CN111609207A

CN111609207A - Valve core for fluid control valve and fluid control valve

Info

Publication number: CN111609207A
Application number: CN202010107730.7A
Authority: CN
Inventors: R.魏斯; I.库默勒
Original assignee: Youomar Plastic Parts Kunshan Co ltd
Current assignee: Youomar Plastic Parts Kunshan Co ltd; Joma Polytec GmbH
Priority date: 2019-02-22
Filing date: 2020-02-21
Publication date: 2020-09-01
Also published as: DE102019202429A1

Abstract

The invention relates to a valve cartridge for a fluid control valve, with: a cage portion configured for receipt within the valve housing, the cage portion including a first control disk, the first control disk being penetrated by a first control groove; and a valve element accommodated in the holder part so as to be rotationally movable about the center axis, the valve element comprising a first control section which is arranged adjacent to the first control disk and extends transversely to the center axis, the first control section being configured to release or block the first control groove depending on the rotational position of the valve element; and a deformation element which is connected with the first end region to the holder part and with the second end region to the valve part and is designed to introduce a rotational movement to the valve part for a temperature-dependent profile change.

Description

Valve core for fluid control valve and fluid control valve

Technical Field

The present invention relates to a valve cartridge for a fluid control valve and a fluid control valve.

Background

Fluid control valves are generally known and are used, inter alia, to influence fluid flow in a closed fluid circuit. In the automotive field, fluid control valves are used, for example, for temperature control in cooling circuits, for example in water-cooling circuits or oil-cooling circuits. In this case, a heat source, for example an internal combustion engine, an electric motor or a battery for an electric motor, is typically connected to one another in fluid communication with the conveying device and the fluid control valve and, in particular, a radiator in the form of a heat exchanger or a cooler in a cooling circuit. The task of a fluid control valve is now to regulate the temperature of the fluid to a predefinable value. For this purpose, it can be provided that the fluid control valve, depending on the temperature of the fluid flowing out of the heat source, directs a predeterminable first component of the fluid back again directly to the heat source, while a second component of the fluid is supplied to the heat sink, in order to provide fluid cooling there, for example by heat exchange with the ambient air. Such fluid control valves are also referred to as thermostat valves or temperature regulators and can be installed, for example, in the case of oil cooling devices for internal combustion engines in a valve module which, in addition to a valve housing for the fluid control valve, also contains a pump and an oil filter and which is also referred to as an oil module or an oil management module.

The valve slide is a component of the fluid control valve and comprises, in particular, a temperature-dependently adjustable valve part, to which an actuating device for changing the position of the valve part temperature-dependently is assigned. Furthermore, the valve slide can also have a valve seat which is provided for interacting with the valve element, so that the flow cross section for the fluid flow can be influenced, in particular can be at least partially blocked or released, when the position for the valve element is changed.

Disclosure of Invention

The object of the invention is to provide a valve cartridge and a fluid control valve with improved durability.

This object is achieved with a valve cartridge of the type mentioned at the outset with the features of claim 1. The valve core includes: for receiving a cage part which is formed in the valve housing and is provided with a first control disk which is penetrated by a first control groove; and a valve element accommodated in the holder part so as to be rotatable about the center axis, the valve element comprising a first control section which is arranged adjacent to the first control disk and extends transversely to the center axis, the first control section being configured to release or block the first control groove depending on the rotational position of the valve element; and a deformation element which is connected with the first end region to the holder part and with the second end region to the valve part and which is designed to introduce a rotational movement to the valve part for a temperature-dependent shape change.

One of the main tasks of the cage part is to provide a pivoting support structure for the valve member and a torque support structure for the deformation element. This allows a relative movement between the valve part and the retainer part that can be moved in a pivoting manner, independently of the valve housing designed to receive the valve slide. This allows, for example, the functional checking of the valve slide during manufacture before it is inserted into the valve housing. Furthermore, the cage part also provides a control disk which is penetrated by the first control groove and thus provides the function of a valve seat. The control recess forms a section of the fluid channel which extends, for example, from the person to the heat sink and which can be completely blocked, partially blocked or completely released by the valve element as a function of the temperature of the fluid. For this purpose, the valve part comprises a control section extending transversely to the central axis, which control section can partially or completely block or completely release the free cross section of the control groove as a function of the rotational relative movement between the valve part and the control disk.

The deformation element has the task of providing a pivoting movement of the valve part relative to the holder part as a function of the temperature of the fluid flowing through the valve slide. The deformation element is preferably designed for a completely autonomous mode of operation, so that no external input of actuating energy, such as current, is required. Rather, the operating energy required for the movement of the deformation element for the valve element is derived from the thermal energy of the fluid to be conveyed.

In particular, it is preferably provided that the deformation element is designed to convert thermal energy of the fluid to be supplied directly into a relative movement of the valve part relative to the holder part. This direct conversion can be brought about, for example, in that the deformation element is made at least partially of a material which can change its shape as a function of the temperature of the fluid to be conveyed. Such a change in shape can occur, for example, as an isotropic or anisotropic expansion or contraction of the deformation element or of a partial region of the deformation element.

Preferably, the fluid flow in the region of the first control disk or of the associated first control section has a flow direction which is at least substantially parallel to the center axis of the valve element, and the relative movement between the valve element and the control section of the control disk takes place in a plane which is oriented transversely to the center axis. Pressure fluctuations, in particular pulsations, of the flowing fluid do not influence or change the position of the valve element. In addition, the wear of the valve element associated therewith is thereby kept at a low level.

Advantageous embodiments of the invention are the subject matter of the dependent claims.

The deformation element is expediently configured as a torsion bar, in particular made of a shape memory alloy, which extends coaxially to the central axis. The torsion bar is preferably made of a nickel-titanium alloy having shape memory properties. In the production of the torsion bar, this torsion bar initially has a predetermined contour, which is changed by elastic-plastic deformation when it is inserted into the valve slide. Once the torsion bar has a temperature above the material-specific profile change temperature based on the fluid flowing around it, it is strived to have its original profile again. If the torsion bar is rotated about the central axis, for example, from its initial configuration by a twisting movement of the first end region relative to the second end region, the torsion bar, when exceeding its material-specific configuration change temperature, executes an opposite twisting movement and can thereby exert a torque on a component, such as a valve element. The pivotal movement of the valve member is thus caused on the basis of the relative movement of the second end region of the torsion bar with respect to the first end region.

In an advantageous embodiment of the torsion bar, the torsion bar is made of a shape memory material, which achieves a two-way memory effect. The torsion bar has a shape which can be fixedly predefined both at temperatures below its material-specific shape change temperature and at temperatures above its material-specific shape change temperature. The torsion bar accordingly has one of the predetermined profiles or, if appropriate, occupies an intermediate position, depending on the temperature of the surrounding fluid. In one embodiment of the torsion bar made of a shape memory material which achieves a two-way memory effect, it is not necessary to apply a restoring force or a restoring torque to the deformation element in order to ensure a desired temperature-dependent position of the valve part relative to the cage part, so that the restoring device can be dispensed with here.

In a further embodiment of the invention, it is provided that the deformation element comprises a sleeve-like, one-sided closed cylindrical housing and a working piston which is accommodated in the cylindrical housing in a linearly movable manner and is coupled to the piston rod, wherein a working chamber which is delimited by the cylindrical housing and the working piston is filled with an expansion material, in particular with an expansion wax, and wherein, for the movement conversion of the temperature-dependent linear movement of the piston rod into a pivoting movement of the valve part, a spiral geometry is formed on the valve part coaxially to the center axis, into which spiral geometry the coupling part of the piston rod engages. Here, the deformation element is configured to provide a linear movement depending on the temperature of the surrounding fluid. The linear movement is based on a temperature-dependent, preferably isotropic, expansion or contraction of the expansion material, which may in particular be an expansion wax. The expansion material is preferably adapted to the temperature range in which the change in shape of the deformation element should occur, such that in this temperature range a phase change of the expansion material (in particular from solid phase to liquid phase) occurs, so that in this temperature range a particularly large change in shape can be caused.

The linear movement introduced by the expanding or contracting expanding material onto the working piston and the piston rod connected thereto must then be converted into a pivoting movement of the valve member. For this purpose, the valve part is formed with a thread-like spiral geometry, in particular with a groove-like depression or a spiral projection. The pitch of the helical geometry is preferably selected such that a self-locking is avoided by the coupling connected to the piston rod when the linear movement is initiated. The coupling piece can in particular be a compression nut which surrounds a tenon-shaped section of the valve part which is provided with a helical geometry and which is provided with a coupling geometry corresponding to the helical geometry. It is likewise possible to provide for a kinematically opposite arrangement of the locking nut on the valve part and of the tenon-like section on the piston rod.

Preferably, a restoring means, preferably a restoring spring, in particular a helical spring, is arranged between the valve element and the cage part for providing a restoring force or a restoring torque, which opposes the restoring force provided by the deformation element or the torque provided by the deformation element. The resetting means serve, in particular, to ensure a resetting movement of the valve element into a predetermined valve position when the temperature of the fluid to be delivered drops. Such a resetting means is particularly provided if the deformation element is not designed to cause such a resetting movement without an external force.

In a deformation element which can provide a linear movement on the basis of an expanding material, the contraction movement is at a much lower force level than the expansion movement, it is then advantageous to use a return means, in particular a return spring, for a reliable return of the valve member. In this case, the restoring spring can be designed to provide an axial force, preferably parallel to the center axis or coaxial to the center axis, in order to thereby deform the deformation element back to the original shape again below the material-specific shape change temperature.

Alternatively, it can also be provided that a restoring means is used in such a deformation element in order to introduce a restoring torque on the valve element. For example, the indirect resetting of the deformation element can be brought about by introducing a resetting torque on the valve part, effected via a combination of a helical geometry on the valve part and a coupling of the piston rod, which serves as a transmission.

In the deformation element embodied as a torsion bar, the return means is preferably embodied as a helical spring which is connected in a rotationally fixed manner to the cage part and to the valve part. The elastic deformation of the helical spring is achieved during the pivoting movement of the valve part about the center axis, wherein the helical spring undergoes a diameter increase or a diameter decrease and can store kinetic energy. The stored kinetic energy is introduced as a restoring torque to the valve element, so that the valve element can deform the deformation element, which is likewise connected in a rotationally fixed manner to the cage part and the valve element, again to a shape, at a temperature below the material-specific shape change temperature, in which the valve element assumes a predefinable preferred position in comparison with the first control disk.

In a further embodiment of the invention, it is provided that the valve element is arranged in the holder part between a first control disk arranged coaxially to the center axis and a second control disk arranged coaxially to the center axis, wherein the second control disk is penetrated by a second control groove, and wherein the valve element comprises a second control section arranged adjacent to the second control disk and extending transversely to the center axis, which second control section is designed to release or block the second control groove depending on the rotational position of the valve element. In this embodiment of the valve slide, a first valve is provided by the combination of the first control disk and the first control section, and a second valve is provided by the second control disk in combination with the second control section. Depending on the geometric arrangement of the first and second control grooves and of the first and second control sections, it is possible, for example, to open and close the two valves synchronously or to carry out phase-shifted, in particular counterclockwise, opening and closing of the two valves.

Preferably, the first control recess has an angular offset relative to the second control recess with reference to the center axis and/or the first control section has an angular offset relative to the second control section with reference to the center axis. By virtue of the fact that the corresponding angular offset can be based on a fixed connection of the first control section to the second control section or of the first control disk provided with the first control groove to the second control disk provided with the second control groove, a valve function of the two valves, which can be predetermined by a correspondingly configured valve element, is achieved in relation to the pivot position of the valve element. This enables, for example, the temperature-dependent division of the fluid flow into a plurality of partial flows, of which one partial flow can be supplied to the heat sink and the other partial flow can be supplied directly to the heat source.

In a further embodiment of the invention, it is provided that the first control section and the second control section are each designed in the form of a disk, and that each of the control sections has at least one control opening, which is oriented, in particular, parallel to the central axis. In the disk-shaped design of the two control sections, the circular, axially oriented end face of the valve part serves a dual function, namely both for influencing the respective fluid flow and as a bearing surface for the opposite cage part. In particular, it can be provided that the valve part is accommodated in a sliding-mounted manner in the holder part and is supported there on a respectively associated control disk of the holder part. The control openings formed in the respective control portion have an adjustable overlap with the control recesses formed in the respective control disk, depending on the pivot position of the valve part relative to the holder part and the associated control disk, so that the cross section of the respective valve can be influenced depending on the pivot position of the valve part. For this purpose, it is provided in particular that the first control recess and the second control recess are each embodied as a recess oriented parallel to the center axis.

In an advantageous embodiment of the invention, it is provided that the cage section is formed by a first cage section, which comprises the first control disk and the receiving section for the first end region of the deformation element, and a second cage section, which comprises the second control disk and is coupled to the first cage section. The first cage segment and the second cage segment, respectively, are preferably produced as plastic injection molded parts, in particular from fiber-reinforced and/or slip-modified (PTFE-filled) plastics (for example polyphenylene sulfide/PPS or aliphatic polyketone/PK). Furthermore, it is preferably provided that the first cage segment and the second cage segment are connected to one another by a positively acting latching connection or a welded joint, and that the outer circumferential surfaces of the first control disk and of the second control disk are designed to bear in particular sealingly against the inner surface of the valve housing. The specific orientation of the first cage part relative to the second cage part, in particular taking into account the angular position relative to the center axis, can be ensured by corresponding, positively acting projections and recesses on the two cage parts. The first cage part and/or the second cage part additionally or alternatively on their outer circumference, in particular in the region of the control disk, are adapted to the inner surface of the valve housing in such a way that an at least approximately fluid-tight seal or gap seal is achieved with respect to the valve housing. Furthermore, it may alternatively be provided that the control disks are each separately formed and are accommodated on a common holder part.

In particular, it is preferably provided that the two control disks are arranged coaxially spaced apart from one another along the center axis, and the valve element is arranged between the two control disks. The valve part can be designed as a plastic injection-molded part and preferably has a cylindrical or round sleeve-like outer shape with two annular bead contours arranged at a distance from each other along the center axis and extending radially outward around the circumference, which form disk-shaped control sections and are each penetrated by at least one control opening oriented in particular parallel to the center axis.

Furthermore, provision is made for a receiving section to be formed on the first holder section, which receiving section serves to fix a first end region of the deformation element, and for a second end region of the deformation element to be fixed to the valve part in the embodiment of the deformation element as a torsion bar. Thus, when the outer shape of the torsion bar changes, a desired pivoting movement of the valve part relative to the first cage section and the second cage section, which is fixedly connected thereto, takes place. The free cross section of the two control grooves and the control opening of the valve member which moves relative to the control grooves can thereby be influenced as desired.

The object of the invention is also achieved by a fluid control valve for influencing a fluid flow. The fluid control valve comprises a valve housing in which a valve slide according to the invention is accommodated, wherein the valve housing has a first input connection which is connected in fluid communication with a first valve chamber which is delimited by a first inner wall section of the valve housing and by a side of a first control disk facing away from the valve element, wherein the valve housing has a first output connection which is connected in fluid communication with a second valve chamber which is delimited by a second inner wall section of the valve housing and by a side of the first control disk facing the valve element.

In this embodiment of the fluid control valve, the fluid control valve is used for blocking or throttling a fluid flow, wherein fluid can be provided at the input connection and can flow into the first valve chamber, from there through the first control recess into the second valve chamber, which is connected in fluid communication with the first output connection, depending on the relative pivot position of the valve part relative to the holder part, depending on the pivot position of the first control section, through which the fluid can subsequently flow out.

In a further embodiment of the fluid control valve, it is provided that the valve housing has a second output connection which is connected in fluid communication with the first valve chamber. In this case, it can be provided that the fluid flow provided at the first inlet connection is provided at the first outlet connection directly at the second outlet connection or at least partially or completely after flowing through the first control recess in the first control disk into the second valve chamber, depending on the pivoting position of the valve part relative to the holder part.

In a further embodiment of the invention, it is provided that a second inlet end connection is formed on the valve housing, which is connected in fluid communication with a third valve chamber, which is delimited by a third inner wall section of the valve housing and by a side of the second control disk of the cage part facing away from the valve element. In particular, it is provided here that the fluid control valve can be traversed by a fluid flow provided at the second input connection in addition to the fluid flow provided at the first input connection, wherein, depending on the pivot position of the valve part relative to the cage part, a mixing of the parts of the two fluid flows and an outflow of at least one part of the two fluid flows through the first output connection can be provided.

Drawings

Advantageous embodiments of the invention are shown in the drawings. In the drawings:

FIG. 1 is a schematic illustration of a cooling circuit for an internal combustion engine, with a fluid control valve shown in cross-section according to a first embodiment, configured for regulating the temperature of oil in the cooling circuit by means of a torsion bar made of a shape memory material;

fig. 2 is a perspective exploded view of the fluid control valve according to fig. 1;

FIG. 3 is a second embodiment of a fluid control valve shown in cross-section, configured for regulating oil temperature in a cooling circuit via a wax expansion element, with the valve member in a first rotational position; and is

Fig. 4 is a detail view in section of the valve element according to fig. 3 in a second rotational position.

Detailed Description

The cooling circuit 1 shown schematically in fig. 1 is formed purely by way of example by a pump 2, an oil filter 3, an internal combustion engine 4, a fluid control valve 5 and a heat exchanger 6, which are connected to one another in a fluid-communicating manner by means of connecting lines 15 to 20, respectively.

The components shown in fig. 1: the pump 2, the oil filter 3, the combustion engine 4 and the heat exchanger 6 are only used to illustrate possible use cases of the fluid control valve 5 and are therefore not described in detail.

In principle, it is assumed that the pump 2 is designed to convey oil through the oil filter 3 into the internal combustion engine 4, wherein the internal combustion engine 4 is flowed through by the oil flow provided by the pump 2. During the flow through the internal combustion engine 4, heating of the oil flow takes place as a result of the combustion process taking place there, wherein for advantageous operation of the internal combustion engine 4 a predetermined temperature window (temperature interval) for the oil flow through the internal combustion engine 4 is observed. For this reason, the oil flow from the internal combustion engine 4 is supplied to the fluid control valve 5, in order there to be completely or only partially or even not fed to the heat exchanger 6 depending on the oil temperature. The heat exchanger is configured in particular for heat dissipation from the oil flowing out into the ambient air for the cooling circuit 1. The (partial) oil flow through the heat exchanger 6 is then fed back to the flow control valve 5 and from there can be fed again to the heat exchanger 6 at least partially again, depending on the now existing oil temperature, or fed back to the pump 2 partially or completely.

To form the cooling circuit 1, the pump 2 is connected in fluid communication with the oil filter 3 by a connecting line 15, which in turn is connected in fluid communication with the internal combustion engine 4 by a connecting line 16. The cooling channels provided for the oil flow in the combustion engine 4 are not illustrated for the sake of clarity. The oil flow from the internal combustion engine 4 is supplied via the connecting line 17 to the first input connection 21 of the fluid control valve 5 and, depending on the operating position of the control valve 5, which will be explained in more detail below, to the first output connection 23 or the second output connection 24 or both

output connections

23, 24.

The first output terminal fitting 23 is connected in fluid communication with the heat exchanger by the connecting line 18. The second outlet connection 24 is connected to the pump 2 via the connecting line 20. Furthermore, it is provided that the heat exchanger 6 is connected via a connecting line 19 to a second inlet connection 22 of the fluid control valve 5.

The fluid control valve 5, which is shown purely by way of example in fig. 1 and 2, comprises a valve housing 30, which is only schematically illustrated, is of substantially sleeve-like design and closed on one side (except for the second input connection 22), and in whose bead-like recess 33 a valve slide 40 is accommodated. In order to ensure a fluid-tight design of the valve housing 30 in addition to the two

inlet connections

21, 22 and the two

outlet connections

23, 24, a terminal cover 32, which is in principle cup-shaped, in particular rotationally symmetrical, is arranged on the open-end region 31 of the valve housing 30. The terminal cover 32 is pressed in a force-fitting manner into a cylindrically formed recess 35 of the recess 33 of the valve housing 30 and with a circumferential bead 36 bears against a circular end face 37 formed therefrom, in order to ensure a predetermined positioning of the terminal cover 32 along the center axis 34 of the valve housing 30. Furthermore, a sealing ring 57 is provided for sealing before the valve housing 30 and the terminal cover 32.

Furthermore, a first cage part 41 of substantially cup-shaped design, a second cage part 42 of likewise substantially cup-shaped design, a valve part 43 of similar design to the spinning tube, a torsion bar 44, also referred to as a deformation element, and a receiving part 45, which are described in detail below, are arranged in the recess 33.

As is evident from the illustration in fig. 1, the first cage part 41, the second cage part 42 and the receiving part 45 are arranged coaxially to the central axis 34, wherein the first cage part 41 and the second cage part 42 are firmly and thus also non-rotatably connected to one another, in a manner not shown in detail, in particular by gluing or welding or latching/clamping.

As can be seen from fig. 2, the receiving portion 45 comprises a coupling ring 46 which is oriented coaxially to the central axis 34 and has radially projecting projections 47 which can engage in a form-fitting manner in corresponding recesses 48 of the first holder part 41 and thus ensure a rotationally fixed locking of the receiving portion 45 on the first holder part 41. Furthermore, the receiving portion 45 comprises a sleeve-like receiving section 50 which is fixed by radial spokes 49 on the coupling ring 46. The receiving section 50 is provided on the end side with a purely exemplary square recess 51, which can be seen in fig. 2, and which is designed to receive a correspondingly square end region 58 of the torsion bar 44. A circular bore 52, which is configured purely by way of example as a conical section, is connected to the recess 51, the inner diameter of which bore is selected to be much larger than the outer diameter of the torsion bar 44, so that the torsion bar 44 is accommodated freely movably in the bore 52. Purely by way of example, the receiving portion 45 has a circumferential, axially aligned groove 53 facing away from the

holder portions

41 and 42, in which a ring-shaped elastomer spring 54 is received, which is supported on a ring-shaped end face 55 of the terminal cover 32. The task of the elastomer spring 54 is essentially to press the assembly formed by the first cage part 41, the second cage part 42 and the receiving part 45 against the end face 38 of the annular bead 39 formed in the valve housing 30 and thus to determine the position of the assembly along the axis of the central axis 34.

The first cage part 41 has, on its outer wall 65 of cylindrical design, purely by way of example, sections 66 which are each configured with the same angular degree and with the same rectangular contour, which sections can coincide with the first input end connection 21 and the first output end connection 23 of the valve housing 30, as shown in fig. 1. The cross section 66, as shown in fig. 1, always and independently of the rotational position of the valve member 43, enables a fluid flow from the first input connection 21 to the first output connection 23.

The base section 67 of the first cage part 41 is purely exemplary of a disk-shaped design and is provided, for example, with four control grooves 68, each of which is constructed symmetrically to the central axis with the same angular degree. The control recess 68 enables fluid flow from the first input connector 21 to the second output connector 23 in accordance with the rotational position of the valve member 43 as shown in fig. 1. The bottom section 67, which may also be referred to as a first control disk, has end faces 69, 70, which are configured purely exemplarily as flat axes.

The second cage section 42 has substantially the same construction as the first cage section 41. On the outer wall 75 of cylindrical design, four rectangular cross sections 76 are arranged purely by way of example with the same angular degree. One of the cross-sections 76 coincides with the second output end fitting 24 as shown in fig. 1.

The bottom section 77, which can also be referred to as a second control disk, is provided with second control grooves 78, which are each arranged symmetrically to the central axis 34 with the same angular degree. The axial end faces 79 and 80 of the bottom section 77 are configured purely by way of example flat.

In contrast to the second holder part 42, the first holder part 41 has a central through-bore 71 in the base section 67, into which a circularly configured guide section 85 of the valve part 43 engages. Provision is made, by way of example, for the guide section 85 to extend completely through the central through-bore 71.

The first cage part 41 and the second inner wall section 25 of the valve housing 30 together form a first valve chamber 27, to which the first input end connection 21 and the first output end connection 23 are assigned. Furthermore, the first and

second holder parts

41, 42 form, with the second inner wall section 26 of the valve housing 30, a second valve chamber 28, to which the second output-end connection 24 is assigned. Furthermore, the third inner wall section 61 of the valve housing 30 and the second holder part 42 form a third valve chamber 62, to which the second input-end connection 22 is assigned.

The valve element 43, which is embodied in the manner of a spinning bobbin, as shown in fig. 1 and 2, comprises a base body 86, which is embodied in the form of a circular sleeve and on which two

valve disks

87 and 88, which are arranged at a distance from one another along the center axis 34 and project radially and are embodied in the form of a circular disk and can also be referred to as a control section. Each valve disk is provided purely by way of example with four annular segment-shaped

recesses

89, 90 which are formed at the same angular degree relative to the central axis.

As is apparent from the illustration in fig. 1 and 2, the purely exemplary annular segment-shaped control recesses 68 and 78 of the two

cage segments

41, 42 respectively have a perfect coincidence with one another in a projection plane, not shown, oriented transversely to the center axis 34.

Furthermore, it is apparent from the illustration in fig. 2 that the

recesses

89 and 90 have the same contour on the valve disks 87 and 88 (along the center axis 34), but have an angular deviation of approximately 30 degrees in a projection plane, not shown in detail, oriented transversely to the center axis 34. Furthermore, it is provided that the extent of the control recesses 68 and 78 in the circumferential direction is selected to be smaller than the extent of the

recesses

89 and 90 in the circumferential direction of the

valve disks

87 and 88, in order to ensure a reliable sealing effect also taking into account the manufacturing tolerances that occur. Correspondingly, the mixing of the fluid flows provided at the first input connection 21 and at the second input connection 22 can take place as necessary depending on the rotational position of the valve part 43 relative to the first holder part 41 and the second holder part 42. Preferably, the

control disks

67, 77 and the valve disk 87 are provided. 88 are adjusted relative to one another in such a way that gentle opening is ensured by the

control recess

68 or 78 and the

recess

89 or 90, respectively. In addition or alternatively, it is provided that the torsion bar 44 is designed for a pivoting movement of the valve element 43 between the first end position and the second end position in an angular interval of, for example, 30 °. For higher torques on the valve element 43, the angle interval is selected to be smaller and is, for example, 20 degrees.

In order to vary the rotational position of the valve element 43 relative to the first and

second holder parts

41, 42 in a temperature-dependent manner, the torsion bar 44 is provided on its second end region 59 with a square profile extending along the central axis 34 in the same manner as on the first end region 58. The second end region 59 of the torsion bar 44 engages in a purely, for example, square recess 91 in the valve part 43 and is therefore received in the valve part 43 in a rotationally fixed manner.

The axial end faces 92 and 93 of the

valve disks

87 and 88 are configured purely by way of example flat and bear against the axial end faces 70 and 79 of the

cage parts

41 and 42 in a sliding manner, thereby ensuring a sliding bearing for the valve part 43 relative to the two

cage parts

41 and 42.

It is also provided that a helical spring 99, which is arranged coaxially with the central axis 34, is fixed in a rotationally fixed manner on the annular end face 94 of the guide section 85. The coil spring 99 is also fixed in a rotationally fixed manner on the annular end face 56 of the receiving section 50.

The operation of the fluid control valve 5 is explained in detail below with reference to the diagram of fig. 1:

the diagram of fig. 1 shows an initial position for the fluid control valve 5, which is present, for example, when the oil supplied by the internal combustion engine has a temperature T1 and is below the temperature required for cooling the oil. At this oil temperature T1, there is a torque balance between the helical spring 99, which is prestressed into torsion, and the torsion bar 44, which is deformed in part elastically and plastically in the context of the rotational movement about the central axis 34. The internal stresses of the torsion bar 44 and of the helical spring 99, which are respectively caused by the torques acting opposite one another, are matched to the geometry of the first holder 41, of the second holder 42 and of the valve element 43 in such a way that the recess 89 in the first valve disk 87 coincides with the control recess 68 in the bottom section 67 of the first holder part 41, which is also referred to as the first control disk. Thereby achieving a fluid flow from the first input terminal connection 21 to the second output terminal connection 24. Correspondingly, there is a direct fluid-communicating connection between the first input connection 21 and the second output connection 24 and oil can flow directly from the internal combustion engine 4 via the fluid control valve 5 to the pump 2 again in order there to enter the internal combustion engine 4 again after passing through the oil filter 3. In addition or alternatively, it can be provided that the valve part 43, the torsion bar 44 or the helical spring 99 are assigned stops, not shown in detail, which limit the torsional movement of the torsion bar 44 and/or the pivoting movement of the valve part 43, in order to thereby avoid overloading the torsion bar 44.

A fluid flow from the first input connection 21 to the first output connection 23 is also achieved in principle on the basis of the cross section 66 in the first cage part 41 coinciding with both the first input connection 21 and the first output connection 23. A further flow of oil through the connecting line 18 to the heat exchanger 6 and from there via the connecting line 19 to the second inlet connection 22 of the fluid control valve 5 is prevented on the basis of the blocking action of the second valve disk 88. This achieves a blocking effect, i.e. the second valve disk 88 of the valve part 43 closes the control recess 78 in the bottom section 77 of the second cage part 42, which is also referred to as the second control disk. Therefore, no oil flow occurs here, and therefore no heat exchange of the oil with the ambient air in the heat exchanger 6, which is important for the oil temperature, occurs.

Due to the sleeve-like shape of the bore 52 in the receiving section 50 and of the base body 86 of the valve element 43, the torsion bar 44 is constantly acted upon by the oil flow from the first input connection 21 to the second output connection 24 with a respectively dynamic oil temperature.

As soon as the oil temperature rises on the basis of the combustion process in the internal combustion engine 4, a heat transfer from the oil to the torsion bar 44 takes place, so that this heat transfer brings about a return deformation of the torsion bar 44 to its initial contour at the point in time at which the oil reaches a temperature T2, which temperature T2 corresponds to the material-specific contour change temperature of the shape memory material of the torsion bar 44. The torsion bar 44 is inserted into the fluid control valve 5 in such a way that it undergoes a torsional deformation at temperatures below the material-specific profile-change temperature on account of the introduction of a torque by means of a helical spring 99 prestressed in torsion about the central axis 34 and the valve element assumes the aforementioned basic position.

Upon reaching the material-specific profile-change temperature, a return of this torsional deformation now occurs, since with increasing oil temperature the torque of torsion bar 44 is also greater than the return torque of helical spring 99. A pivoting movement of the second end region 59 relative to the first end region 58 takes place and a corresponding rotational movement of the valve element 43 about the central axis 34 takes place.

Due to this rotational movement, on the one hand, the freely flowing cross section between the first input connection 21 and the second output connection 24 changes, since the overlap between the recess 89 of the first valve disk 87 and the control recess 68 in the first cage part 41 is reduced.

The recess 90 in the second valve disk 88 of the valve member 43 and the control recess 78 in the bottom section 77 of the second cage part 42 are preferably designed in such a way that the freely passable cross section between the first output connection 23 and the second input connection 22 is enlarged in the same way as the freely passable cross section between the first input connection 21 and the second output connection 24 is reduced. A part of the oil flow provided by the internal combustion engine 4 can now flow through the heat exchanger 6, in order then to reenter the fluid control valve 5 at the second inlet connection 22 and to leave the fluid control valve 5 at the second outlet connection 24 in the direction of the pump 2.

At a further rising oil temperature, the rotational position of the valve element 43 is changed in such a way that the freely flowing cross section between the first input connection 21 and the second output connection 24 is completely closed, so that the oil flow provided by the internal combustion engine 4 flows only from the first input connection 21 to the first output connection 23 and, after flowing through the heat exchanger 6, through the second input connection 22 to the second output connection 24, and thus cooling of the entire fluid flow is ensured.

The second embodiment of the fluid control valve 105 shown in fig. 3 is provided with a valve slide 104, which is described in detail below, and which is configured differently from the valve slide 40, but does not differ significantly from the first embodiment of the fluid control valve 5 shown in fig. 1 and 2 in terms of the components provided directly for influencing the fluid flow. Correspondingly, functionally identical components have the same reference numerals.

The main difference between the valve spools 40, 104 of the two

fluid control valves

5, 105 is the manner in which a temperature-dependent movement of the

respective valve parts

43, 106 is provided, wherein in the fluid control valve 105 a wax expansion element 107 is used instead of the torsion bar 44 used in the fluid control valve 5. The design differences between the two

fluid control valves

5, 105 are essentially limited in that the wax expansion element 107 provides a temperature-dependent linear movement which is converted by means of the coupling 111 and the respectively associated valve part 106 into a pivoting movement of the valve part 106, while the torsion bar 44 directly executes a temperature-dependent torsional movement which can be introduced as a pivoting movement onto the associated valve part 43.

The wax expansion element 107, which may also be referred to as a deformation element, comprises a sleeve-like, unilaterally closed cylinder housing 112 and a working piston 113, which is only schematically illustrated by dashed lines, is accommodated in the cylinder housing 112 in a linearly movable sealing manner and is coupled to a piston rod 114. The working chamber 127 delimited by the cylindrical housing 112 and by the working piston 113 is filled with an expansion material, in particular with an expansion wax. Here, the cylindrical housing 112 forms a first end region of the wax expansion element 107, while the piston rod 114 forms a second end region of the wax expansion element 107.

When the expansion material heats up, this expands and moves the working piston 113 in the direction of the valve element 106, as a result of which the piston rod 114 coupled to the working piston 113 executes a linear movement along the central axis 34 and the coupling element 111, which is embodied purely as a cup, is moved relative to the valve element 106. The valve element 106 is accommodated here only in a pivoting manner between two

bottom sections

117 and 118, which are also referred to as control disks of the first cage part 115 and the second cage part 116.

Furthermore, it is provided that the coupling part 111 engages with at least one radially projecting pin 122 in a corresponding oblique groove 119 formed in a guide bore 120 of the valve part 106, wherein the oblique groove 119 is preferably formed helically with respect to the central axis 34. The angular position of the at least one angled groove 119 relative to the center axis 34 therefore produces a pivoting movement of the valve element 106 about the center axis 34 from the pivot position according to fig. 3 into the pivot position according to fig. 4 when the coupling element 111 is moved linearly. The angular position or slope of the angled slot 119 is selected such that self-locking between the coupling member 111 and the valve member 106 does not occur. Purely exemplarily, a pivot angle of about 30 degrees is defined for the valve member 106 between the two pivot positions.

Furthermore, during the aforementioned expansion movement of the expansion material and thus the linear movement of the piston rod 114 and the coupling element 111, the helical spring 99 accommodated in the guide bore 120 between the coupling element 111 and the bottom section 121 of the valve element 106 is compressed and thus stores a restoring energy by elastic deformation. This reset energy can move the coupling member 111 and piston rod 114 together relative to the valve member 106 as the expandable material subsequently cools as expansion of the expandable material diminishes. A return pivoting movement of the valve part 106 from the pivot position according to fig. 4 into the pivot position according to fig. 3 takes place here on the basis of the kinematic coupling between the coupling part 111 and the valve part 106 by means of the tongue 122 on the coupling part 111 and the groove 119 on the valve part 106.

The torque support for this pivoting movement is realized purely by way of example by means of a further radially projecting tongue 123 which is formed on the coupling 111 and engages into a straight groove 124 which is formed on a support section 125 of the first holder part 115. The support section 125 extends to the end face 126 of the cylindrical housing 112 and therefore ensures a secure axial fixing of the wax expansion element 107.

Claims

1. Valve cartridge (40; 104) for a fluid control valve (5; 105), with: a cage part (41, 42, 45; 115, 116) configured for being accommodated in the valve housing (30), the cage part comprising a first control disk (67; 117) which is penetrated by a first control groove (68); and a valve element (43; 106) which is accommodated in the holder part (41, 42, 45; 115, 116) so as to be rotatable about the center axis (34), said valve element comprising a first control section (87) which is arranged adjacent to the first control disk (67; 117) and extends transversely to the center axis (34), said first control section being designed to release or block the first control groove (68) depending on the rotational position of the valve element (43; 106); and a deformation element (44; 107) which is connected with the first end region (58; 112) to the cage part (14, 42, 45; 115, 116) and with the second end region (59; 114) to the valve element (43; 106) and is designed to introduce a rotational movement to the valve element (43; 106) for a temperature-dependent profile change.

2. Valve cartridge (40; 104) according to claim 1, characterized in that the deformation element (44) is configured as a torsion bar made of a shape memory alloy, in particular extending coaxially to the center axis (34).

3. Valve cartridge (40; 104) according to claim 1, characterized in that the deformation element (107) comprises a sleeve-like, one-sided closed cylindrical housing (112) and a working piston (113) which is accommodated in the cylindrical housing (112) in a linearly movable, sealed manner and is coupled to the piston rod (114), wherein a working chamber (127) which is bounded by the cylindrical housing (112) and by the working piston (113) is filled with an expansion material, in particular with an expansion wax, and wherein, for the movement conversion of the temperature-dependent linear movement of the piston rod (114) into a pivoting movement of the valve part (106), a helical geometry (119) is formed on the valve part (106) coaxially to the central axis (34), into which the coupling piece (111) of the piston rod (114) engages.

4. Valve cartridge (40; 104) according to claim 1, 2 or 3, characterized in that a return means, preferably a return spring, in particular a coil spring, for providing a return force or a return torque which is opposed to the adjusting force provided by the deformation element (107) or the torque provided by the deformation element (44) is arranged between the valve member (43; 106) and the cage portion (41, 42, 45; 115, 116).

5. The valve slide (40; 104) according to claim 1, 2, 3 or 4, characterized in that the valve element (43; 106) is arranged in the cage part (41, 42, 45; 115, 116) between a first control disk (67; 117) arranged coaxially with the center axis (34) and a second control disk (77; 118) arranged coaxially with the center axis (34), wherein the second control disk (77; 118) is penetrated by a second control groove (78), and wherein the valve element (43; 106) comprises a second control section (88) arranged adjacent to the second control disk (77; 118) and extending transversely to the center axis (34), which second control section is designed to release or block the second control groove (78) depending on the rotational position of the valve element (43; 106).

6. The valve cartridge (40; 104) as claimed in claim 5, characterized in that the first control recess (68) has an angular offset relative to the second control recess (78) with reference to the center axis (34) and/or the first control section (87) has an angular offset relative to the second control section (88) with reference to the center axis.

7. The valve cartridge (40; 104) as claimed in claim 5 or 6, characterized in that the first control section (87) and the second control section (88) are each configured in the form of a disk, and each of the control sections (87, 88) has at least one control opening (89, 90), which is oriented in particular parallel to the center axis.

8. The valve cartridge (40; 104) as claimed in claim 5, 6 or 7, characterized in that the first control recess (68) and the second control recess (78) are each configured as a recess oriented parallel to the center axis (34).

9. Valve cartridge (40; 104) according to claim 5, 6, 7 or 8, characterized in that the cage section (41, 42, 45; 115, 116) is formed by a first cage section (41; 115) comprising the first control disk (67; 117) and a receiving section (45; 108) for the first end region (58; 112) of the deformation element (44; 107) and a second cage section (42; 116) comprising the second control disk (77; 118) and coupled with the first cage section (41; 115).

10. Fluid control valve (5; 105) for influencing a fluid flow, having a valve housing (30) in which a valve slide (40; 104) according to one of the preceding claims is accommodated, wherein the valve housing (30) has a first input end connection (21) which is connected in fluid communication with a first valve chamber (27) which is delimited by a first inner wall section (25) of the valve housing (30) and by a side of a first control disk (67) facing away from the valve element (43; 106), wherein the valve housing (30) has a second output end connection (24) which is connected in fluid communication with a second valve chamber (28) which is delimited by a second inner wall section (26) of the valve housing (30) and by a side of the first control disk (67) facing the valve element (43; 106).

11. The fluid control valve (5; 105) of claim 10 wherein said valve housing (30) has a first output end fitting (23) connected in fluid communication with the first valve chamber (27).

12. The fluid control valve (5; 105) as claimed in claim 11, characterized in that a second inlet connection (22) is formed on the valve housing (30), which is connected in fluid communication with a third valve chamber (62) which is delimited by a third inner wall section (61) of the valve housing (30) and by a side of the second control disk (77; 118) of the cage part (41, 42, 45; 115, 116) facing away from the valve element (43; 106).