EP3791053A1

EP3791053A1 - Control valve for a heat management module

Info

Publication number: EP3791053A1
Application number: EP19727584.5A
Authority: EP
Inventors: Sebastian Hurst
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2018-05-08
Filing date: 2019-05-07
Publication date: 2021-03-17
Also published as: DE102018110983B3; US20210115838A1; CN111788374A; CN111788374B; WO2019214776A1; US11306646B2

Abstract

The invention relates to a control valve (1) for a heat management module (2) of a motor vehicle (3), comprising at least the following components: - a valve disk (4) for sealingly resting on a valve seat (5) in a closed position; - a valve shaft (6) having an axial extension, the valve shaft (6) being connected to the valve disk (4); - a shaft bearing (7) having a bearing surface (8), in which the valve shaft (6) is mounted such that it can move axially from the bearing surface (8). The control valve (1) is primarily characterized in that a radial spring (9) is also provided, wherein the radial spring (9) is preloaded radially towards the shaft bearing (7) and rests radially on the shaft bearing (7), wherein the receiving groove (10) has an inhibiting section (11) and a free-running section (12) which are separated axially adjacent to one another by means of a clamping wedge (13), wherein the clamping wedge (13) cannot be overcome by the radial spring (9) in the region of the bearing surface (8) and the radial spring (9) can be pressed radially by the clamping wedge (13) in such a way that the valve shaft (6) is inhibited in the axial direction (15) away from the free-running section (12). With the control valve proposed here, a control position can be kept with simple means continuously, preferably without energy, in a small installation space.

Description

Control valve for a thermal management module

The invention relates to a control valve for a thermal management module of a motor vehicle, comprising the following components:

- A valve disc for sealing seating on a valve seat in a closed Stel development;

- A valve stem having an axial extent, wherein the valve stem is connected to the valve disc;

- And a shaft bearing with a bearing surface in which the valve stem guided by the La gerfläche is mounted axially movable.

Furthermore, the invention relates to a thermal management module with such a control valve for a motor vehicle.

Various rotary valve devices are known from the prior art, which is for a thermal management module (WMM), as a thermal management module (TMM) be, for example, a cooling control loop for an internal combustion engine of a motor vehicle, are set up. For example, from DE 10 2013 209 582 A1 a rotary slide ball for a thermal management module is known. The thermal management module described therein is set up in particular for space-optimized components of a coolant circuit of an internal combustion engine. Such a rotary valve is driven elekt romotorisch and can be converted into different positions, such as a blocking division or an open position, but also intermediate positions.

Further state of the art:

- EP 2 102 534 B1: Two-stage fluid connector for pressure fluid container

- DE 10 2006 058 507 A1: angle valve

- DE 38 12 233 A1: water valve

- DE 75 15 533 U: valve

- US 3 120 968 A: Quick coupling with ring detent

- DE 60 204 004 250 T2: Thermostat valve for a coolant circuit

- DE 199 05 466 A1: A method for controlling the temperature of the coolant of internal combustion engines and a thermostatic valve used for this purpose

- DE 10 2014 004 668 A1: Valve

For many applications, it is necessary to search for cost-effective solutions and find ei ne construction with the least possible space requirement. On this basis, the present invention has the object, at least partially overcome the known from the prior art disadvantages. The fiction, contemporary features emerge from the independent claims, to which advantageous embodiments are shown in the dependent claims. The features of the claims can be combined in any technically meaningful manner, and for this purpose, the explanations from the following description and features of the figures can be consulted, which include additional embodiments of the invention.

The control valve is characterized by a radial spring received in a receiving groove of the valve stem and biased radially toward the stem bearing and radially abutting the stem bearing having a first reverse groove and a second reverse groove, the receiving groove having an inhibiting portion and a freewheeling portion which are axially adjacent separated by means of a clamping wedge with an inhibiting ramp which, starting at the inhibiting section, inclines radially towards the bearing surface towards the freewheel section, wherein the clamping wedge of the radial spring in the region of the bearing surface is insurmountable and the radial spring of the clamping wedge so radially is compressible, that the valve stem is inhibited in the axial direction away from the freewheeling portion, and wherein the clamping wedge of the radial spring in the region of the Umkehrnuten is overcome.

However, movement of the valve stem in the axial direction towards the freewheel section is free.

It will hereinafter genom men on the said axial extent of the valve stem reference, if without explicitly other reference the axial direction, radial direction or the direction of travel and corresponding terms are used.

In contrast to previously known control valves indiscreet, so any axial Stellun conditions energy-resistant, so that a continuous control of the means of the control valve under breakable volume flow is possible. At the same time, the structure and the control of the control valve are very simple and constructed with little space demanding.

The control valve proposed here is suitable for a heat management module of a motor vehicle and a volume flow of a coolant by means of this control valve adjustable. The control valve has for this purpose a valve plate, which assumes the switchable sealing function and is seated in a closed position on a valve seat and in an open position is lifted from the valve seat. In the closed position, the control valve for the cooling liquid is no longer or only negligibly low flow-through.

For actuating the valve disk, so for lifting the valve disk from the valve seat and / or pressing the valve disk onto the valve seat, a valve stem is provided, wel cher is firmly connected to the valve disk. The valve stem has an axial extent. This axial extent defines the axis of movement of the valve disk. For this purpose, the valve stem is received in a shaft bearing, which has a corresponding bearing surface. The valve stem is guided by this bearing surface and slides on it indirectly or un indirectly. It should be noted that the valve stem is not necessarily a one-piece component, but is composed according to an embodiment of a plurality of Teilelemen th, for example, a separately manufactured and with one, beispielswei se integrally formed with the valve disc, shaft member firmly connected barrel sleeve has.

Here it is now provided that the control valve has a radial spring. This radial spring is adapted to exert a radial force on the bearing surface and, as a result, an axial frictional force on the bearing surface and an axial force on the valve stem. In one embodiment, the radial spring is a spring introduced with radial snap ring, which is preferably directly clamped in certain operating situations between the valve stem and the tread, be preferred.

The radial spring is received in a receiving groove having a first end wall and a second end wall such that the radial spring is moved with the axial movement of the Ven tiltellers. The receiving groove, for example, circumferentially or interrupted circumferentially formed, for example by means of a plurality of holes or depressions.

The receiving groove has a first axial portion and a second axial portion. These sections are separated from each other by means of a clamping wedge. The clamping wedge has an inhibiting ramp. In an embodiment with the valve stem in the center of the bearing surface, the inhibiting ramp slopes radially outward from the inhibiting portion to the freewheeling portion. The clamping wedge has a radial extent, which can not be overcome by the radial spring in the region of the bearing surface. In addition, the dial spring is seated radially on the arresting ramp of the clamping wedge with the running surface in such a way that the valve stem is then no further away in the axial direction away from the freewheel bearing. cut is movable.

For this purpose, the clamping wedge can be set up in two different configurations. In a first configuration, the valve disk is connected to a drive such that the valve disk can be actively lifted from its valve seat. An antagonist, for example, a biased Axialfe, leads the valve plate back in the direction of the closed position and presses the Ventililtel ler in an end position passively against its valve seat. The closed position is then the normal position. But if the radial spring arranged axially overlapping with the clamping wedge, the valve stem is held due to the frictional engagement, ie inhibited ge in its closing movement. In a second configuration, conversely, the valve disk is connected to a drive in such a way that the valve disk can only be actively pressed onto its valve seat. An antagonist, such as a preloaded axial spring, guides the valve head away from the valve seat. The open position is then the normal position. But if the radial spring arranged axially overlapping with the clamping wedge, the valve stem is held due to the frictional engagement, so inhibited in its opening movement. The terms active and passive refer to the control of the control valve, wherein the drive is preferably an electric drive and voltage for active actuation of the control valve power or power clamping voltage needed, while for a passive operation no power or no power voltage is necessary, for example due to Utilization of mechanically stored energy of an axial spring.

Both in the inhibiting section (ie before the beginning of the ramp inclination) and in freewheeling section, the radial spring is not stretched so strongly against the tread that thereby the axial movement is inhibited. Rather, the valve disk is then freely movable. For Überwin the clamping wedge, so in order to be moved by the inhibiting portion in the freewheeling section or vice versa, and thus axially relative to the valve stem, a radial extension is easily seen at both ends of the tread or the predetermined travel, so that there each Radial spring radially even further can expand. In such a state, the clamping wedge of the radial spring can be overcome and thus an axial re relative movement relative to the valve stem possible. This is a Wech sel allows the sections for the radial spring. For example, the tread is formed by a sleeve, wel che forms the bearing surface over their, preferably entire, axial extent.

According to one embodiment, to facilitate the return of the radial spring in the radially narrower region of the tread, so the travel, the radial spring tread, preferably axially on both sides, for example, a radially inwardly inclined rounding and / or skew. It should be noted that the valve stem is arranged in relation to the (sealable) flow opening formed by the valve seat in an embodiment on the back of the valve disk, so that the valve disk for closing the flow opening of the valve stem is pressed against the valve seat (hereinafter: boost valve). In another embodiment, the valve stem is disposed on the side of the flow opening so that the valve stem protrudes through the flow opening. To close the flow opening, the valve disk is then pulled by the valve stem against the valve seat (hereinafter: pull valve). This affects the orientation of the clamping wedge and the desired (first or second) configuration accordingly.

According to an advantageous embodiment of the control valve, the Umkehrnuten are arranged at the ends of the travel and recessed to the ends thereof so that the clamping wedge of the radial spring axially overcome and thus due to movement of the Ven tilschafts relative to the radial spring of the Hemmabschnitt in the freewheel section or to swept reversed, the Umkehrnuten towards the travel return ramps ge tends towards the bearing surface of the shaft bearing have.

In this embodiment, the shaft bearing at both ends of the bearing surface on a ers te reverse groove or a second reverse groove. It should be noted that ordinal numbers used in the preceding and following description, unless explicitly pointed out to the contrary, serve only the unique distinctiveness or clear assignment to another component with the same ordinal number and do not represent any order or order of the designated components. In particular, an ordinal number greater than one does not require that more must be present from the named components. For example, in one embodiment, only a second reverse groove but no first reverse groove vorgese hen.

The Umkehrnuten have at the relevant end of the travel on a flank, wel surface of the radial spring is not overcome. Likewise, the receiving groove on the clamping wedge axially facing away from each side an end wall. As a result, an axial movement of the valve stem is limited in the interplay of the respective end wall with the respective edge. This has the advantage that at least one, preferably on both sides, a mechanical stop and thus a defined end of the axial movement is created, which prevent exceeding the predetermined axial travel, and preferably also be used as reference points for a position measurement. The reverse groove is recessed in such a way that the radial spring can be radially spaced from the receiving groove so far that then the clamping wedge for the radial spring is axially overcome. Thus, in such a position of the radial spring in the reverse groove due to movement of the valve stem relative to the radial spring, the radial spring from the Hemmabschnitt in the free running section or vice versa transferred.

The reverse groove preferably has a return ramp towards the travel path. This is inclined towards the bearing surface of the shaft bearing. This facilitates the return of the radial spring in the region of the running surface of the shaft bearing. For this purpose, neither a rounding nor a skew on the radial spring is necessary.

In the case of two reversing grooves, these are for example mirrored to one another to form an imaginary transverse plane, with the movement axis forming a normal to this transverse plane. In the (for example, first) reverse groove, which is arranged on the side to wel cher, the forward movement is inhibited by means of the clamping wedge, a transfer of the freewheeling portion in the Hemmabschnitt is possible. In the (then, for example, second) To sweeping, which is arranged on the side to which the forward movement by means of

Clamping wedge is not inhibited, a transfer of the inhibitor section in the freewheel section is possible.

According to an advantageous embodiment of the control valve, a return spring is vorgese hen, which acts with a return force in the axial direction away from the freewheeling portion on the valve stem, so that the axial return force presses the radial spring by means of the clamping wedge with the bearing surface of the shaft bearing.

In this embodiment, a return spring is provided as a mechanical memory and a drive for the control valve only for a movement in the opposite direction to the return set up. For example, the drive is a magnet, which works with the valve shaft in the manner of a solenoid valve. Here, the return spring is so rich tet that it promotes the valve plate towards the valve seat when the control valve is a pusher valve, and away from the valve seat promotes when the control valve is a pull valve (see description of the embodiments of the control valve above) ,

Thus, in this embodiment, for opening the control valve designed as a pusher valve and for closing the control valve designed as a pull valve each active actuation by means of the drive is necessary. On the other hand, in the axial countermovement, the current axial position held passive by means of the return spring. If the drive is activated or overcomes the drive force, the return force of the return spring, the clamping of the clamping wedge is released and transferred the control valve in a new position. This movement is carried out until the drive is switched off again or the return force again overcomes the drive force.

In another embodiment, the drive for actively holding the pusher valve in egg ner axial position of the control valve is arranged in cooperation with the clamping wedge. If the drive is switched off or overcomes the return spring, the driving force, the clamping of the clamping wedge is released and the control valve leads to a new position. This movement is carried out until the drive is reactivated or the driving force again overcomes the return force.

The return spring is preferably designed as a helical compression spring and arranged biased between an on impact of the control valve and a stop of a housing.

In an embodiment in which the return spring loads the control valve in the closing direction, the return spring is biased such that a closing force sufficient to hold the control valve closed under the predetermined pressure conditions is transferred to the valve disk.

According to an advantageous embodiment of the control valve, an axially sealed log device is provided, which is arranged axially between the bearing surface of the shaft bearing and the valve disk, preferably between the bearing surface of the shaft bearing and the return spring according to an embodiment according to the above description, such that the Ven tilschaft Protected stock side before a valve disk side penetration of a liquid ge.

The control valve projects in this embodiment of a drying space in which no coolant can penetrate, in a wet room, wherein the valve disk is arranged in the wet room and cooperating with the drive and (at least there) mounted portion of the valve stem is arranged in the drying room. The proportion which dips into the wet space in a maximally submerged position and is arranged in a maximum lifted position in the drying space is preferably stripped off by means of at least one sealing lip of the sealing element, so that the cooling liquid remains in the wet space.

The return spring is in the above-mentioned preferred embodiment in the wet room, So valve plate side, arranged. Particularly preferably, the drive and the clamping wedge, preferably the entire bearing surface is made dry and encapsulated by the wet space.

In another embodiment, the bearing surface and / or the drive is wet out leads. This allows to use only static seals.

According to an advantageous embodiment of the control valve of the shaft bearing, a path sensor is arranged and detected by means of the displacement sensor, the axial position of the valve stem bar.

In this embodiment, by means of a displacement sensor at any time the position of the Ventililtel coupler can be determined. Because the mechanical relationship in a preferred embodiment form is considered to be almost ideal stiff, so that a direct inference to the Volu menstrom is possible, without the need for additional measurement, such as the Strö mungsgeschwindigkeit required. The displacement sensor is preferably a measuring element, which is integrated in the drive and whose data for a precise control of the drive are he settable.

According to a further aspect, the invention relates to a thermal management module for a motor vehicle, preferably for an internal combustion engine, comprising at least the fol lowing components:

at least one coolant circuit,

at least one pressure source, preferably a coolant pump, at least one heat transfer interface for a heat sink, the heat sink preferably being a cooler,

at least one heat absorption interface for a heat source, wherein the heat source is preferably a combustion chamber of an internal combustion engine,

a control valve according to an embodiment according to the above description,

wherein the coolant circuit can be opened and closed by means of the control valve, so that with means of switching the control valve, a volume flow of the coolant is variable.

The proposed here thermal management module is adapted to the heat of a heat source, for example, an internal combustion engine of a motor vehicle, abzufüh ren and using a heat sink to supply a cooling liquid with a suitable temperature and thus heat capacity of the heat source. For this purpose, the thermal management module on a coolant circuit, wherein the coolant circuit is controlled, for example, map-controlled. Furthermore, the thermal management module to a pressure source, preferably be a coolant pump, by means of which the circulation of the coolant, preferably pressure-controlled, so approximately with a constant pressure in the coolant circuit si is chergestellt.

The thermal management module has a heat receiving interface for a heat source, for example a heat exchanger with a plurality of cooling fins or a connection to a heat exchange device, and a heat release interface, for example also a heat exchanger of a plurality of cooling fins or a connection to a heat exchange device, for a heat sink. The heat sink is preferably a wind in interaction with a radiator of a motor vehicle, wherein the radiator, for example, in addition a fan for stationary operation (no wind) includes.

The thermal management module includes a control valve as previously described. The control valve is adapted to continuously control the coolant flow, that is to say the volumetric flow, with no coolant flowing when the control valve is closed, and a maximum volumetric flow when the control valve is open to the maximum. In one embodiment, the control valve is switched in a partial circuit, for example a by-pass, such that the partial circuit is flowed through by the coolant when the control valve is open and is not flown when the control valve is closed.

By the control valve, preferably passive, is durable in any position, a stu fenlose control or regulation of the volume flow is adjustable, without the need for an agile apparatus, such as a spindle drive, is necessary. In addition, the energy requirement of such a control valve is low.

The above-described invention will be explained in detail below before the relevant technical background with reference to the accompanying drawings showing preferred Ausgestal lines. The invention is limited by the purely schematic drawing calculations in any way, it being noted that the drawings are not measured and are not suitable for the definition of proportions. It will be presented in

Fig. 1: a continuously passively durable control valve;

Fig. 2: the continuously variable actuating mechanism with the valve stem at the first end;

Fig. 3: the stepless adjusting mechanism shortly before pushing out of the first reverse groove;

Fig. 4: the stepless adjusting mechanism with the radial spring in the area of the bearing surface in

inhibiting portion;

Fig. 5: the stepless adjusting mechanism in clamped position; Fig. 6: the stepless adjusting mechanism again dissolved with the radial spring in the region of the bearing surface in the Hemmabschnitt;

Fig. 7: the continuously variable actuating mechanism with the valve stem at the second end;

Fig. 8: The stepless adjusting mechanism with the radial spring in overcoming the

Clamping wedge;

Fig. 9: the stepless adjusting mechanism with the radial spring in the area of the bearing surface in

Freewheeling section; and

10 shows a thermal management module in a motor vehicle.

In Fig. 1, a control valve 1 is shown in a schematic diagram, which is performed as a pusher valve. That is, the valve disk 4 of the control valve 1 must be pressed to close the Strö tion opening 41 of the (rear) valve stem 6 ge to the associated valve seat 5. In the embodiment shown, a return spring 20 is provided, wel che by means of their mechanically stored return force 33 the valve head 4 along the loading movement axis 34, ie in the axial direction 15, presses against the valve seat 5, when the axial force 43 of the drive 36 (and optionally the flow forces in the coolant channel 40) is overcome. For this purpose, the return spring 20 here between a stop 37 of the control valve 1 and a housing stop 39 of the housing 38 (or here a rigid connected to the housing 38 and by means of a static seal 35 sealed from the outside valve closure in the housing 38) braced. Here, the return spring 20 in a wet room, ie in a non-sealed by means of sealing means with respect to the Kühlmittelka 40 space arranged. In the axial direction 15 to the shaft bearing 7 of the return spring is a sealant 21, here a dynamic axial seal, downstream, which an ingress of (cooling) liquid from the wet room in the storage space undercut. The axial position of the valve stem 6 and thus of the valve disk 4 is here detected by means of a displacement sensor 22, which is integrated in the drive.

The valve stem 6, which summarizes here a set up for the bearing contact separate sleeve, is guided in the shaft bearing 7 by means of the bearing surface 8. The bearing surface 8 comprises at the first end 18 of the travel path of the control valve 1, a first return groove 16 and the second end 19 of this travel a second return groove 17 between the first end 18 and the second end 19 is a radial spring 9 movable here, for example, as a snap ring is executed. The radial spring 9 is received in a receiving groove 10 of the valve stem 6 and is thus moved axially with the valve stem 6, wherein a certain Rela tivbewegung between the radial spring 9 and the valve stem 6 is possible. This and the construction of the receiving groove 10 will be explained in the following figures 2 to 9. In FIG. 2 to FIG. 9, the continuously variable actuating mechanism, as can be used for example in the control valve 1 according to FIG. 1, is shown in a schematic diagram, the axial direction 15 being shown horizontally in the illustration. In the illustration above, the shaft bearing 7 is shown with the bearing surface 8 and below the valve stem 6. The receiving groove 10 to summarizes a Hemmabschnitt 11 adjacent to a first end wall 44 (here left, also referred to as groove cheek) and axially adjacent to a freewheeling section 12th adjacent to a second end wall 45 (here on the right), which are separated from each other by a clamping wedge 13. The inhibiting ramp 14 rises from the Hemmabschnitt 11 towards the Freilaufab section 12 radially outward (up here) gently and falls to the freewheel section 12 steeply. In this case, the clamping wedge 13 is set up such that the radial spring 9 can not overcome the clamping wedge 13 when the radial spring 9 rests against the bearing surface 8. The radial spring 9 is, due to their radially outwardly acting spring force against the bearing surface 8 gezwun gene and thus can only overcome the clamping wedge 13 when the radial spring 9 of their radially outwardly acting spring force following in one of the Umkehrnuten 16 or 17 can dodge radially. The radial spring 9 is thus taken from the end walls 44 and 45 of the receiving groove 10 or the free-running side steep edge of the clamping wedge 13 axially. If the radial spring 9 but not at an end wall 44 and 45 of the Aufnah menut 10 or on the said steep flank of the clamping wedge 13, it is due to the resulting from the radially outwardly acting spring force of the radial spring 9 friction with the bearing surface 8 or the plant on a flank 46 and 47 (see FIG. 3) one of the reversing grooves 16 or 17, a relative movement between the radial spring 9 and the valve stem 6 instead. Is a relative movement between the radial spring 9 (upright) and the valve stem 6 (moved) in the illustration to the left executed while the radial spring 9 somewhere in the range of travel between the Umkehrnuten 16 and 17 on the bearing surface 8 and in the receiving groove 10 in Hemmabschnitt 1 1 is located, the radial spring of the inhibiting ramp 14 of the clamping wedge 13 is pressed radially against the bearing surface 8, that the applied (here to the left) axial force resulting therefrom gengeichtete axial friction force of the radial spring 9 in the interaction of clamping wedge 13 and Storage area 8 can not overcome. The functional sections 1 1, 12 and 14 of the recording groove 10 are only in Fig. 2, but in Figs. 3 to 9 of course identical table and have been omitted for clarity. Alone for orientation, each of the functional sections 1 1 and 12 separating clamping wedge 13 is marked. Likewise, only in Fig. 3, the first reverse groove 16 and the second reverse groove 17 are more accurately gekennzeich net, in the other figures 2 and 4 to 9 of course identical and the labeling has been omitted for clarity. The first return groove 16 has the first end 18 of the travel of the valve stem 6, so in the illustration on the left, a steep (first) edge 46, which is not overcome by the radial spring 9, if this due to their Bias is introduced radially outward into the first return groove 16. Gegenüberlie ing, ie in the illustration on the right, a (first) return ramp 48 is provided, which of the first end wall 44 of the receiving groove 10 entrained radial spring 9 ent against their bias return (to the right) in the radially narrower region of La gerfläche. 8 allows. The second reversal groove 17 is constructed in the same way and function, here mirrored identical. The (second) flank 47, here on the right, limits the axial movement of the radial spring 9 and thus (in interaction with the first end wall 44 of the receptacle 10) the axial movement of the valve stem 6 (see FIG. 7). The (second) return ramp 49, here on the left, allows the second end wall 45 of the receiving groove 10 entrained radial spring 9 against its bias return (to the left) in the radially narrower region of the bearing surface 8 (see change from the state shown in FIG to the state of FIG. 9).

In the following, this stepless actuating mechanism is explained on the insert example as shown in FIG. 1 and reference is made to FIG. 1 without further reference, wherein in the illustration of FIGS. 2 to 9, to the left, to the valve disk 4 and to the right, to the drive 36, wherein, therefore, a movement to the left is a movement toward the closed position of the Ventililtel coupler 4 and a movement to the right is a movement to open the control valve 1. In principle, however, a rotated relative assignment of the orientation of the inhibiting ramp 14 of the clamping wedge 13 to the return spring 20 and the drive 36 is possible and / or an opposite direction 15 for closing the control valve 1, as well as another type of antagonistic drive means for moving the valve stem 6.

In Fig. 2, a position is shown in which (according to FIG. 1) the valve disk 4 in the biased by the return spring 20 contact with the valve seat 5 is normal (default) and closed without active drive. The valve stem 6 is thus located at the first end 18 of the Ver driving path, which here on the first (left, hemmabschnittseitigen) end wall 44 on the receiving groove 10 is characterized. The radial spring 9 is seated in the first reverse groove 16 and be found in contact with the second (right, free-running side) end wall 45 of the receiving groove 10, wherein the second end wall 45 thus by means of the radial spring 9 and the first edge 46 of the first reverse groove 16 the end stop for forms the travel of the control valve 1. Be preferred but this (left) end stop is only a safety stop and the movement away is limited in this direction to ensure a sufficient force reservoir for closing Shen control valve 1 and to avoid a double fit only of the valve plate 4 and the valve seat 5.

In Fig. 3, starting from the position shown in Fig. 2 by means of the drive 36 of the Valve stem 6 is moved in the open direction, ie to the right. The valve plate 4 stands out from his contact with the valve seat 5 against the bias of the return spring 20. The Radialfe of 9 is in contact with the first (left, hemmabschnittseitigen) end wall 44 on the receiving groove 10th

In Fig. 4, the further course of the movement of the valve stem 6 (to the right) is shown to the second reverse groove 17 due to the axial force 43 of the drive 36 from the position shown in Fig. 3. The radial spring 9 was pushed out of the first (left, hemmabschnittseitigen) end wall 44 of the receiving groove 10 via the (first) return ramp 48 from the first order to 16 and compressed radially inward (ie down here). The Ven tilschaft 6 is now infinitely actuated along the axial direction 15, whereby the control valve 1 is opened more and more.

In Fig. 5, a position is shown, which occurs when the displacement sensor 22 and the control electronics has detected the achievement of a desired position of the valve stem 6. Then, the active operation is stopped by means of the drive 36. Then, the return spring 20, the valve stem 6 again a little direction closed (to the left) press it, until after a short distance the clamping wedge 13 in contact with the radial spring 9 and in the wake of the return force 33 of the return spring 20, the three components valve stem 6, radial spring 9 and bearing surface 8 are clamped to each other. This results in an axially acting clamping force 42, so that is from the return force 33, the set position is held without energy th. This works at any point of the bearing surface 8 and the energy-free maintained position is thus infinitely adjustable. The short distance necessary for clamping is precisely predictable and thus easily taken into account in the control electronics for precise control of the held position of the valve disk 4.

In Fig. 6 it is now shown how the energy-free position shown in Fig. 5 is left again, namely by the drive 36 again an axial force 43 is applied, which overcomes the return force 33 of the return spring 20. The tension of the Rückholfe 9 between clamping wedge 13 and bearing surface 8 is now canceled due to the relative movement between rule radial spring 9 and valve stem 6 and receiving groove 10. The valve stem 6 continues to move open (to the right). On the way to the second order to sweeping groove 17, as shown in Fig. 5 and related explanation again every position lying on the way energetically clamped.

FIGS. 7 to 9 show how a new position can be approached which lies closed from the current position. For this purpose, the second conversion be swept 17. There, the radial spring 9 slips radially outward into the order to sweeping 17 and expands radially accordingly (Fig. 7). Here, the second end 19 of the travel path (in analogy to FIG. 2, relative to the first end wall 44 of the receiving groove 10) is characterized, in which case the control valve 1 is open to the maximum; because the first Endwan extension 44, the radial spring 9 and the (second) edge 47 of the second reversal groove 17 together form a second (right) end stop.

In Fig. 8 it is shown how due to the occurring increase in the inner diameter of the radial spring 9 (when removing axial force 43 of the active movement by means of the drive 36) of the clamping wedge 13 of the radial spring 9 (axially moved by the return force 33 of the Rückholfe of 20) overcome and thus in the freewheel section 12 (see FIG. 2) is transferred.

In Fig. 9 is now shown how the second end wall 45 of the receiving groove 10 of the valve stem 6 now transported the radial spring 9 toward the first reverse groove 16, and passively by means of the return force 33. A bracing in a desired position can in this Operation does not take place, but the process must again be started again from the bottom order to sweeping, compare Fig. 2.

In Fig. 10 a detail of a motor vehicle 3 is shown, in which in the engine compartment, al so where the internal combustion engine 23 is arranged, a thermal management module 2, comprising a coolant circuit 24 for the internal combustion engine 23, is shown. The coolant circuit 24 connects a heat receiving interface 30, here in the internal combustion engine 23, the combustion chambers 32 thus represent the heat source 31, and a heat release interface 27, which uses, for example by (wind) wind, which represents the heat sink 28, by means of a radiator 29 for heat dissipation , The Kühlmit tel in the coolant circuit 24 is funded by the pressure source 25, for example, a coolant pump 26. The coolant circuit 24 has here a control valve 1, which is executed in example as shown in Fig. 1. By means of the control valve 1, the volume flow of the coolant circuit 24 can be controlled. In this case, the pressure source 25 is preferably regulated in a pressure-constant manner, so that when the control valve 1 is opened, the volume flow increases.

With the control valve proposed here can be with simple means on low construction space a control position continuously, preferably energy-free, hold. LIST OF REFERENCE NUMBERS

1 control valve

2 thermal management module

3 motor vehicle

4 valve plates

5 valve seat

6 valve stem

7 shaft bearings

8 storage area

9 radial spring

10 receiving groove

11 inhibiting section

12 freewheel section

13 clamping wedge

14 inhibition ramp

15 axial direction

16 first reverse groove

17 second reverse groove

18 first end

19 second end

20 return spring

21 sealing element

22 displacement sensor

23 internal combustion engine

24 coolant circuit

25 pressure source

26 coolant pump

27 heat release interface

28 heat sink

29 coolers

30 heat absorption interface

31 heat source

32 combustion chamber

33 return force

34 movement axis 35 static seal

36 drive

37 valve stop

38 housing

39 housing stop

40 coolant channel

41 flow opening

42 clamping force flow

43 axial force

44 first end wall

45 second end wall

46 first flank

47 second flank

48 first return ramp 49 second return ramp

Claims

claims

1. control valve (1) for a thermal management module (2) of a motor vehicle (3) aufwei send the following components:

- A valve disc (4) for sealing seating on a valve seat (5) in a closed position Ge,

a valve stem (6) having an axial extent, the valve stem (6) being connected to the valve plate (4),

- And a shaft bearing (7) with a bearing surface (8), in which the valve stem (6) guided by the bearing surface (8) is mounted axially movable,

characterized by a radial spring (9) which is received in a receiving groove (10) of the valve stem (6) and radially biased towards the shaft bearing (7) and which rests radially on the shaft bearing (7) having a first return groove (16 ) and a second order to sweeping groove (17), wherein the receiving groove (10) has an inhibiting portion (11) and a freewheeling portion (12), which are axially adjacent by means of a clamping wedge (13) with a Hemmrampe (14) are separated at Starting from the restraining section (11), towards the freewheel section (12), it inclines radially towards the bearing surface (8), wherein the clamping wedge (13) of the radial spring (9) in the region of the bearing surface (8) is insurmountable and the radial spring (9 ) of the clamping wedge (13) is radially compressible such that the valve stem (6) in the axial direction (15) away from the freewheeling portion (12) is inhibited, and wherein the clamping wedge (13) of the radial spring (9) in the region Reverse grooves (16, 17) can be overcome.

Second control valve (1) according to claim 1, characterized in that the Umkehrnuten (16, 17) at the ends (18, 19) of a predetermined travel path and to the ends (18, 19) are recessed out such that the clamping wedge (13) of the radial spring (9) axially überwindbar and thus due to a movement of the valve stem (6) relative to the radial spring (9) of the Hemmabschnitt (11) in the freewheeling section (12) or vice versa is reversible, wherein the Umkehrnuten ( 16, 17) towards the travel return ramps (48, 49) inclined towards the bearing surface (8) of the shaft bearing (7).

3. Control valve (1) according to claim 1 or 2, characterized by a return spring (20) which with a return force (33) in the axial direction (15) away from the freewheeling section (12) acts on the valve stem (6), so that the axial return force (33) presses the radial spring (9) by means of the clamping wedge (13) with the bearing surface (8) of the shaft bearing (7).

4. Control valve (1) according to one of the preceding claims, characterized by an axially sealing sealing element (21) which is arranged axially between the bearing surface (8) of the shaft bearing (7) and the valve disc (4) such that the valve stem (6 ) is protected on the storage side before a valve disc side penetration of a liquid.

5. Control valve (1) according to one of the preceding claims, characterized by egg NEN rear side of the shaft bearing (7) arranged displacement sensor (22) for detecting the axial position of the valve stem (6).

6. Thermal management module (2) for a motor vehicle (3), comprising the following components:

a coolant circuit (24),

a pressure source (25),

a heat dissipation interface (27) for a heat sink (28),

a heat receiving interface (30) for a heat source (31),

and a control valve (1) according to one of the preceding claims,

wherein the coolant circuit (24) by means of the control valve (1) can be opened and blocked, so that by means of switching the control valve (1) a volume flow of the coolant is changed derbar.