US2127738A - Hydrodynamic fluid coupling - Google Patents

Description

AugG 23g, 193 F. KUGEL.

HYDRODYNAMIC FLUID COUPLING Filed Aug. 10 1936 2 Sheets-Sheet l Aug. 23p 1933.. F, KUGEL 2,127,738

HYDRODYNAMIC FLUID COUPLING Filed. Aug. 1o, 1936 2 sheets-sheet 2 Patented Aug. 23, ,1938

Application August 10, 1938, Serial No. 95.301

In Germany August 14, 1935 l '14 claim (01; iso- 54) The invention relates to hydraulic power transmitting devices, such as ,hydraulic couplings or Atorque converters, and iii-particular to the provision, in such devicesgwofs. rotating reservoir chamber connected by separate passages to the working chamber so as. to take up the working fiuidtemporarily notl required, and thereby to enect a quick emptying and lling of the fluid circuit.

Hitherto, in such devices. the discharge of the working fluid to the reservoir chamber has frequently been effected by scoop tubes which started to work as soon as a sumciently large difference in speed existed between the fluid and the scoops. l

In such prior devices the fluid returned to the reservoir chamber from the working chamber through the same canals by which it entered, as

soon as the slip decreased in response to a change in the operating conditions. By this use of a common intake and discharge passage, either the filling or the emptying conditions were interfered with and unfavorably inuenced.

One object ofthe present invention is to provide a hydraulic power transmitting device wherein two separate connections between the reservoir chamber and the working chamber allow the working fluid to enter and leave the working chamber by separate paths, thus providing the most favorable arrangement for filling and emptying the working chamber. l v

, Another object is to provide such a device wherein the reservoir chamberv is arranged in the primary or driving part of the deviceby reason of the fact that the latter rotates always at maximum speed so that theV working fluid storedy there stands under high pressure, due to centrifugal force.` If the speed of the prime mover operating the primary or drivingv part of the hydraulic coupling or torque converter can be varied, centrifugal force may be utilized to effect 'the entrance of theV working fluid from the rotating reservoir chamber into the working chamber through passages in the primary wheel, these being preferably adjustable. The centrifugal force may be varied by changing the speed and thus the slip between the wheels. If the 4speed of the prime mover is not variable, a valve is arranged to control the supply of fluid to and from the working chamber and rotating chamber, respectively. This valve, operated automatically or manually, controls' the supply of working iluid from the reservoir chamber to the working chamber.

Another object is to provide such a device with scoops at the circumference of the secondary part,

these scoops being arranged toleifect a complete emptying of the working chamber. In ,order to obtain the large slip between primary and secondary parts necessary for the working of the scoops, the speed of the primary wheel is either 5 decreased or the discharge valve of the reservoir chamber 'is connected to a ring valve which may throttle or even interrupt the flowv of fluid to the working chamber.' .v

In the drawings:

Figure 1 is a vertical longitudinal sectionv through a iluid coupling 'with a control valve in its closed position.

Figure 2 is a similar section through a uid coupling with the control valve in its open posil5 tion.

Figure 3 is a similar section through a fluid coupling having an automatic regulating device for the control valve. f A

Figure 4 is a cross section along the line l-l inV 20 Figure 1, showing the scoop tube construction.

Referring tothe drawings in detaiLin Figure 1 the primary wheel a is connected with a variable speed engine by the driving shaft al. The secondary wheel bis mounted on the driven shaftbl.' Awall 26 a2 connected-with the primary wheel a, togetherwith the back of the latter, forms the rotating chamber u, while coupling casing aii extends over the secondary part-or turbine wheel b and forms a bearing for shaft b1 and is sealed against the 30 v shaft b1 by the'stuillng box f. Primary wheelv a is provided with passages p the openings of which are preferably adjustable. These passages p form a connection between the chamber u and the core space r. In the secondary part h, scoops m and 35 canals n are provided to return the working fluid from the transmission circuit to the chamber u along overiiow edget.'

When starting the coupling, the secondary part b of the coupling is at' rest. As the speed ofthe 40 primary part a. increases, the fluid in the chamber u is urged from the chamber u, through the passages p by centrifugalV force, thus filling the fluid circuit, i. e. engaging the coupling. With decreasing speed of the engine, and thus of the A4&5 primary part a, the scoops m gradually come into operation, due to the increased slip, and empty the fluid circuit` to the chamber u,

In Figures 1 and 2 the blade wheel, driven by a constant speed engine, is marked a.. This `wheel 50 is connected with the engine shaft al by means of a shell a, which is integral with the engine shaft a1. Blade wheel b is fastened on the shaft b1 of the machine, to be driven and inclosed by the coupling casing a3 connected to the primary blade 55 cated, the valve s1 closes the blade canals ofy wheel a. The coupling casing a.l forms a bearing for the output shaft b1 and is sealed thereagainst by means of the stuffing box f. The back of the primary blade wheel a and the shell a2 connected thereto, inclose the hollow space u serving as a reservoir chamber for the working fluid which is temporarily not required by the coupling. A number of passages p lead from this chamber to the core space r of the coupling. These passages p can be closed by the valve body s, to which the ring valve s1 is connected. In the position indithe primary wheel and at the same time the annular portion sa also closes the passages p leading to the core space r. 'I'he valve body s can be adjustably moved from the outside, adjusting sleeve i in an axial direction through the operating connection formed by the pin j and the slot k. By moving the valve body s towards the driving shaft al, the circuit is thereby opened for working fluid through the blade canals of the primary wheel a from the reservoir chamber u by way of the core space r and passages p. Secondary blade wheel b is fitted with scoops m connected by canals n to the part of chamber u near the axis.

When starting with the valve s1 closed (Figure l) the secondary part or rotor b is at rest. With increasing speed of the primary part or rotor a, however, any fluid that might have remained between the blade wheels will be thrown out by centrifugal force, caught by the scoops 1n and led through the canals n to the space q near thev axis, whence it then flows back to the chamber u. Since a return of the fluid accumulated in the chamber u into the working circuit is made impossible by the closed condition of the valve s1. an almost complete discharge of the working fluid from the coupling spaces a, b, q and r to the chamber `u is secured. This means that the coupling cannot transmit any torque when started with the valve 81 in this condition.

The working fluid accumulated in the chamber u is now influenced bythe rotating walls and subjected to centrifugal pressure. As soon as the valve body s is moved to the left by meanslof displaceable sleeve i (Figure 2). the consequent shifting of the ring valve sl uncovers the passages p so that the fluid passes through the passages 'p into the working space of the coupling at high velocity. The coupling thereby acquires the capacity to transmit torque, i. e. the coupling is engaged. Secondary runner b then starts to rotate, whereupon the fluid which is still discharged by scoops m to the rotating axis does not reach the chamber u any more, but is immediately returned to the coupling spaces a, b and r by centrlfugal force. The scooping efi'ect of the scoops m decreases with the increasing speed of the secondary wheel b and finally ceases completely, due to the centrifugal force counteracting thev passage of the iluid through the canals n. @The coupling spaces a. b and r thusremain completely filled, 'whereby the full transmitting capacity of the coupling is obtained.

.When stopping the coupling, the valve body-s is moved to the right (Figure 1) whereupon the ring valve s1 closes the openings to the blade canals ofthe wheels a and b, and simultaneously closes the passages p. This interruption of the fluid circuit immediately causes a considerable reduction in the transmission capacity of the coupling so that the speed of the secondary wheel b decreases considerably, due to the load on the machine being driven. This speed reduction I,

causes the scoops mito become-operative again to return the fluid to the chamber u so that finally a complete emptying and disengagement of the coupling is again obtained, and the driven machine comes to rest.

In order to assist the flow of the fluid from the secondary wheel b to the chamber u, it is preferred to provide the secondary wheel b with an overflow edge t projecting into the chamber u. It is further preferred to construct the valve body s in such a manner that it will also form one of the lateral limiting walls of the chamber u. Accordingly, when the valve body s is moved, for the purpose' of filling and thus engaging the coupling, this wall will have a displacing effect on the uid in the chamber u, whereby the filling of the coupling is accelerated.

Thus it will be seen that in the operation of the coupling shown in Figures 1 and 2 the fluid contained in the space u is urged outwardly by reasonof the centrifugal force created by the rotation of the coupling. 'I'his fluid is forced ythrough the bores p in the coupling rotor a. by

reason of this centrifugal force, when the valve member s and its annular portion s3 are shifted to the left, as shown in Figure 2. Thus the ring slide valve s1. and the annular portion sa cooperate to produce the desired result. 'Ihe ring slide valve s1, by altering the circulation within the coupling rotors a and b, increases the slip in thefrotor a so y that the scoop tube comes into operation, whereupon the fluid within the rotors and b is conducted through the scoop tubes m and the space q into the chamber u. To prevent the escape of the fluid at the same time through the bores p, the annular portion sa comes into action, and closes the inlets to the bores p. When it is desired to fill the coupling again, the slip is once more reduced by moving the slide valve s1 and annular ,portion s by shifting \the shift member i so that the working fluid canlflow freely through the bores p, from the chamber u, to the rotors a. and b of the coupling.

In the modined construction of Figure 3 there is shown means to provide for an automatic engaging and disengaging ot the coupling in response to the' input and output speeds or to the slip. This is realized by utilizing a centrifugal mechanism c, which becomes operative te displace the valve body s as soon as a certain speed is exceeded. This centrifugal mechanism c consists of a ily weight c1, on an arm c. pivotally mounted on the pivot member c. Likewise mounted upon the pivot member ca is an arm c4, pivotally connected at' its opposite end to a link c. The link c* is pivotally attached to a lug s mounted upon the valve body s.

In the operation of the apparatus shown in Figure 3, the rotation of the casing aI creates centrifugal force which causes the ily weight c1 to move outward, swinging the arm c4 to move the link ci to the left. lIfhis action shifts the valve body s to the left, overcoming the thrust of the coil spring h1 and causes' the ring valve s1 to Open the passages.

It will be understood that I desire to comprehend within this invention such modifications as come within the 'scope of the claims and the invention.

. I claim: 4 A

1. In a hydraulic power transmitting device, aworking chamber, a driving rotor and a driven rotor therein, and inclosing casing for said device additionally forming the outer wall of a rol tatable reservoir connected to one of said rotors for' varying the flow of fluid through both ing said reservoir and said working chamber, a-

valve member arranged adjacent said fluid pas# sage and movable relatively thereto for varying the flow of iluid therethrough, and means responsive to the rotation of one 'of said rotors for automatically varying the setting of said valve member.

3. In a hydraulic power transmitting device, a working chamber, a driving rotor and a driven rotor therein, a rotatable reservoir associated in one oi said rotors, a uid passage interconnectber toward i ing said reservoir and said working chamber, and a valvemember having .portions movable relatively to said uid passage and also relatively to the iluid circuit within said working chamber for varying the now of iiuid through both said iiuid passage and said working chamber iluid circuit. 4. In a hydraulic power transmitting device, a Working chamber, a driving rotor and a driven rotor therein, a rotatable reservoir associated in one of said rotors,a huid passage interconnecting said reservoir and said working chamber, a

-valve member arranged adjacent said iluid passage and movable `relatively thereto for varying the flow of iluid therethrough, means responsive to the rotation oi one oi' said rotors for automatically varying the setting of said valve member, and yielding means urging said valve memclosed position.

5. In a hydraulic power transmitting device, a working chamber, a driving rotor and a driven rotor therein, a rotatable reservoir associated in one of said rotors, a fluid passage interconnecting said reservoir and said working chamber, a. valve member having portions movable relatively to said iluid passage and also relatively to the iluid circuit within said working chamber for varying the iiowot fluid through both said fluid passage and said working chamber fluid circuit,

and yielding means urging said valve member toward its closed position.

6. In a hydraulic power transmitting device, a working chamber, a driving rotor and a driven rotor therein, an inclosing casing Iorsaid device additionally forming the outer wall o! a rotatable reservoir connected to one oi said rotors and 'extending' substantially to the periphery thereof, a`relatively short fluid intake passage extending from said reservoir at a location near vthe periphery of one of said rotors to' said working chamber, a'separate discharge passage extending irom said working chamber to said reservoir, and a peripherally disposed valve member arranged adjacent said intake passage `and movable relatively thereto for varying the ilow of iiuid therethrough.

'7. In a hydraulic power transmitting device, a working chamber, a driving rotor and a driven rotor forming a working circuit therein, a huid reservoir, a iiuid passage interconnecting said iiuid reservoir and said working chamber, and a valve member having portions movable relatively' to both said iluid passage and working circuit l'a working chamber, a

` rotor forming a working circuit therein, reservoir, a iluid passage interconnecting said and peripherally said iluid passage and said working circuit.

8. In a hydraulic power transmitting device, driving. rotor and a driven rotor forming' a workingcircuit therein, a iiuid reservoir, a fluid passage interconnecting said `iiuid reservoir and said working chamber, and a valve member having portions movable rela'- tively to both said iiuid passage and working circuit for varying the ilowv oi `iiuicl through both the said iiuid passage and said working circuit,

across said fluid passage and said working circuit, whereby to valve the duid flow therethrough by a single motion of said valve.

9. Ina hydraulic power transmitting device, a working chamber, a driving rotor and a driven iiuid reservoir and said working chamber, a valve member' having portions movable relatively to both said iluid passage and working circuit for varying the flow oi' fluid through both the said uid passage and said working circuit, and means responsive to the rotation oi.' one of said rotors for automatically varying the setting of said valve member.

10. In a hydraulic power transmitting device, a working chamber, a driving rotor and a driven rotor forming a working circuit therein, a iluid reservoir, `a iluidv passage interconnecting said fluid reservoir and said working chamber, a valve member having portions movable relatively to both s aid uid passage and working circuit i'or varying the ilow of uid through both the said iiuid passage and said working circuit, and yielding means urging said valve member toward its closed position.

11. In a hydraulic power transmitting device,`

` a working chamber, a driving rotor and a driven rotor therein, an inclosing casing for said device additionally forming the outer wall of a rotatable reservoir connectedv to one of said rotors and extending substantially to the periphery thereof, a iiuid intake passage extending from the pe-f riphery of said reservoir to said working chamber, a separate iiuid discharge passage interconsaid valve portions being movable simultaneously ilk a iiuid,

necting said reservoir and said working chamber,

and peripherally disposed valve means for con trolling the flow of iluid through one'of said passages.

l2. In a hydraulic power transmitting device, a working chamber, a. driving rotor and a driven rotor therein, an inclosing casingfor said .device additionally forming' the outer Wall of a rotatable reservoir connected to one of said rotors'and extending substantially to the periphery thereof, y

Va iiuid intake passage extending from the periphery of said reservoir to said working chamber, a separate iiuid discharge passage interconnecting said reservoir and said working chamber, disposed valve means having a valve member disposed near the periphery-of one of said rotors for controlling the ilow of iiuid through said intake passage.

13.` In a hydraulic power transmitting device, a working chamber, a driving rotor and a driven rotor therein, a' rotatable reservoir associated '.with one of said rotors, a fluid intake passage and a fluid discharge passage interconnecting said reservoir and said working chamber, valve means for controlling the ilow of fluid through one of said passages, and means responsive to the rotation of one oi'said rotors for automatically varying the setting of said' valve means.

14. In a hydraulic power transmitting device. a working chamber, a driving rotor and a driven rotor therein, an inclosing casing for said device additionally forming the outer wail o! a rotatable reservoir connected to one oi said rotors and extending substantially to the periphery thereof, a relatively short iiuid intake passage extending from the periphery of said reservoir to said working chamber, a separate fluid discharge passage interconnecting said reservoir and said working chamber, valve means having a valve member disposed near the periphery of one of said rotors adjacent said working chamber for controlling the now of uid through said intake passage, and a scoop on said discharge passage within said working chamber arranged to assist the emptying. 5

driven rotors.

FRITZ KUGEL.

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