US3792585A - Hydraulic coupling - Google Patents
Hydraulic coupling Download PDFInfo
- 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
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)
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)
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)
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)
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 |
-
1971
- 1971-01-26 DE DE2103598A patent/DE2103598C3/de not_active Expired
- 1971-12-31 IT IT33229/71A patent/IT944655B/it active
-
1972
- 1972-01-20 AU AU38125/72A patent/AU3812572A/en not_active Expired
- 1972-01-21 DD DD160465A patent/DD97041A5/xx unknown
- 1972-01-21 GB GB303672A patent/GB1375944A/en not_active Expired
- 1972-01-24 AT AT53772A patent/AT316227B/de not_active IP Right Cessation
- 1972-01-24 US US00220249A patent/US3792585A/en not_active Expired - Lifetime
- 1972-01-24 CS CS429A patent/CS162631B2/cs unknown
- 1972-01-25 CA CA133,150A patent/CA955814A/en not_active Expired
- 1972-01-25 FR FR7202361A patent/FR2124836A5/fr not_active Expired
- 1972-01-25 BE BE778457A patent/BE778457A/xx unknown
Patent Citations (6)
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)
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 |
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