DE19940537A1 - Fluid friction clutch - Google Patents

Fluid friction clutch

Info

Publication number
DE19940537A1
DE19940537A1 DE1999140537 DE19940537A DE19940537A1 DE 19940537 A1 DE19940537 A1 DE 19940537A1 DE 1999140537 DE1999140537 DE 1999140537 DE 19940537 A DE19940537 A DE 19940537A DE 19940537 A1 DE19940537 A1 DE 19940537A1
Authority
DE
Germany
Prior art keywords
liquid
friction clutch
space
valve arrangement
storage space
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.)
Withdrawn
Application number
DE1999140537
Other languages
German (de)
Inventor
Hans Martin
Original Assignee
Hans Martin
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 Hans Martin filed Critical Hans Martin
Priority to DE1999140537 priority Critical patent/DE19940537A1/en
Publication of DE19940537A1 publication Critical patent/DE19940537A1/en
Withdrawn legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D35/00Fluid clutches in which the clutching is predominantly obtained by fluid adhesion
    • F16D35/02Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with rotary working chambers and rotary reservoirs, e.g. in one coupling part
    • F16D35/021Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with rotary working chambers and rotary reservoirs, e.g. in one coupling part actuated by valves
    • F16D35/024Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with rotary working chambers and rotary reservoirs, e.g. in one coupling part actuated by valves the valve being actuated electrically, e.g. by an electromagnet

Abstract

It becomes a fluid friction clutch with at least one rotor that can be coupled to a drive shaft and that is arranged in a working space of a housing that can be at least partially filled with liquid, with a storage space for the liquid that is arranged in the rotor, the storage space being connected to the working space via at least a first connecting path Working space are connected to the storage space via at least a second connection path, and with a valve arrangement with the aid of which the liquid level in the working space can be influenced. The fluid friction clutch is characterized in that the valve arrangement (59) is designed such that the first and second connecting paths (43, 45) can be closed in a first functional position of the valve arrangement (59).

Description

The invention relates to a fluid friction coupling with at least one with a drive shaft couplable rotor, which in a with liquid at least partially fillable work space a housing is arranged, according to the preamble of claim 1 and a fluid friction clutch lung according to the preamble of claim 5.

DE 197 42 823 A1 describes a liquid series exercise clutch of the type mentioned here. This includes one with the help of an with an drive torque applied drive shaft driven rotor which in a ge with liquid filled work space is arranged. In the rotor a storage room for the liquid is integrated. The storage room is connected via a first connection path with the work space and the work space over a second connection path with the storage room connected. The supply can be and drain of the liquid to the work area so ge controls that in a first extreme position the valve arrangement ver the first connection path is closed while the second connection path is open, and that in a second extreme position the first connection path is open while the second connection path is closed. The below other in connection with fan arrangements for  Liquid friction used in vehicle engines clutch has the disadvantage that depending speed of the rotor's drive speed, which in turn depends on the engine speed of the vehicle, the pumped itself from the work room into the storage room te amount of liquid changes, so that constantly Readjustment required by the valve arrangement is to ensure a constant filling level of the Workspace and thus a constant, over adjustable torque. As a result of that the drive in city traffic, for example speed is constantly changing, is a defined, about portable friction torque practically not adjustable.

It is therefore an object of the invention to use a liquid keits friction clutch of the type mentioned create that does not have these disadvantages.

To solve the problem, a liquid is used Exercise coupling with the features of claim 1 suggested. This is characterized in that the valve arrangement is designed such that in a first functional position of the valve arrangement close the first and second connection paths are cash. The fluid connections between stocks space and work space or between ar The working room and the storage room can therefore work simultaneously be completely closed so that independent a constant fluid from the drive speed quantity can be set in the work area. With at their words, by foreclosing the supply room with the help of the valve arrangement can be one of the drive speed of the fluid friction clutch independent, constant transferable  Frictional torque can be set so that a steady Readjustment of the amount of liquid in the work area, as in the known fluid friction clutch must be made, not necessary is.

In a first embodiment of the liquid friction clutch, a shaft drive is provided, that is, the rotor comes with a driving torque pressurized so that be in the work room sensitive liquid a frictional moment on the Housing surrounding the liquid room exercise clutch is transmitted. The speed of the Ge is dependent on the degree of filling of the Working area with liquid correspondingly smaller than the drive speed of the rotor respectively the drive shaft. In another execution example of the fluid friction clutch is a Housing drive provided, in which the housing is driven and located in the work room liquid a frictional moment on the with the Drive shaft coupled rotor is transmitted which corresponds to the housing accordingly reduced speed rotates. The drive shaft has the function of a drive shaft here, to drive another unit, at for example, a water pump shaft.

After a further development of the invention, it is provided hen that in a second position Valve arrangement only the first connection path between lockable pantry and work space is. In the pantry, in which at least one Ab opening opens through the liquid from the front  Council room in the first connection path and from there can flow into the work area is located in the drive at a radial distance from the axis of rotation shaft so that when the rotor is rotating and open filling the first connection path of the work space is feasible. For example can operate the fluid friction clutch that flow from the workroom into the store room de amount of liquid by closing the first Connection paths stored in the pantry and from there needs-based, that is, to one to one desired transferable friction torque adjusted before by opening the he at least partially Most connection paths in the work area be directed. Opening and closing the he Most connection path can for example with the help a control and / or regulating device follow, so that the valve arrangement as required actuated or controlled accordingly becomes. It is therefore possible that the opening and Closing the first connection path with Tak Ten of the valve assembly is done, which is a simplification the control.

After a further development of the invention, it is provided hen that in the first functional position of the Venti arrangement the liquid in the work area circulates only within the work area. There can be ensured by that on a the valve associated with the second connection path Valve arrangement acting pressure only relatively low is, so that an "overpressing", ie an opening of the Valve, can be avoided. Beyond that a level change in the pantry what  inevitably also to a level change in the Work space leads, easily possible.

Further advantageous refinements of the liquid friction clutch result from the rest Dependent claims.

A liquid is also used to solve the problem Friction clutch with the features of claim 5 suggested. This is characterized in that at least two first connection paths between Ar beitsraum and pantry are provided, whose radial distance to the axis of rotation of the rotor below is different, and that the valve arrangement such is arranged that in a first function at least one of the first connection paths is lockable, the other first connection path at least partially, preferably full constantly open. If at least one of the first connection paths is open, flows continuously Liquid from the work room into the storage room and from this back into the work space. This is depending on the radial distance of the first Connection paths to the rotor axis of rotation one step at a time se adjustment of those in the work area Realized amount of liquid. The following applies greater the radial distance of the first one Connection path to the axis of rotation of the rotor is de The larger is when the first connection is open liquid in the work area quantity and thus the transferable friction torque. Is the distance between one of the first connections paths and the axis of rotation of the rotor only slight, so can with appropriate control or  Regulating the valve arrangement a large liquid quantity in the pantry and thus a corresponding Smaller amount of liquid in the work area can be set. It is particularly advantageous that regardless of the drive speed of the rotor (Shaft drive) or the housing (Housing drive) a constant filling Degree of the work area adjustable with liquid is.

Finally, an embodiment of the rivers sigungsreibungskupplung preferred that there characterized by that the fluid friction coupling designed as a pre-assembled unit is in the fully assembled state only with a suitable drive or output must become. This is an adaptation of the liquid friction clutch to a drive shaft, at for example the drive shaft of a water pump egg nes motor vehicle, easily in a short time possible. The fluid friction clutch can for example also in connection with a fan arrangement of a motor vehicle can be used, the fan blades preferably on the rotating housing of the fluid friction clutch are attached.

Further advantageous embodiments of the liquid friction clutch result from the rest Dependent claims.

The invention based on the drawing tion explained in more detail. Show it:  

Figure 1 shows a cross section through a first embodiment of a liquid friction clutch.

Fig. 2 is a cross-section through the liquid keitsreibungskupplung of FIG. 1;

Figs. 3A to 3C each is a highly schematic representation of a control of a first embodiment of a valve assembly in different operative positions;

FIGS. 4A to 4C are a schematic diagram of a control of a further example of the guide from Ventilanord voltage in various functional Stel lungs and

Fig. 5 is a diagram in which a is from a rotor to a liquid carryover bares friction torque as a function of the differential rotational speed of the rotor Darge presents with several characteristic curves.

The fluid friction clutch 1 described below is generally applicable, for example in connection with a fan assembly or egg ner water pump of a motor vehicle.

Fig. 1 shows a longitudinal section of a first exemplary embodiment from the fluid friction clutch 1 , of which only the part lying above an axis of symmetry 3 is shown. The liquid keitsreibkupplung 1 includes a housing 2 parts here 5 , which comprises a substantially cup-shaped, first housing part 7 and a second housing part 9 , which is partially accommodated by the first housing part 7 . The first housing part 7 has radially projecting cooling fins 11 . At the two housing part 9 th several bores are vorgese hen, of which only the bore 13 is shown in FIG. 1, which are used for attaching fan blades, which are part of a radiator of a motor vehicle, not shown, cooperating fan arrangement.

Between the housing parts 7 , 9 , which are arranged at a distance from one another, a working space 15 is defined which can be filled with viscous liquid, for example silicone oil. In the working chamber 15 in a rotationally fixed to a drive shaft 17 verbun Dener, disc-shaped rotor 19 is arranged which on its side facing the first housing part 7 side face 21 and its side facing the second housing part 9 facing side face 23 of projections 25 has, the 27 of the first in coaxial grooves and engage second housing parts 7 , 9 and form shear gaps with them. Another shear gap is gebil det between the peripheral surface 29 of the rotor 19 and an inner wall 31 of the first housing part 7 .

The drive shaft 17 , the longitudinal center axis 33 of which coincides with the axis of symmetry 3 , is supported by a bearing 35 , which is formed here by a ball bearing, in the second housing part 9 of the preferably rotationally symmetrical fluid friction clutch 1 . At the end of the drive shaft 17 facing away from the rotor 19 , a fastening flange 37 is provided, via which the drive shaft 17 can be coupled to a drive, for example a pulley, a water pump shaft or the like, preferably with the interposition of an elastic coupling.

In the rotor 19 , an annular, coaxial storage space 39 is arranged for the viscous liquid. The storage space 39, which can be closed by a cover 41, is connected to the working space 15 via a first connecting path 43 and the working space 15 is connected to the storage space 39 via a second connecting path 45 . The connecting paths 43 , 45 are provided at a radial distance from one another and from the longitudinal central axis 33 of the drive shaft 17 in the cover 41 . The first - seen in the radial direction hen - externally arranged connection path 43 is here from a ver in the direction of the longitudinal central axis 33 running blind hole 47 and a perpendicular to it ver, opening into the storage space 39 tap hole 49 and the second connection path 45 from a parallel to Blind hole 47 extending through hole 51 and a perpendicular to the through hole 51 tap hole 49 'is formed. The first connecting path 43 or the tap hole 49 opens directly on the outer circumferential surface 53 of the storage space 39 , while the second connecting path 45 or the tap hole 49 'opens into the area of the inner peripheral surface 55 of the storage space 39 .

The storage space 39 is connected to the working space 15 via a ventilation hole, not shown in FIG. 1, which is preferably arranged in the cover 41 , whereby a pressure compensation is possible.

In addition, a bypass opening 57 is seen in the rotor 19 through which the liquid located in the working space 15 can flow or be pumped off via the second connection path 45 into the storage space 39 . The bypass opening 57 thus forms part of the second connection path 45 .

As can be seen from FIG. 1, in the rotor 19 there is at least one return channel 58 which runs perpendicular to the longitudinal central axis 33 and opens into the bypass opening 57 and which starts from the radially outermost region of the working space 15 and there with a not shown in FIG. 1, known bluff body is in operative connection, which forms a return pump system with the return channel 58 . The liquid, which is in the shear gap between the circumferential surface 29 of the rotor 19 and the inner wall 31 of the first housing part 7 , is conveyed in the operation of the fluid friction clutch 1 - as indicated by an arrow - radially inward in the direction of the longitudinal central axis 33 and can can be pumped back into the storage space 39 when the second connecting path 45 is open.

The connecting paths 43 , 45 can be closed with the aid of a valve arrangement 59 which, in this exemplary embodiment, comprises a control element 61 shown with a broken line, which here is formed by a valve lever 63 ( not shown). On the side facing away from the working space 15 of the valve lever 63 , an annular permanent magnet 65 is arranged. In the area between the mounting flange 37 and the second housing part 9 , an annular coil having an electromagnet 67 is preferably stationary relative to the drive shaft 17 and the housing 5 , which was a greater radial distance from the longitudinal central axis 33 relative to the permanent magnet 67 arranged at a distance of the drive shaft 17 . With the help of the electromagnet 67 , which interacts with the permanent magnet 65 in a contactless manner and attracts or repels them, depending on the polarity, the entire valve arrangement 59 can be moved back and forth in several functional positions in the direction of the longitudinal central axis 33 (double arrow 69 ) , which will be discussed in more detail below with reference to FIG. 2.

If the first and second connecting paths 43 , 45 are closed with the aid of the valve arrangement 59, the liquid pumped radially inward through the return channel 58 into the bypass opening 57 flows into the shear gap between the rotor 19 and the second housing part 9 and via the bypass opening 57 and the through hole 51 in the shear gap between the rotor 19 and the first housing part 7 back. Due to the centrifugal forces acting on them, the liquid is then pumped out again. In closed Verbindungspfa the 43, 45 so the fluid in the working chamber 15 is circulated only within the working space 15th The degree of filling of the working space 15 is therefore constant in the first functional position of the valve arrangement and is not dependent on the drive speed of the fluid friction clutch designed here as a shaft drive. That is, even with a change in driving speed, the amount of liquid in the working space 15 remains unchanged.

In the currentless state of the electromagnet 67 befin the control det 61 and the valve lever 63 gear position to the position shown in Fig. 1 from which is a central position, that is, the valve lever 63 is in the representation according Fi gur to the left and to the right displaceably . In the starting position, the control element 61 closes all the connecting paths 43 , 45 between the storage space 39 and the working space 15 or between the working space 15 and the storage space 39 . To reach in the de-energized state of the electromagnet 67 with the help of the magnetic forces, an independent shift of the control element 61 to its starting position, for example in the immediate vicinity of the permanent magnet 65 arranged on the valve lever 63 , another permanent magnet, not shown in the figures be provided, which is arranged for example on the cover 41 of the rotor and interacts with the permanent magnet 65 . Instead of or in addition to the further permanent magnet, an element made of ferromagnetic material can also be provided, which holds a stable central position of the control element by corresponding pole beams. Alternatively or in addition, a spring or other mechanical or fluid-technical aids can also be inserted so that the control element 61 - preferably independently - can be shifted into its starting position (first functional position).

The electromagnet 67 is thermally only slightly loaded. Since the actual current applied to the electromagnet 67 occurs only relatively rarely and good heat dissipation of the coil can be realized, the coil can be kept relatively small, which saves costs and space.

FIG. 2 shows a section of the fluid friction clutch 1 shown in FIG. 1 , namely a cross section through the valve arrangement 59 . The control element 61 formed in this exemplary embodiment as a slide has a U-shaped closure element 71 at its endbe cooperating with the first connecting path 43 , which has a projection 73 of the cover 41 with side walls 75 projecting radially into the storage space 39 and having the stitch bore 49 and 77 engages so that when the control element 61 is moved in the direction of the longitudinal central axis 33 of the drive shaft 17, an overlap between the side wall 77 and the tap hole 49 can be brought about, where the first connection path 43 between the storage space 39 and the work space 15 is closed. The control element 61 is constructed at its end facing the second connection path 45 substantially the same as at its end facing the first connection path 43 and has a U-shaped closure element 71 'with a projection 73 ' in the cover 41- extending side walls 75 'and 77 'of which the side wall 77 ' in a defined position of the control element 61 covers the tap hole 49 'and thereby closes the second connection path 45 . In another embodiment, not shown in the figures, the closure elements 71 , 71 'are not U-shaped, but only have the side wall 77 or 77' necessary to cover the respective tap hole 49 , 49 '. The valve arrangement 59 has only a small mass.

As can be seen from Fig. 2, the stitch bores 49 , 49 'extend substantially transversely to the longitudinal extension of the drive shaft 17 , the Stichboh tion 49 ' of the second connection path 45 in this embodiment to the left of the perpendicular to the longitudinal central axis 33 of the drive shaft 17 Axis 79 and the tap hole 49 of the first connecting path 43 open to the right of the axis 79 into the storage space 39 . Of course, both tap holes 49 , 49 'can also open into the storage space 39 on one side of the axis 79 .

The closure elements 71 , 71 'are arranged within the storage space 39 in the rotor 19 . When the rotor 19 rotates, the valve lever 63 is rotated about the longitudinal central axis 33 of the drive shaft 17 . Due to this configuration, a flee force independent valve is provided, the displacement force must be applied at the single Lich to the rotating valve lever 63 to move to actuate relation ship example.

The function of the valve arrangement 59 is explained in more detail below with reference to FIGS. 3A to 3C, which each show a schematic diagram of the control element 61 described with reference to FIGS. 1 and 2.

In FIGS. 3A to 3C, the control element 61 is shown simplified as a plate which be on open edge opposite sides of recesses 81 relationship as 81 ', of which mung the Ausneh 81 the first connecting path 43 and from recess 81' to the second connecting path 45 assigned. Only if there is a recess in overdec tion with the associated connection path 43 or 45, this is open so that liquid can flow or be pumped out from the working space 15 into the storage space 39 or from the storage space 39 into the working space 15 . In this embodiment, the valve assembly 59 with the aid of the electromagnet 67 in the direction of the longitudinal central axis 33 in two functi onsstellungen displaceable. In the illustration accelerator as Fig. 3A is the valve assembly 59 in a first functional position, which preferably has a starting position in which the first and second connection paths 43 are sealed, 45, that is, both tap holes 49, 49 'are of the control element 61 covered. So neither liquid can flow from the storage space 39 into the working space 15 or from the working space 15 into the storage space 39 .

In a particularly preferred embodiment, the electromagnet is de-energized in the first functional position of the control element 61 , so that no energy loss occurs. In order to allow a required amount of liquid via the first connec tion path 43 from the storage space 39 into the working space 15 or via the second connecting path 45 from the working space 15 into the storage space 39 , the electromagnet 67 is energized in such a way that the on the valve lever 63 brought permanent magnet 65 is attracted or repelled se. In the illustration according to FIG. 3B, the control member 61 is in its second functional position, which is shifted relative to the first function (output) position (Fig. 3A) to the right path in which only the first connection is closed 43 while the second connection path 45 is fully open. This means that the liquid in the working space 15 can flow into the storage space 39 , which thereby fills up. In Fig. 3C, the control element 61 is in the third functional position, which, starting from the starting position ( FIG. 3A) of the control element 61, is located to the left thereof, in which only the second connection path is closed.

For control / regulation of the transmissible Reibmo ments of be with reference to the preceding figures signed fluid friction clutch. 1 The torque that can be transmitted by the fluid friction clutch 1 is dependent, inter alia, on the degree of filling of the working space 15 , that is to say the amount of fluid in the working space. In order to increase the transmissible friction torque, liquid must also be brought into the working space 15 from the storage space 39 . To reduce the friction torque, it is necessary to discharge liquid from the working space 15 into the storage space 39 . In order to set a differential speed-independent, transferable torque, the fluid connections in the work space 15 must have the fluid connections from the storage space 39 to the work space 15 or, respectively, from the work space 15 to the storage space uninterrupted, especially by relocating the valve arrangement to its first function position, if the desired torque is sufficient lung. When the valve arrangement 59 is shifted into its second functional position, the storage space 39 begins to fill, since no liquid can flow from the storage space 39 into the working space 15 via the closed first connection path 43 . Due to the decreasing fluid level in the working space 15 , the transmissible torque of the fluid friction clutch 1 is also reduced. In the second functional position of the valve arrangement 59 , an essentially complete emptying of the working space 15 while simultaneously filling the storage space 39 is possible. In the drit th functional position of the valve assembly 59, the fluid flows from the reservoir 39 into the working space 15, wherein the amount of liquid in the reservoir 39 drops and rises in the working chamber 15, whereby the transmittable torque of the liquid friction clutch 1 increases.

Particularly advantageous in the fluid friction clutch 1 described with reference to the figures is - in contrast to the known fluid friction clutch - that fluid is not constantly pumped out of the working space 15 into the storage space 39 , but only as required, that is only when a change in the transmissible torque is desired is. Due to the integrated in the rotor 19 before storage room 39 , the supply of a desired amount of liquid can be ensured from the storage room 39 in the working space 15 even at high speeds of the drive shaft 17 . Thus, a critical operating state, as it can occur in the known liquid friction clutch, namely when at high drive speeds the amount of liquid returned to the storage space is greater than the amount of liquid that can be supplied from the storage space into the working space, can be excluded.

FIG. 4A to 4C each show a detail of a further embodiment of the liquid keitsreibungskupplung 1 with another exporting approximate shape of the valve assembly 59. The same parts are provided with the same reference numerals, so that reference is made to the description of the previous figures.

Between the storage space 39 in the rotor 19 and the working space 15 , not shown, there are two first connecting paths 43 and 43 'and from the working space 15 to the storage space 39 there is only a second connecting path 45 . Through the valve arrangement 59 , only the first connection paths 43 , 43 ', which are at different distances from the axis of rotation 33 of the drive shaft 17 , can be closed, so that in each functional position of the valve arrangement 59 , liquid is constantly flowing out of the working space 15 via the always open second connection path 45 into the Storage space 39 can flow back. The valve assembly 59 includes resilient, tongue-shaped valve elements 83 and 85 , of which the Ventilele element 83 is the first connection path 43 and the Ven valve element 85 is assigned to the other first connection path 43 '. The valve elements 83 , 85 are connected to one another at their end facing away from the connecting paths 43 , 43 ', with the permanent magnet 65 being attached in the connecting region. The valve element 83 is arranged inside the storage space 39 , ie in the rotor 19 , and the valve element 85 in the working space 15 . The displacement of the valve assembly 59 in the direction of the longitudinal central axis 33 of the drive shaft 17 is also carried out here with the aid of an electromagnet 67 , with the permanent magnet 65 preferably in the de-energized state independently - as described above - or with other suitable means in the in FIG. 4A shown starting position of the valve assembly 59 is shifted, in which both first connecting paths 43 , 43 'are closed sen.

In Fig. 4A, the valve assembly 59 is in a first operating position in which the two first connection paths 43, 43 are closed '. The storage space 39 is constantly filled with liquid from the working space 15 via the second connecting path 45 and can therefore - as indicated - have a large amount of liquid. The amount of liquid in the working space 15 is correspondingly small at this moment. In the second functional position shown in FIG. 4B (first connection path 43 open, first connection path 43 'closed), practically all of the liquid can flow out of the storage space 39 into the work space 15 , as a result of which the transmissible torque is increased while the drive speed remains the same. In Fig. 4C, the valve assembly 59 in its drit th functional position (first connection path 43 'open, the first communication path 43 is closed) arranged, in which the reservoir is so far drainable 39, until the level of at rotating rotor 19 to the outer peripheral surface 53 of the liquid film forming the storage space 39 is substantially the same as the distance H between the upper edge of the drain opening of the first connecting path 43 'and the outer peripheral surface 53 . In the second and third functional positions of the valve arrangement 59 , a constant degree of filling of the working space 15 can be set, so that a different level, but constant in both functional positions, can be achieved via portable torque without having to - as in known liquid friction clutches required at constant drive speed - must be readjusted constantly.

Fig. 5 shows a diagram, on the abscis senachse the differential speed Δn of the drive of the fluid friction clutch 1 , that is, depending on the form of implementation of the clutch, the rotor or Ge housing speed, and on the ordinate axis from the rotor to the housing or from the housing to the Rotor transferable torque M d is applied. The characteristic curve III is realized in the third functional position of the valve arrangement 59 shown in FIG. 4B, in which the storage space 39 is largely emptied and there is a large amount of liquid in the working space 15 . The portable torque is therefore greatest. The characteristic line II corresponds to the second functional position of the valve arrangement 59 shown in FIG. 4C, in which the outer first connecting path 43 is closed and the other, radially inner he ste connecting path 43 'is opened, so that the storage space 39 is only partially emptied and thus the work space 15 is only partially filled. There is a correspondingly smaller via portable torque than in the functional position of the valve arrangement shown in FIG. 4B. The characteristic curve I corresponds to the functional position of the valve arrangement 59 shown in FIG. 4A, in which the storage space 39 is essentially completely filled, which means that the working space 15 is emptied accordingly, so that practically no torque from the rotor 19 to the housing 5 can be worn over. When looking at the characteristic curves I to III it is clear that in all functional positions of the valve arrangement 59, the transmitted torque is independent of the differential speed of the drive shaft 17 or the rotor 19 .

In summary, it should be noted that in all embodiments of the liquid friction clutch 1 with the aid of the valve arrangement 59, a differential speed-independent transferable torque is adjustable.

Claims (10)

1. Fluid friction clutch with at least one rotor which can be coupled to a drive shaft and which is arranged in a working space of a housing which can be at least partially filled with liquid, with a storage space for the liquid arranged in the rotor, the storage space via at least a first connection path to the arm beitsraum and the working space verbun a second connection path to the storage space over at least the are, and with a valve arrangement, with de ren means of the fluid level in the working chamber be einflußbar is characterized in that the valve arrangement (59) is formed such that in a first Functional position of the valve arrangement ( 59 ), the first and second connecting paths ( 43 , 45 ) can be closed.
2. Fluid friction clutch according to claim 1, characterized in that in a second func tional position of the valve arrangement ( 59 ) only the ste connection path ( 43 ) between the storage space ( 39 ) and the working space ( 15 ) can be closed.
3. Fluid friction clutch according to claim 1 or 2, characterized in that in a drit th functional position of the valve arrangement ( 59 ) only the second connection path ( 45 ) between the working space ( 15 ) and the storage space ( 39 ) can be closed.
4. Fluid friction clutch according to one of the preceding claims, characterized in that in the first functional position of the valve arrangement ( 59 ) located in the working space ( 15 ) liquid only circulates within the working space ( 15 ).
5. Fluid friction clutch with at least one rotor which can be coupled to a drive shaft and which is arranged in a working space of a housing which can be at least partially filled with liquid, with a storage space for the liquid arranged in the rotor, the storage space via at least a first connection path to the arm beitsraum and the working area are connected to the storage room via at least one second connecting path, and with a valve arrangement with which the liquid level in the working area can be influenced, characterized in that at least two first connecting paths ( 43 , 43 ') between the storage room ( 39 ) and work space ( 15 ) are provided, the radial distance from the axis of rotation ( 33 ) of the rotor ( 19 ) is different, and that the valve assembly ( 59 ) is designed such that in a first functional position at least one of the first connecting paths ( 43 ; 43 ') can be closed, the other e first connection path ( 43 '; 43 ) is at least partially open.
6. Fluid friction clutch according to claim 5, characterized in that in a second func tional position of the valve arrangement ( 59 ) both first connecting paths ( 43 , 43 ') can be closed.
7. Fluid friction clutch according to one of the preceding claims 5 or 6, characterized in that in the first functional position of the valve arrangement ( 59 ) be in the working space ( 15 ) be sensitive liquid circulates through the storage space ( 39 ).
8. Fluid friction clutch according to one of the preceding claims, characterized in that the valve arrangement ( 59 ) can be actuated with the aid of at least one electromagnet ( 67 ).
9. Fluid friction clutch according to one of the preceding claims, characterized in that a level change of the storage space ( 39 ) can be brought about with the aid of a conveying device for the liquid.
10. Fluid friction clutch according to one of the preceding claims, characterized in that it is designed as a preassembled unit.
DE1999140537 1999-08-26 1999-08-26 Fluid friction clutch Withdrawn DE19940537A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE1999140537 DE19940537A1 (en) 1999-08-26 1999-08-26 Fluid friction clutch

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1999140537 DE19940537A1 (en) 1999-08-26 1999-08-26 Fluid friction clutch
PCT/EP2000/008352 WO2001014759A1 (en) 1999-08-26 2000-08-26 Ventilator coupling

Publications (1)

Publication Number Publication Date
DE19940537A1 true DE19940537A1 (en) 2001-03-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
DE1999140537 Withdrawn DE19940537A1 (en) 1999-08-26 1999-08-26 Fluid friction clutch

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Country Link
DE (1) DE19940537A1 (en)
WO (1) WO2001014759A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7828529B2 (en) 2004-02-23 2010-11-09 Behr Gmbh & Co. Kg Regulatable drive for a motor vehicle component
DE102010043264A1 (en) * 2010-11-03 2012-05-03 Behr Gmbh & Co. Kg Adjustable fluid friction clutch for power regulation of coolant pump and for use in drive for driving coolant pump, has a propelled side and driven off side, which are separated from each other

Families Citing this family (8)

* Cited by examiner, † Cited by third party
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ES2253618T3 (en) 2002-08-23 2006-06-01 BEHR GMBH & CO. KG Viscose friction clutch.
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Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2153720A1 (en) * 1971-10-28 1973-05-03 Daimler Benz Ag Coupling, in particular for connecting a fan of a vehicle with a drive shaft
DE2748204A1 (en) * 1976-11-03 1978-05-18 Eaton Corp fluid coupling
DE2212367B2 (en) * 1972-03-15 1980-11-06 Daimler-Benz Ag, 7000 Stuttgart
GB2107438A (en) * 1981-10-09 1983-04-27 Daimler Benz Ag Temperature responsive fluid-friction clutch device for cooling fan
DE3242381C2 (en) * 1981-11-30 1986-05-28 Aisin Seiki K.K., Kariya, Aichi, Jp
DE2414017C2 (en) * 1973-05-24 1987-01-22 Dynair Ltd., Nailsworth, Gloucestershire, Gb
DE3932450A1 (en) * 1988-09-29 1990-05-10 Aisin Seiki A viscose fluid coupling
DE4030294A1 (en) * 1989-09-28 1991-04-11 Atsugi Unisia Corp Fluid coupling
EP0870943A1 (en) * 1997-04-09 1998-10-14 Eaton Corporation Heavy duty viscous fan drive and bracket mounting assembly therefor
DE19741073A1 (en) * 1997-09-18 1999-03-25 Behr Gmbh & Co Fluid friction clutch with primary disc on drive shaft
DE19742823A1 (en) * 1997-09-27 1999-04-01 Behr Gmbh & Co Liquid friction coupling for vehicle engine fans
DE19753725A1 (en) * 1997-12-04 1999-06-17 Behr Gmbh & Co Fluid friction coupling

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4011528A1 (en) * 1990-04-10 1991-10-17 Erwin Dipl Ing Lang Viscous clutch for automobile engine cooling fan - uses electromagnetic valves as clutch control elements in hydraulic circuit
DE19533641B4 (en) * 1995-09-12 2005-11-10 Behr Gmbh & Co. Kg Fluid friction clutch
DE19810296A1 (en) * 1998-03-10 1999-09-23 Mannesmann Sachs Ag Vehicular fluid clutch with fluid passage to and from reservoir with variable characteristics

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2153720A1 (en) * 1971-10-28 1973-05-03 Daimler Benz Ag Coupling, in particular for connecting a fan of a vehicle with a drive shaft
DE2212367B2 (en) * 1972-03-15 1980-11-06 Daimler-Benz Ag, 7000 Stuttgart
DE2414017C2 (en) * 1973-05-24 1987-01-22 Dynair Ltd., Nailsworth, Gloucestershire, Gb
DE2748204A1 (en) * 1976-11-03 1978-05-18 Eaton Corp fluid coupling
GB2107438A (en) * 1981-10-09 1983-04-27 Daimler Benz Ag Temperature responsive fluid-friction clutch device for cooling fan
DE3242381C2 (en) * 1981-11-30 1986-05-28 Aisin Seiki K.K., Kariya, Aichi, Jp
DE3932450A1 (en) * 1988-09-29 1990-05-10 Aisin Seiki A viscose fluid coupling
DE4030294A1 (en) * 1989-09-28 1991-04-11 Atsugi Unisia Corp Fluid coupling
EP0870943A1 (en) * 1997-04-09 1998-10-14 Eaton Corporation Heavy duty viscous fan drive and bracket mounting assembly therefor
DE19741073A1 (en) * 1997-09-18 1999-03-25 Behr Gmbh & Co Fluid friction clutch with primary disc on drive shaft
DE19742823A1 (en) * 1997-09-27 1999-04-01 Behr Gmbh & Co Liquid friction coupling for vehicle engine fans
DE19753725A1 (en) * 1997-12-04 1999-06-17 Behr Gmbh & Co Fluid friction coupling

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7828529B2 (en) 2004-02-23 2010-11-09 Behr Gmbh & Co. Kg Regulatable drive for a motor vehicle component
DE102010043264A1 (en) * 2010-11-03 2012-05-03 Behr Gmbh & Co. Kg Adjustable fluid friction clutch for power regulation of coolant pump and for use in drive for driving coolant pump, has a propelled side and driven off side, which are separated from each other

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