DE2325119A1 - HYDRAULIC CLUTCH OR CONVERTER - Google Patents

Description

The parent application relates to a hydraulic coupling or connection to the automatic speed control, using positive displacement pumps (volumetrisehen pumps), which is able _s is automatically the rotational speed and to adjust the torque of the driven member ", thread a continuous winding or unwinding of - Or tape-like material on spools, coils or the like. to ensure under essentially constant tension "

The one described in the main application, Mydraulic

The clutch can only run in one direction of rotation and an all-

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gradual starting is only partially guaranteed.

. The present invention aims to provide the device to improve according to the main patent so that it rotates in both directions and that it is particularly gentle when starting and gradually starts up.

The inverse b _(arkeit the rotational direction of the coupling is useful in many industrial processes, for example in the textile industry, in which wound fabric webs up often several times on their drums and must be processed, during the various treatments to which the fabric is subjected.

Achieving a gradual start-up of the driven part is particularly useful in cases in which where masses must be set in rotation with great inertia and where there is a risk of overloading the Motor should be switched off.

In the following description, a hydraulic Coupling 'described with reversible direction of rotation according to the invention and then a hydraulic Coupling with reversible direction of rotation, with means for achieving a slow and gradual start-up of the output shaft is provided.

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• According to the invention, the hydraulic clutch described in the main application is improved in such a way that the Pumps with their suction line and their pressure line in direct connection with a first or second intermediate chimney he stands, each of which with the interior of the housing via at least one liquid inlet line and one or more liquid outlet lines connected is; furthermore, a valve element is arranged in each of the chambers, around the inlet conduit in the first to close the intermediate chamber of each pump and to open the second chamber or vice versa, depending on the the direction of rotation of the liquid caused by the direction of rotation of the shaft and the housing; the cross section of the The outlet lines of each chamber can be changed by a common control valve that can be operated from the outside.

The present invention is thus based on the principle that a group of volumetric pumps is provided, which are rotatably mounted and actuated by the clutch itself, each pump in a closed circuit with the is connected by the housing formed container, through an intermediate chamber in which both the suction line and the outlet line of the pump open, and these Chamber is provided with a first passage, which allows the flow of the liquid only in the suction direction of the pump, and with outlet openings for the pumping liquid; of course, in each chamber at any point in time, only

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neither the suction line nor only one or more outlet lines in operation, depending on the direction of rotation of the pump, whereby the first passage can be automatically closed by a valve triggered by the flow of the liquid in the opposite direction. In addition, the pressure of the pumped liquid changes as a function of that on the output shaft required torque to pull the train on the winding or unwinding To keep material essentially constant.

An embodiment of the invention is described below explained with reference to the drawings.

FIG. 1 shows a longitudinal section through the hydraulic coupling along the line 1-1 of FIG. 3.

Fig. 2 shows a section along the line 2-2 of Fig. 3. '

.Fig. 3 shows a cross section essentially longitudinally the line 3-3 of FIG. 1.

All parts that are already included in the main application are no longer described here. The description limited to those parts that enable the direction of rotation of the clutch according to the invention to be reversed.

The pump housing 22 has a central recess for receiving a central gear 25, which on

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the \ Jelle 20 ÄUtgeteiTt is §m \% 1W \ Ö.i «Saftt, TÄl lying recesses for the reception of satellite wheels 26 which are in engagement with the central wheel 25 and which are freely rotatable on pin 2? are stored (Fig. 1), which are fastened, for example, by screws to the cover 18 closing the housing or to another part firmly connected to the pump housing »The gears 25 and 26 form a system of volumetric pumps for circulating a pressure fluid along closed flow paths connected to the container inside the housing.

As can be seen from Figs. 1 and 2, each pump 25 and ' 26 by two lines 28, 29 and 28 ·, 29 ', which are in one are formed with the pump housing 22 firmly connected plate 30, with corresponding interposed chambers 31, 32 or 31 '»32 * in connection. These are between the Plate 30 and the valve body 33, which is also firmly connected to the plate 30 and the pump housing 22 is.

Each intermediate chamber 31 »32, 31 'and 32 ^!

(Fig. 1 and 3) is with the interior 11 of the housing via first annular, arranged openings 34 in connection, the are formed in the valve body 33 obliquely to the axis of the coupling. These are used exclusively for the The liquid is discharged when the relevant intermediate chamber is connected to the discharge line of the pump.

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depending on the working direction of this pump. The mentioned Openings can be opened to a greater or lesser extent by a valve 35 in the form of a truncated cone Shell, which all passage openings 34 in common is and is carried by the shaft 20 and adjustable from the outside is.

In a corresponding manner, each intermediate chamber 31, 32, 31 'and 32 ^f communicates via an axially extending suction opening 36 in the valve body 33 with an annular chamber 37 which is formed between the valve body 33 and the valve 35. This annular chamber 37 in turn communicates with the interior of the casing via openings 38 in combination which are det trained in the valve 35 '. Closed circuits are thus formed, all of which are connected to the interior space 11 of the housing serving as a container.

As I said, each intermediate chamber can optionally be connected to the suction line or the outlet line of the associated pump are in communication, depending on the direction of operation of this pump. It is clear that if, for example, the intermediate chamber 31 is connected to the outlet line of the pump 25, 26, the chamber 32 is connected to the suction line must be and vice versa. Therefore; so that the pumps can work, each intermediate chamber with an automatic Provided a valve in order to connect the outlet line 36

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•, ■ * -.... 2325113

close when the chamber is connected to the outlet line of the pump connected.

In the illustrated embodiment, this exists Valve from a valve plate 39 with side, to the rear bent legs with which it is guided displaceably in the axial direction in the chamber between an open position for the passage of the pumping liquid in the suction trap and a closed position depending on the working conditions. Of course, the legs of the valve plates are arranged where they meet the side openings 34 of each intermediate chamber can not block.

As can be seen from the drawings, the valve becomes 35 carried by a sleeve 40 which is displaceable in the longitudinal direction of the shaft 20 and which has an annular shoulder 41, against which the valve 35 is applied. A number of compression springs 41 'in corresponding recesses in the valve body 33 are arranged around the shaft 20 ", press constantly the valve 35 away from the valve body 33 in the axial direction.

Upon rotation of the housing 10, the satellite wheels 26 taken by their engagement with the central wheel 35, at which a certain drag torque to think is forced to rotate their pegs 27. The rotation of the satellite wheels 26 about their pins 27 and their rotation around the central wheel 25 result in a pumping action

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of the pump system formed by them. As a result, oil is sucked in when a direction of rotation according to the arrow 55 in Fig. 3 is assumed by the openings 34 and the intermediate chambers 32, 32 'and the associated suction lines 29, 29 ', and this oil is fed under pressure through the outlet lines 28, 28' to the intermediate chambers 31, 31 ', in which, in contrast to the chambers 32, 32 ', the valve plates are in such a way that they open the axial passage opening 36 lock. This allows the liquid only • emerge through the openings 34, their opening cross-section is regulated by the valve 35.

If the direction of rotation of the housing 10 is reversed, the intermediate chambers described interchange their function, and the clutch works in exactly the same way, but in the opposite direction of rotation.

Another embodiment is described below, the direction of rotation of which is reversible and a slow one Has started.

This hydraulic clutch has centrifugal masses, which in contrast to previously known hydraulic clutches actually make it possible to achieve a gradual starting, with the centrifugal masses driven with the Shaft are connected, which is set in rotation through the interposition of suitable pumps with closed Cycles.

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Furthermore, according to the invention, a fluid dynamic coupling is to be created for gradual starting, whose direction of rotation is reversible.

Furthermore, the coupling according to the invention of the type mentioned should be characterized in that it has a regulation of the maximum transmitted torque and that it can be used as a safety clutch under certain working conditions can work in such a way that a sudden stop or change in the load is essentially

can have an influence on the electric drive motor of the device.

The invention is based on an oleodynamic clutch with a rotating housing, which can be connected to a load to be driven, and which has a container for a Forms pumping liquid, with a coaxially rotatably mounted drive shaft in the housing and with a system of Pumps that are circulating and mechanically connected between the Housing and the shaft are arranged such that they go through a rotational difference between the housing and the shaft are drivable. In accordance with the invention, each pump is in the system connected in a closed circuit with the container, at least the outlet line of each pump with the Container is connected via a valve arrangement, which has a valve seat fixed to the housing and a valve closing member includes, which along the shaft between an opening point

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ment and a closed position adjacent to the valve seat is, and this valve closing member can be moved into its closed position by the force of rotating Centrifugal masses that are movably arranged and on the one hand on radial guides for the power transmission support the valve closure member and on the other hand against a reaction surface on the housing. The reaction surface and the radial Guides are inclined towards each other and converging outwards.

An embodiment of the invention is explained with reference to the further drawings:

Fig. 4 shows a longitudinal section through the coupling.

FIG. 5 shows a cross section substantially along line 2-2 of FIG. 4.

Fig. 6 shows a cross section substantially along the line 3-3 of Fig. 4;

Fig. 7 shows the pump housing in plan view.

Figure 8 shows a top view of the manifold of the pump.

FIG. 9 shows a section along the line 6-6 of FIG. 8.

FIG. 10 shows a partial section along line 7-7 of FIG Fig. 8.

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As can be seen from the drawings, the oleodynamic clutch or converter according to the invention essentially comprises a housing 10 ₉ which forms a closed container chamber 11 for a pump fluid = this housing carries a pump housing 112 inside, which is sealingly between the housing 10 itself and its closure cover 113 is arranged by means of a ring of screws 114 arranged on the circumference, only one of which is shown in FIG. 4. The cover 113 of the housing or the housing itself may have a hub, pulleys 115 or other means connected therewith to produce a drive transmission from the hydraulic clutch to a work load which is to be driven by a suitable motor, directly or via intermediate members. The coupling further includes a drive shaft 116 which is coaxially and sealingly supported within the rotating housing 10. This is connected to a central gear 117 of a pump system. As can be seen from FIGS. 5 and 7, the pump housing 112 has a central recess 118 for the central wheel 117 as well as two diametrically opposite recesses 119> 120 for receiving corresponding satellite gears 121, 122 which mesh with the central wheel 117 with this to form two gear pumps which are connected in a closed circuit to the container 11 inside the rotating housing 10. It goes without saying that, instead of the described pump with two planetary gears, a different number of planetary gears can be used.

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Each planetary gear 121, 122 is rotatably mounted on a pin 123 with a screw 124 in a corresponding conical seat is fixed, which is formed in the distributor 125 of the gear pump, as in the upper one Part of Fig. 4 for the planetary gear .121 is shown.

The manifold 125 of the pump is fastened with screws 126 to the pump housing 112 and thus to the rotating housing 10 together with a side cover 127.

The manifold 125 is shown in detail in FIGS. 8, 9 and 10 shown. .

As can be seen from these drawings, the manifold 125 has the two conical seats 128, 129 for the pins of the planet gears 121 and 122. There are also suction openings and outlet openings for the two gear pumps in it 117, 121 and 117, 122, respectively. More specifically, there are two distributor chambers in the distributor 125 for each gear pump 130, 131, which extend over an arc of a circle and which have an axial passage 132 or 133 are connected to the associated gear pump, as shown in the lower half of FIG. Each distribution chamber 130, 131 is on the side that the axial Opposite liquid passage, with a truncated cone gene valve seat 134 in connection, in the manifold 125 is formed on the opposite side to the pump.

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This valve seat 134 is practically concentric to the The axis of rotation of the housing 10 and the drive shaft 116 are arranged. In the embodiment shown, the Chambers 130, 131 and the associated openings T32. » 133 in the manifold 125 optionally the intake ducts and the outlet ducts of the associated pump, depending on the direction of rotation of the coupling. Accordingly, the hydraulic Coupling according to the invention of the reversible type.

As can be seen from FIGS. 5 and 9, the manifold 125 also has peripheral openings 135 associated with each pump, 136 on which the associated pump with the pump liquid connect the filled container space 11 without running through the valve seat mentioned above »

Located in front of the valve seat 134 in the manifold 125 a closing member 137, which is mounted displaceably in the longitudinal direction of the axis of the coupling. This closing link 137 forms together with the valve seat 134 of the manifold 125 a valve arrangement for the regulation and function of the clutch.

More specifically, the locking member 137, which accordingly the valve seat is frustoconical, carried by a bushing 138 which extends longitudinally in the axial direction a flange sleeve 139 ".verschiebbar, which in turn means Screws 140 is attached to the housing 10. Between

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the drive shaft 116, the sleeve 139 and the pulleys 115 of the carcass are of course suitable seals arranged and also suitable bearings, such as bronze bushings, ball bearings or the like.

The closing member 137 is, as shown in Fig. 4, under the action of compression springs 141, and is accordingly the bush 138 under the action of compression springs 142 which push these parts away from the valve seat 134.

From the sectional view of Fig. 6 it can be seen that a ring of springs 141 and a further ring of springs 142 are provided for the closing element or for the socket are to distribute the forces over the whole perimeter. This gives you the opportunity to get the most out of the clutch regulate transmitted torque by adding more or less springs are used or springs of one type are replaced by springs of another type with different elastic properties replaced, as will be understood from the following.

, The hydraulic clutch according to the invention is used for a gradual acceleration of the load and for a direct connection between the load and the drive motor, once the operating speed is reached. That's why the closing member 137 must be movable between its closed position shown in FIG. 4 and an open position be.

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The control of the closing element for the transition from the open position to the closed position takes place according to of the invention by rotating centrifugal masses connected to the housing 10, i.e. with the driven or slower Part of the clutch are connected, so that in practice there is a start-up process that takes place gradually and from the The mass of the load to be driven is independent ο

For this purpose, the guide bushing 138 for the Closing member, as shown in Fig. 4 and 6, three radial guides 143, which for reasons of balance at equal angular intervals are arranged to each other. A centrifugal mass can move along each radial guide 143, which in the essentially consists of a transverse pin 144 which is in contact is displaceable with the corresponding guide or cam surface of the associated guide 143. This cross pin

144 carries a ball bearing 145 or the like at both ends, which rolls into contact with a reaction surface of the housing 10 opposite the cam surface of the radial guides is arranged.

As can be seen from Fig. 4, the cam surfaces of the guides 143 and the corresponding reaction surface of the housing inclined towards each other and converge outwards, so that by the centrifugal forces acting on the masses 144,

145 act during the rotation of the housing 10, these masses are pressed radially outwards and thereby against the guide

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gen 143 and via this on the holder 138 and the locking member 137 press so that the latter is pressed towards the valve seat 134 in the manifold 125, namely against the power of the pumping liquid that is circulated by the gear pumps 117, 121 and 117, 122.

The use of the pins 144 and the ball bearings 145 for the formation of the centrifugal masses is advantageous because the Direction of rotation of a pin 144 with respect to the cam surface a radial guide 143 opposite to the direction of rotation of the ball bearings 145 on the reaction surface of the housing 10 is.

It is thus through suitable dimensioning of the centrifugal masses, of the pump system and the counter pressure springs possible, a clutch with gradually increasing power transmission to realize that transmits a maximum torque of a given value.

The coupling according to the invention works as follows. It it is assumed that the drive shaft 116 is connected to an electric motor is connected, while the housing 10 is connected to a load to be driven. It is also assumed that the load and the motor stop. In this state, the locking member 137 and its holder 138 are by the action the springs 141 and 142 pushed away from the valve seat 134, and the centrifugal masses 144, 145 are

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consequently in a position which lies radially further inward than shown in FIG.

As soon as the input shaft 116 of the coupling is set in rotation, the load and thus the housing 10 still being fixed, the pumps are put into operation due to the speed difference between the housing 10 and the shaft 116. These suck in the oil or the liquid contained in the container 11, for example via the opening 132, and push them out through opening 133. This causes the pumps to generate an initial drive torque, which slowly rotates the housing 10 and the load connected to it "at a speed ranging from depends on the amount of the load itself ».

As soon as the housing 10 begins to rotate, the rotating masses 144, 145 move radially outward due to the resulting centrifugal force, whereby they simultaneously act against the end face or cam surface of the guides 143 and against the reaction surface of the housing 10 and thereby on the closing member 137 exert a force ^ to this to move toward the valve seat by an amount proportional to the radial displacement of the masses.

When the closing element approaches the valve seat and accordingly the passage cross-section for the pumping liquid decreases, the pressure of the liquid in the pump

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pen and thus the transmitted torque gradually to, until finally the centrifugal masses up to the position according to 4, where they have moved the closing member 147 so far that it completely closes the valve seat. In this position there can be no more flow of the liquid, which then remains under pressure, and the Gear pumps can no longer rotate. In this state there is consequently a direct connection between the Input shaft 116 and the housing 10, which during the entire normal operation of the clutch is maintained.

When the load and thus the housing slow down, the rotating masses 144 and 145 shift due to them inward again, proportional to the decreasing centrifugal effect to reduce the speed of the housing 10 compared to the shaft 116. This allows the springs 141 and 142 move the closing member and its holder so that the valve is opened again. The same thing happens with a sudden increase in the load, so that the coupling according to the invention is also effective as a safety coupling.

Based on the above description and drawings it can be seen that in the coupling according to the invention, in contrast to other commercially available couplings, the time for the load to start, i.e. the time it takes for the valve to close completely and thus to accelerate the load to the maximum specified

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The speed of rotation seen is a function of the load itself - accordingly, the acceleration of a light load is faster than the acceleration of a heavy "load, whereby a corresponding time saving results.

Furthermore, precisely because of the fact that the centrifugal masses with the driven part of the clutch connected, the possibility of setting large masses in motion even with low power.

. The embodiments described are only available as an example. games to understand and deviations and. Refinements are possible within the scope of the invention.

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Claims (6)

Claims 1. Hydraulic coupling with a rotatable housing that forms a container for pumping liquid, one coaxial Rotatable shaft mounted in the housing, a system of revolving Pumps ,, which are mechanically arranged between the housing and the shaft so that they are common to a Rotation difference between housing and shaft are operated according to patent (P 23 15 772.4), characterized in that each pump of the system with its suction line and its pressure line are in direct connection with a first or second intermediate chamber, each of which with the interior of the housing via at least one liquid inlet line and one or more liquid outlet lines is connected, and that a valve element is arranged in each of the chambers to close the inlet line in the first intermediate chamber of each pump and to open in the second intermediate chamber or vice versa, depending on the direction of rotation of the shaft and the Housing-related direction of circulation of the pump liquid, wherein the cross-sections of the outlet openings of each pump can be changed by means of a common control valve that can be actuated from the outside is. 2. Hydraulic coupling according to claim 1, characterized in that it has a pump housing, - 20 3 0 9 8 4 9/0482 which is arranged in the interior of the housing and rotatable with it, the pump housing having a central recess for a central gear attached to the shaft as well as recesses arranged around it for corresponding plan = base gears has, which are freely rotatably mounted on the housing or a part connected to this and with the Central gear are in engagement, so that each planet gear with the central gear forms a volumetric pump, which with two separate lines is connected to the associated intermediate chambers, which in turn are formed in a valve housing are arranged concentrically to the shaft and rigidly connected to the pump housing. 3. Hydraulic coupling according to claim 1 or 2, characterized in that the shaft is the drive shaft and the housing is the driven part of the clutch. 4. Hydraulic coupling according to one of claims 1 to 3, marked by the fact that each inlet opening is formed for the intermediate chambers in the valve body in the direction parallel to the axis of the coupling and that one Valve plate is provided in each intermediate chamber - around the to close said opening when the intermediate chamber in question is connected to the pressure side of the associated pump is. ~ 21 - 309,849 / 0482 5. Pump according to one of claims 1 to 4, characterized in that each pump with the container is connected via a valve, which consists of a valve seat fixed to the housing and a closing element, along the drive shaft between an open position and a closed position adjacent to the valve seat is displaceable and in the direction of the closed position by the force of rotating centrifugal masses which are movably arranged and on one side against radial guides, which apply the force to the Transferring closing member, and on the other side against · a reaction surface of the housing, wherein the reaction surface and the radial guides are inclined to one another and are arranged to converge outward. 6. Coupling according to claim 5, characterized in that g e k e η η draw, t that each centrifugal mass is formed from a central roller body and two lateral roller bodies, which are freely rotatably mounted on the central roller body are running along the associated guide, while the lateral rolling elements on the reaction surface of the Housing run. - 22 - 9849/0482 Blank page