulley. It is well known that in motor vehicles the required fan wheel output or performance decreases progressively with increasing driving speed, whereas the power input of the fan wheel increases with the third power of the speed.
  • the coupling according to the present invention makes it possible to reduce, to the required extent, the torque which is transmitted fromthe drive mechanism to the fan wheel, and also to reduce the transmitted rate of revolutions, until the fan wheel will rotate, at higher speeds, practically without power input.
  • the axial distance of the two vane rings from each other is adjustable by'means of a setting or adjusting device. If the two vane rings are displaced or shifted in the axial direction far enough away from each other, the liquid leaving the pump wheelor impeller is no longer forced to directly enter into the turbine wheel. Rather, it can flow within the space between the two wheels back to the pump wheel so that only rellatively small power losses will arise when the vane rings are removed from each other. The problem of the supply and drainage of the liquid is thereby eliminated, and the pump may be constructed as a unit which requires a seal outwardly between rotating parts only at one point thereof.
  • one of the vane rings being rigidly connected with its reversing wheel and the housing, is positioned on one shaft end, whereas the other shaft end projecting into the housing is axially displaceable and carries the other wheel formed by the other vane ring and the other reversing wheel.
  • the axial position of the two reversing wheels and of one of the vane rings not be changeable with respect to each other, and that the vanes of the other vane ring are axially displaceably guided within slots of the respectively coordinated re versing wheel thereof.
  • one of the vane rings be adapted to be pulled out, in the axial direction, of the hydraulic coupling proper being enclosed by the two reversing wheels.
  • This type of construction has the advantage that a flow or circulation between the two vane rings is prevented to the greatest possible extent by the reversing wheel from which the corresponding vane ring was pulled out.
  • a construction of this type also has structural advantages.
  • the pump wheel or impeller and also the turbine wheel are constructed as has been explained hereinabove, it is nevertheless preferred that the blades or vanes of the pump vane ring are the vanes which are axially displaceable within the reversing wheel thereof.
  • the blades being axially displaceable within the reversing wheel thereof are preferably rigidly positioned at the housing, which latter rotates concomitantly therewith, and within which the other vane ring is rotatably and axially displaceably mounted.
  • the other vane ring is suitably positioned rigidly at the reversing wheel being coordinated thereto, which latter is axially displaceable only together with the other reversing wheel.
  • the reversing wheel being rigidly connected with its vane wheel or impeller is securely positioned on a bushing on which the other reversing wheel is rotatably, but not axially displaceably, positioned.
  • the bushing is mounted axially displaceably, but not rotatably, on a hollow shaft extending through or into the housing and serving for the drive, or preferably for the power take-off, in which hollow shaft a setting or controlling element is arranged for the axial displacement of the bushing on the hollow shaft.
  • the housing is advantageously driven and carries the hollow shaft of the fan wheel.
  • the hollow shaft there will be mounted in the hollow shaft, as a setting member, an element responsive to the temperature of the air flowing in through the radiator and changing its length when heated, which element, when heated, displaces the bushing against the action of a spring in a sense tending to cause the vane rings to approach each other.
  • the driven speed is increased.
  • the elastic force displaces the vane rings in a sense or direction such as to remove the same from each other, whereupon the driven speed of the fan Wheel is reduced.
  • FIG. 1 is an axial cross-sectional view through a fan wheel coupling according to the present invention, in which the coupling has been shown in the upper half of the figure in the disengaged condition thereof, and in the lower half of the figure in the engaged condition thereof;
  • FIG. 2 is a cross-sectional view, taken through line II--Il of FIG. 1, with the coupling being in the engaged condition thereof, and
  • FIG. 3 is a view from the left of FIG. 1 with the fan wheel removed.
  • the coupling shown comprises a housing consisting of the lid 1 and the bottom portion 2.
  • the two housing parts are connected with each other by means of screws 35.
  • the housing may be flanged to the V-belt pulley, for the drive of the fan of the motor vehicle engine, by means of the screws 36 indicated-in phantom.
  • the housing On the outside, the housing is provided with the cooling ribs 4, 5 and 6 which serve for the dissipation of the heat due to energy losses being produced inside the hydraulic
  • the blades 3 of the pump blade or vanering P are positioned at the end wall of the bottom portion 2. They are preferably made integral with the latter, for example in a high-quality casting process or according to an injection molding process.
  • a driven hollow shaft 7 is rotatably positioned on an inwardly projecting stud 9 of the housing bottom and in a bearing hub 8 projecting outwardly from the lid 1. It is lubricated by the couplingfluid, usually a thin oil. It is prevented from an axial-displacement on the one hand by virtue of its abutment against the housing bottom 2 and, on the other hand, because of a snap ring 16 resting against the bearing hub 8 via an intermediate disc 17.
  • a radial sealing ring 18 seals the driven hollow shaft 7 against the bearing hub 8.
  • a bushing 19 is axially displaceably positioned on the hollow shaft 7 by means of a keyway 32.
  • the bushing 19 is rigidly connected with the turbine wheel T, for example by means of a press fit.
  • the latter consists of the turbine reversing wheel 33 and the turbine blade or vane ring 20 which is suitably cast in one piece with the reversing wheel 33.
  • the turbine wheel extends in'the axial direction approximately over only half of the bushing 19.
  • Rotatably positioned on the other half of the bushing 19 is the reversing wheel 24. An axial displacement of the reversing wheel 24 is prevented by the snap ring 21 and a thrust collar or ring 22.
  • the reversing wheel 24 comprises a plurality of blade slots or vanes 23 extending in axial planes of the wheel, through which during the displacement of the bushing 19 with the reversing wheels 33 and 24 from the above-described disengaged position into the engaged position shown at the bottom of FIG. 1 the pump blades 3 penetrate into the inner space of the pump reversing wheel 24 so that thereafter the two reversing wheels 33 and 24 will cooperate in the conventional manner with the two blade or vane rings 20 and 3 being disposed therein as a Foettinger hydraulic coupling.
  • a filler screw cap 34 Mounted within the bearing stud 9 is a filler screw cap 34 serving for filling the fluid into the hydraulic coupling.
  • the driving flange 11 for the fan wheel 15 Pressed into the left end (in FIG. 1) of the hollow shaft '7 is the driving flange 11 for the fan wheel 15 with the interposition of a heat-insulating plastic bushing 10. Screws l4 connect the driving flange 11 with the fan wheel proper 15.
  • a central bore is provided into which an element 12, of an known elastic material is pressed.
  • Heat-transferring ribs 13 of the driving flange ll assure that the air being supplied from the radiator of the motor vehicle due to the air flow and/or the suction of the fan wheel communicates its temperature rapidly to the driving flange l1 and therewith to the elastic material element 12.
  • the latter has a central axially displaceable-operating pin which is progressively more markedly. pushed out of the element 12 with increasing temperature and is adapted to develop considerable forces.
  • the free end of the operating pin 30 rests against a leaf-type spring 26 which extends through two longitudinal grooves 31 of the hollow shaft 7 and projects with its two ends into an annular groove 25 of the bushing 19 so that, when the pin 30 displaces the leaf-type spring 26 in FIG. 1 from left to right, the bushing 19 and therewith the turbine'wheel and the pump reversing wheel will equally be displaced or shifted, so that as a result the pump vane ring 3 is pushed into or inserted increasingly more markedly into the pump reversing wheel 24.
  • the leaf-type spring 26 is reinforced by means of a second leaf-type spring 27.
  • a helical spring 28 which counteracts the force of the regulating element 12 of elastic material and which, by way of an annular disc 29, presses against the leaf-type springs, thus seeking by means of the latter to displace the bushing 19 together with the turbine wheel and the pump reversing wheel in FIG. 1 toward the left into the position which corresponds to the disengaged condition of the coupling.
  • the arrangement of the flat or leaf-type springs 26 and 27 is provided for so that, at very high temperatures, when the axially displaceable coupling parts are in the position shown at the bottom of FIG. 1. a short additional travel or shift of the operating pin 30 toward the right cannot cause any damage.
  • the coupling shown herein should not be totally filled with operating fluid. There should remain at the inside thereof an air volume of, for example 2 to 3 cubic centimeters in order that the change in volume by means of the operating pin 30 can be absorbed inside the housing.
  • the helical spring carries along the turbine wheel and the pump guide wheel or impeller so that the pump vane ring 3 enters or penetrates into the pump guide wheel 24 to a corresponding degree, and so that the portion of thepump vane ring 3 now being present within the pump guide wheel 24 will cooperate with the turbine wheel T in the conventional manner as a Foettinger Coupling.
  • the fan wheel 15 is rotated at a considerably increased rate as compared to the rate or speed when cold air flows in, which increased rate does not yet, however, come close to the driving speed or rate of revolutions of the pump wheel.
  • the losses in such an intermediate condition are relatively small.
  • a hydrodynamic coupling comprising a driving shaft and a driven shaft coaxial with and adapted to rotate relative to one another, a housing adapted to contain a power transmitting fluid fixedly coupled to one of said driving shaft and said driven shaft and rotatable therewith, first vane ring means mounted on said housing and rotatable therewith, a pair of guide wheels having annular concavities with their open portions facing each other to form a chamber, said pair of guide wheels being in fixed axial relation to one another and axially slidable on the other of said driving shaft and said driven shaft, a first of said guide wheels being rotatable about said other of said driving shaft and said driven shaft and having slots formed therein to receive at least a portion of the vanes of said first vane ring at all posi tions thereof, whereby said second guide wheel rotates with said first vane ring, and a second of said guide wheels being fixedly coupled to said other of said driving shaft and said driven shaft and rotatable therewith, sacond vane ring means mounted in
  • a hydrodynamic coupling in accordance with claim 3 wherein a bushing is nonrotatably and axially slidably mounted on the hollow shaft, the first guide wheel is rotatably mounted on said bushing, the second guide wheel is nonrotatably mounted on said bushing and the setting means is operatively coupled to said bushing to axially slide said bushing on said hollow shaft.
  • a hydrodynamic coupling in accordance with motor vehicle and the driving means includes an output means of a motor vehicle engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00220249A 1971-01-26 1972-01-24 Hydraulic coupling Expired - Lifetime US3792585A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2103598A DE2103598C3 (de) 1971-01-26 1971-01-26 Hydrodynamische Kupplung

Publications (1)

Publication Number Publication Date
US3792585A true US3792585A (en) 1974-02-19

Family

ID=5796945

Family Applications (1)

Application Number Title Priority Date Filing Date
US00220249A Expired - Lifetime US3792585A (en) 1971-01-26 1972-01-24 Hydraulic coupling

Country Status (11)

Country Link
US (1) US3792585A (de)
AT (1) AT316227B (de)
AU (1) AU3812572A (de)
BE (1) BE778457A (de)
CA (1) CA955814A (de)
CS (1) CS162631B2 (de)
DD (1) DD97041A5 (de)
DE (1) DE2103598C3 (de)
FR (1) FR2124836A5 (de)
GB (1) GB1375944A (de)
IT (1) IT944655B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6112869A (en) * 1998-02-17 2000-09-05 Luk Getriebe-Systeme Gmbh Force transmitting apparatus having an external damper
WO2016149740A1 (en) * 2015-03-26 2016-09-29 Norman Ian Mathers Hydraulic machine
US10788112B2 (en) 2015-01-19 2020-09-29 Mathers Hydraulics Technologies Pty Ltd Hydro-mechanical transmission with multiple modes of operation
US11085299B2 (en) 2015-12-21 2021-08-10 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with chamfered ring
US11168772B2 (en) 2009-11-20 2021-11-09 Mathers Hydraulics Technologies Pty Ltd Hydrostatic torque converter and torque amplifier
US11255193B2 (en) 2017-03-06 2022-02-22 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with stepped roller vane and fluid power system including hydraulic machine with starter motor capability

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3106665A1 (de) * 1981-02-23 1982-09-09 Siegfried Dipl.-Ing. 7960 Aulendorf Eisenmann Hydrodynamische kupplung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1125593A (en) * 1913-03-10 1915-01-19 Thomas D W Pinckney Fluid power-transmitter.
US2318187A (en) * 1940-04-17 1943-05-04 Jr Harry W Addison Automatic control for fluid transmissions
US2359930A (en) * 1941-04-14 1944-10-10 Hydraulic Brake Co Fluid coupling
US2391413A (en) * 1942-06-19 1945-12-25 James F Gregg Hydraulic coupling
US2987887A (en) * 1958-08-14 1961-06-13 Gen Motors Corp Hydraulic coupling with fluid content control
US3149465A (en) * 1960-08-19 1964-09-22 Gen Motors Corp Hydraulic coupling with thermosensitive control means

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1125593A (en) * 1913-03-10 1915-01-19 Thomas D W Pinckney Fluid power-transmitter.
US2318187A (en) * 1940-04-17 1943-05-04 Jr Harry W Addison Automatic control for fluid transmissions
US2359930A (en) * 1941-04-14 1944-10-10 Hydraulic Brake Co Fluid coupling
US2391413A (en) * 1942-06-19 1945-12-25 James F Gregg Hydraulic coupling
US2987887A (en) * 1958-08-14 1961-06-13 Gen Motors Corp Hydraulic coupling with fluid content control
US3149465A (en) * 1960-08-19 1964-09-22 Gen Motors Corp Hydraulic coupling with thermosensitive control means

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6112869A (en) * 1998-02-17 2000-09-05 Luk Getriebe-Systeme Gmbh Force transmitting apparatus having an external damper
US6298965B1 (en) 1998-02-17 2001-10-09 Luk Getriebe-Systeme Gmbh Force transmitting apparatus having an external damper
US11168772B2 (en) 2009-11-20 2021-11-09 Mathers Hydraulics Technologies Pty Ltd Hydrostatic torque converter and torque amplifier
US10788112B2 (en) 2015-01-19 2020-09-29 Mathers Hydraulics Technologies Pty Ltd Hydro-mechanical transmission with multiple modes of operation
WO2016149740A1 (en) * 2015-03-26 2016-09-29 Norman Ian Mathers Hydraulic machine
US10487657B2 (en) 2015-03-26 2019-11-26 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine
US11085299B2 (en) 2015-12-21 2021-08-10 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with chamfered ring
US11255193B2 (en) 2017-03-06 2022-02-22 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with stepped roller vane and fluid power system including hydraulic machine with starter motor capability

Also Published As

Publication number Publication date
CA955814A (en) 1974-10-08
DE2103598A1 (de) 1972-08-03
BE778457A (fr) 1972-05-16
AU3812572A (en) 1973-07-26
DD97041A5 (de) 1973-04-12
CS162631B2 (de) 1975-07-15
DE2103598C3 (de) 1975-07-17
AT316227B (de) 1974-06-25
DE2103598B2 (de) 1974-12-05
GB1375944A (en) 1974-12-04
FR2124836A5 (de) 1972-09-22
IT944655B (it) 1973-04-20

Similar Documents

Publication Publication Date Title
US4064980A (en) Dual speed viscous fluid coupling
US2902127A (en) Torque transmitting fluid coupling
US3055473A (en) Fluid coupling device
US4281750A (en) Fluid coupling device having improved response time
US2879755A (en) Fluid coupling mechanism
US3727735A (en) Viscous fluid clutch
US3587801A (en) Viscous fluid clutch
CA1101308A (en) Hydrokinetic torque converter with lock-up clutch
US3792585A (en) Hydraulic coupling
US3227254A (en) Fluid coupling
US3741359A (en) Fluid coupling
US2090401A (en) Fluid pump construction
US4741421A (en) Viscous clutch for engine cooling fan with improved fluid flow path control and feed to shear zone
US4116318A (en) Fluid flow restriction path in viscous fluid clutch
US3502056A (en) R.p.m. multiplier for automobile fan
JPS5925859B2 (ja) 自動切換式ファンの係合離反方法
US4076110A (en) Quick disengagement viscous drive coupling
US3584716A (en) Viscous fluid clutch
US2146717A (en) Transmission mechanism
US2680348A (en) Rotary pump and motor hydraulic transmission
US4924984A (en) Quick pump-out clutch plate for a viscous fluid clutch
US5487457A (en) Pressure activated rotary clutch
US2648952A (en) Rotary pump and motor hydraulic transmission
US3505908A (en) Transmission unit
US2075498A (en) Pump for liquid cooling systems of internal combustion engines