COOLING CIRCUIT ARRANGEMENT AND METHOD FOR COOLING AN ENGINE

Abstract

A cooling circuit arrangement (1) for cooling an engine (2), in particular a motor vehicle combustion engine, by means of a cooling medium, which can be conveyed by a cooling medium pump (4) between a suction side (S) and a pressure side (P) in a cooling medium circuit (3), which comprises a cooler fluid path (7) passing through a cooler (6) and a bypass fluid path (5), wherein a cooling medium valve (8) having an actuator (9) is arranged in the cooling medium circuit (3) for setting a volume flow ratio between cooling medium flows flowing through the cooler fluid path (7) and bypass fluid path (5), wherein the actuator (9) has a hydraulically activatable adjustment element (17), which can be supplied with a cooling medium via at least one control valve (11) allocated to the cooling medium valve (8), in particular from the pressure side (P) out of the cooling medium circuit (3), in order to set the volume flow ratio, and wherein the adjustment element (17) borders a control chamber (19) that can be supplied with cooling medium via the at least one control valve (11), and a valve chamber (20) also supplied with cooling medium, wherein the adjustment element (17) can be displaced in both mutually opposed displacement directions exclusively through exposure to hydraulic pressure by means of the cooling medium, and wherein, in order to displace the adjustment element (11), both the control chamber (19) and valve chamber (20) can be joined with the cooling circuit (3) by means of the at least one control valve (11), or the free flow cross section of corresponding connections can be varied, and that wherein, in order to maintain an adjustment position, the at least one control valve (11) can be used to join both the control chamber (19) and valve chamber (20) with the same cooling circuit side, or the free flow cross section of corresponding connections can be varied, wherein, the at least one control valve (11) has a 4/3-way valve functionality and a pressure-side cooling medium pressure port (P), a cooling medium outflow port (T), a first working port (B) leading to the control chamber (19) and a second working port (A) leading to the valve chamber (20).

Claims

1. A cooling circuit arrangement (1) for cooling an engine (2), in particular a motor vehicle combustion engine, by means of a cooling medium, which can be conveyed by a cooling medium pump (4) between a suction side (S) and a pressure side (P) in a cooling medium circuit (3), which comprises a cooler fluid path (7) passing through a cooler (6) and a bypass fluid path (5), wherein a cooling medium valve (8) having an actuator (9) is arranged in the cooling medium circuit (3) for setting a volume flow ratio between cooling medium flows flowing through the cooler fluid path (7) and bypass fluid path (5), characterized in that the actuator (9) has a hydraulically activatable adjustment element (17), which can be supplied with cooling medium via at least one control valve (11) allocated to the cooling medium valve (8), in particular from the pressure side (P) out of the cooling medium circuit (3), in order to set the volume flow ratio.

2. The cooling circuit arrangement according to claim 1, characterized in that, by displacing the adjustment element (17), in particular by means of an annular slide (24) coupled with the adjustment element (17), a free flow cross section of a connection of an outlet (15) of the cooler fluid path (7) to the cooling medium pump (4) and/or a free flow cross section of an outlet (15) of the bypass fluid path (5) to the cooling medium pump (4) can be varied, or that, by displacing the adjustment element (17), in particular by means of the annular slide (24) coupled with the adjustment element (17), a free flow cross section of a connection of an inlet (14) of the cooler fluid path (7) to the cooling medium pump (4) and/or a free flow cross section of an inlet (14) of the bypass fluid path (5) to can be varied.

3. The cooling circuit arrangement according to one of claim 1 or 2, characterized in that the adjustment element (17) borders a control chamber (19) that can be supplied with the in particular pressure-side cooling medium via the at least one control valve (11), and preferably a valve chamber (20) also supplied with a cooling medium, in particular a suction-side cooling medium.

4. The cooling circuit arrangement according to claim 3, characterized in that, in order to displace the adjustment element (11), exclusively the control chamber (19) can be joined with the cooling circuit (3) by means of the at least one control valve (11), or the free flow cross section of such a connection can be varied, or, in order to displace the adjustment element (11), both the control chamber (19) and the valve chamber (20) can be joined with the cooling circuit (3) by means of the at least one control valve (11), or the free flow cross section of corresponding connections can be varied, and/or that, in order to maintain an adjustment element position, the at least one control valve (11) can be used to join both the control chamber (19) and valve chamber (20) with the cooling circuit, in particular on the same cooling circuit side, or the free flow cross section of corresponding connections can be varied.

5. The cooling circuit arrangement according to one of claim 3 or 4, characterized in that, in order to especially translationally displace the adjustment element (17) in a first displacement direction, the control chamber (19) can be joined by means of the at least one control valve (11) with the cooling medium circuit (3), in particular the pressure side (P) of the cooling medium circuit (3), and/or a free flow cross section of this connection can be enlarged, and that, in order to displace the adjustment element (17) in a second displacement direction opposite the first displacement direction, the at least one control valve (11) can be used to open a connection between the control chamber (19) and cooling medium circuit (3), preferably the suction side (S) of the cooling medium circuit (3), in particular inside of the cooling medium valve (8) and/or a free flow cross section of this connection can be enlarged.

6. The cooling circuit arrangement according to one of claim 3 or 4, characterized in that, in order to especially translationally displace the adjustment element (17) in a first displacement direction by means of the at least [one] control valve (11), the control chamber (19) can be joined with the pressure side (P) of the cooling medium circuit (3) and the valve chamber (20) with the suction side (S) of the cooling medium circuit (3), or the free flow cross section of the respective connection can be varied, in particular enlarged, and that, in order to displace the adjustment element in a second displacement direction opposite the first displacement direction, the at least [one] control valve (11) can be used to join the valve chamber (20) with the pressure side (P) of the cooling medium circuit (3) and the control chamber (19) with the suction side (S) of the cooling medium circuit (3), or the free flow cross section of the respective connection can be varied, in particular enlarged, and/or that, in order to maintain an adjustment element position, the at least one control valve (11) can be used to join both the control chamber (19) and valve chamber (20) with the pressure side (P) of the cooling circuit, or alternatively the suction side (S) of the cooling circuit, or the free flow cross section of corresponding connections can be varied.

7. The cooling circuit arrangement according to one of claims 3 to 6, characterized in that the control chamber (19) and valve chamber (20) are arranged in a cylinder (18) that envelops the adjustment element (17), which is preferably piston-shaped and translationally displaceable.

8. The cooling circuit arrangement according to one of claims 3 to 7, characterized in that a leakage fluid path is provided between the control chamber (19) and valve chamber (20), through which a cooling medium leakage fluid path can flow out of the control chamber (19) into the valve chamber (20), in particular outside passing by the adjustment element (17).

9. The cooling circuit arrangement according to one of the preceding claims, characterized in that the at least one control valve (11) is designed and/or actuated as a preferably solenoid, in particular PWM actuated, proportional valve, or as a preferably solenoid, in particularly discretely switching switch valve, and/or that the at least one control valve (11) is designed as a multi-seat switch valve or as a combined slide/multi-seat switch valve, preferably each as a 4/3-way valve, which consists of two valve bodies (33, 34) that can be displaced with a shared actuator, wherein one of the valve bodies is preferably penetrated by an adjusting part that can be displaced by means of the actuator, in particular a piston, in order to displace the other valve body, wherein the adjusting part (39) can preferably be displaced either exclusively relative to one of the valve bodies (33, 34) or alternatively relative to both of the valve bodies (33, 34).

10. The cooling circuit arrangement according to one of the preceding claims, characterized in that the control valve (11) can be and/or is actuated by way of a control unit that preferably consists of a thermal switch and is joined with the control valve (11) in a signal-conducting manner in such a way that the adjustment element (17), preferably exclusively, can assume two stable adjustment positions, which each define a fixed volume flow ratio, preferably a first adjustment position in which the entire cooling medium flows through the cooler fluid path (7) and/or a second adjustment position in which the entire cooling medium or a portion of the cooling medium flows through the bypass fluid path (5), or that the control valve (11) can be and/or is actuated by way of a control unit joined with the control valve (11) in a signal-conducting manner in such a way that the adjustment element can assume a plurality of adjustment positions, in particular more than two, preferably more than three, further preferably more than ten, which each result in volume flow ratios that differ from each other.

11. The cooling circuit arrangement according to one of the preceding claims, characterized in that the control valve (11) is a 3/2-way valve, which preferentially has a preferably pressure-side cooling medium pressure port (PA), a preferably suction-side cooling medium outflow port (T.sub.A), and an adjustment-side cooling medium working port (AA), or that the at least one control valve (11) has a 4/3-way valve functionality and a preferably pressure-side cooling medium pressure port (P), a preferably suction-side cooling medium outflow port (T), a first working port (B) leading to the control chamber (19) and a second working port (A) leading to the valve chamber (20).

12. The cooling circuit arrangement according to one of the preceding claims, characterized in that the at least one control valve (11) can be actuated by way of a control unit, preferably as a function of an engine temperature-dependent temperature signal and/or independently of the engine temperature signal, wherein, in order to determine an ACTUAL volume flow ratio, the control unit is joined with a position sensor (31) in a signal-conducting manner to detect the position of the adjustment element.

13. The cooling circuit arrangement according to one of the preceding claims, characterized in that the adjustment element (19) can be displaced against the spring force of a return spring by supplying it with in particular a pressure-side cooling medium, or that the adjustment element (17) can be displaced in both opposite displacement directions exclusively by being hydraulically pressurized by means of the cooling element.

14. The cooling circuit arrangement according to one of the preceding claims, characterized in that the cooling medium pump (4) is arranged in such a way that the cooling medium flows out of the pump to the engine (2), and that, after the engine (2), the cooling medium circuit (3) branches into the bypass fluid path (5) and cooler fluid path (7).

15. A method for cooling an engine (2), in particular a motor vehicle combustion engine, in particular by means of a cooling circuit arrangement (1) according to one of the preceding claims, wherein cooling medium is conveyed between a suction side (S) and a pressure side (P) in a cooling medium circuit (3), which consists of a cooler fluid path (7) leading through a cooler (6) and a bypass fluid path (5), wherein a volume flow ratio between the cooling medium volume flows flowing through the cooler fluid path (7) and bypass fluid path (5) is set by means of a cooling medium valve (8) that is arranged in the cooling medium circuit (3) and has an actuator (2), characterized in that the actuator (2) has a hydraulically activatable adjustment element (17), which is supplied with cooling medium from the cooling medium circuit (3), in particular from the pressure side (P) of the cooling medium circuit (3), in order to set the volume flow ratio by way of a control valve (11) allocated to the cooling medium valve (8).

16. The method according to claim 15, characterized in that the adjustment element (17) is supplied with the in particular pressure-side cooling medium for displacement in a first displacement direction, and that this supply of cooling medium to the adjustment element (17) for displacing the adjustment element (17) in a second displacement direction opposite the first displacement direction is reduced, in that the cooling medium supplied to the adjustment element (17) is at least partially discharged into the cooling medium circuit (3), preferably toward the suction side (S) of the cooling medium circuit (3), in particular inside of the cooling medium valve (8).

17. The method according to claim 15, characterized in that the adjustment element (17) preferably not exposed to the force of a return spring is displaced in a first displacement direction by using the at least one control valve (11) to guide preferably pressure-side cooling medium out of the cooling medium circuit into the control chamber (19) and having the cooling medium be discharged via the at least one control valve (11) out of the valve chamber (20), in particular toward the suction side (S) and into the cooling medium circuit, and that the adjustment element (17) is displaced in an adjustment direction opposite the first displacement direction by using the at least one control valve (11) to guide preferably pressure-side cooling medium out of the cooling medium circuit into the valve chamber (20), and having cooling medium be discharged via the at least one control valve (11) out of the control chamber (19), in particular toward the suction side (S) and into the cooling medium circuit, and/or that, to maintain an adjustment element position, both the control chamber (19) and valve chamber (20) are joined in a fluid-conducting manner with the cooling circuit, preferably both with the suction side (S) or alternatively with the pressure side (P), by means of the at least one control valve (11).

18. The method according to one of claims 15 to 17, characterized in that the at least one control valve (11) is actuated in such a way that the adjustment element (17) is displaced exclusively between two stable adjustment positions, or that the adjustment element (17) is displaced between more than two stable adjustment positions, in particular a plurality of intermediate positions between two extreme positions, which differ with respect to the volume flow ratio.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0046] Additional advantages, features and details of the invention may be derived from the following description of preferred exemplary embodiments, as well as based on the drawings.

[0047] The latter show:

[0048] FIG. 1: A cooling medium circuit arrangement designed based on the inventive concept, with completely open cooler fluid path (large circuit) and completely closed bypass fluid path (small circuit), wherein the control valve designed as a solenoid valve is in its de-energized state,

[0049] FIG. 2: A cooling medium circuit arrangement according to FIG. 1 with completely open bypass fluid path and completely closed cooler fluid path, as well as maximally supplied control valve,

[0050] FIG. 3: A perspective sectional view of a preferred embodiment of a cooling medium valve that is preferably used in the cooling circuit arrangement according to FIGS. 1 to 3, and has a control valve designed as a 3/2 path proportional solenoid valve, which either accompanies or forms a structural unit with it,

[0051] FIG. 4: A hydraulic equivalent circuit diagram of an alternative embodiment of a cooling circuit arrangement according to the invention, in which the at least one control valve joins the control chamber and valve chamber with the pressure side and suction side of the cooling medium circuit in a simultaneously alternating manner,

[0052] FIGS. 5 to 7: Different valve positions of a multi-seat switch valve with a 4/3-way functionality that is preferably used in a cooling circuit arrangement according to FIG. 4,

[0053] FIG. 8: A diagram [showing] the spring force progressions for the springs used in the control valve depicted on FIGS. 5 to 7,

[0054] FIGS. 9 to 11: Different valve positions of an alternative combined slide-multi-seat switch valve with a 4/3-way functionality that is preferably used for hydraulically displacing a cooling medium valve in a cooling medium circuit, FIG. 12: A diagram [showing] the spring force progressions for the springs used in the control valve depicted on FIGS. 9 to 11.

[0055] Identical elements and elements with the same function are marked with the same reference number on the figures.

DET.SUB.A .ILED DESCRIPTION

[0056] FIG. 1 shows a cooling circuit arrangement 1 designed based on the inventive concept, in particular for integration into a motor vehicle (mv).

[0057] In evidence is an engine 2 to be cooled, here exemplarily designed as a combustion engine, which is integrated into a cooling medium circuit 3 or hooked up thereto in a known manner. This cooling medium circuit 3 consists of a cooling medium pump 4 preferably driven by the engine 2 that conveys cooling medium from a suction side S of the cooling medium circuit 3 to a pressure side P.

[0058] After the engine 2, the cooling circuit 3 branches into a bypass fluid path 5, which in the specific exemplary embodiment completely bypasses a cooler 6 (radiator), and a cooler fluid path 7 that flows through the cooler 6.

[0059] Both the bypass fluid path 5 and cooler fluid path 7 are guided to a cooling medium valve 8, which can be used to set the volume flow ratio of the cooling medium volume flows flowing through the fluid paths 5, 7. In an alternative embodiment (not shown), the cooling medium valve 8 after the engine can be arranged where the cooling medium circuit 3 branches into the bypass fluid path 5 and cooler fluid path 7, and set the inflow in at least one of these paths. It is basically possible to use a cooling medium valve 8 to only set or influence the free flow cross section of one of the fluid paths 5, 7, wherein it makes more sense to vary both flow cross sections, in particular simultaneously or coupled, by actuating the cooling medium valve. Regardless of the specific configuration and arrangement of the cooling medium valve 8, the latter in any event has a hydraulic actuator 9 with a hydraulically activatable adjustment element. The adjustment element can be displaced through exposure to hydraulic pressure by means of a pressure-side cooling medium. To this end, the actuator 9 can be supplied with the aforementioned pressure-side cooling medium via a connecting line 10 by means of a control valve 11 presently designed as a solenoid 3/2-way proportional valve.

[0060] For this purpose, the control valve 11 comprises a pressure port P.sub.A, which is hooked up to the pressure side P of the cooling circuit 3. The control valve 11 further comprises a working port AA, by way of which pressure-side cooling medium is guided to the adjustment element (also as a function of the valve position). The control valve 11 further comprises a outflow port T.sub.A, by way of which cooling medium can be diverted or discharged from the adjustment element or a control chamber allocated thereto and/or the pressure port PA to the suction side S of the cooling circuit 3.

[0061] The control valve 11 is designed in such a way that the connection between the ports P.sub.A and A.sub.A in the depicted non-energized position is completely open. To this end, a valve spring of the control valve 11 correspondingly displaces the valve body of the control valve 11 against a stop.

[0062] As evident, a connection established via the cooling medium valve 8 between an outlet of the cooler fluid path 7 and the cooling medium pump 4 is completely open, while the outlet of the bypass fluid path 5, and hence its suction side, is completely closed, so that the cooling medium pump conveys the entire cooling medium flow through the cooler 6.

[0063] FIG. 2 shows the other extreme case. Correspondingly actuating the control valve 11 here interrupts the pressure-side cooling medium supply to the actuator 9, and the actuator 9, or more precisely the control chamber provided therein and allocated to the adjustment element, is hydraulically connected with the outflow port T.sub.A, so that cooling medium located in the control chamber can be discharged to the suction side S, and the adjustment element is displaced by the valve springs (return springs) of the cooling medium valve 8 into the shown position, in which the cooling medium valve 8 completely closes off the cooler fluid path 7, and instead completely opens the outlet of the bypass fluid path 5 or connects it with the cooling medium pump 4.

[0064] Correspondingly actuating the control valve 11 also makes it possible to set in particular any intermediate positions, so that both the cooler fluid path 7 and the bypass fluid path 5 are partially open toward the cooling medium fluid pump 4.

[0065] FIG. 3 presents a perspective, cut view of a preferred embodiment of a cooling medium 8 according to the invention, in particular for integration into a cooling circuit arrangement 1 shown on FIGS. 1 and 2.

[0066] The cooling medium valve 2 together with the control valve 11 forms a shared assembly, for which purpose the control valve 11 is secured to the cooling medium valve 8 and, for example, here protrudes axially into an outwardly open port opening 12 in a housing 13 of the cooling medium valve 8.

[0067] The housing 13 of the cooling medium valve comprises an inlet 14 for the cooling medium flow from the cooler fluid path 7. A likewise provided inlet for the fluid flow from the bypass fluid path 5 is not depicted. This fluid flow gets into the area marked with the arrow 5. The cooling medium valve 8 comprises a (shared) outlet 15 denoted only by an arrow for cooling medium from the bypass fluid path and cooler fluid path, wherein the volume flow ratio for these volume flows can be set by means of the cooling medium valve. Depending on the switched position of the cooling medium valve 8, the outlet 15 joins the fluid paths with the cooling medium pump 4 (see FIGS. 1 and 2).

[0068] The cooling medium pump 8 comprises a hydraulic actuator 9 with a here translationally displaceable adjustment element 17, which is arranged as a piston in a cylinder 18 formed by the housing 13. The adjustment element 17 separates a control chamber 19 formed in the housing 13 from a valve chamber 20 arranged on the side of the adjustment element 17 facing away from the control chamber, which is connected with the outlet 15 in a directly fluid-conducting manner.

[0069] A return spring 21 exerts a spring force on the adjustment element 17 in a second, lowermost displacement direction in the drawing plane, so that the adjustment element 19 tries to minimize the volume of the control chamber 17.

[0070] The return spring 21 is axially supported directly on the adjustment element 17 at one end, and at the other end on a reciprocal support plate 22, which has a through opening 23 for joining the valve chamber 20 in a fluid-conducting manner with the suction side of the outlet 15 connected with the suction side of the cooling medium circuit.

[0071] An annular slide 24 is secured to the adjustment element 17, so that displacing the adjustment element simultaneously also displaces the annular slide 24, so that, as has yet to be explained below, the volume flow ratio released to the cooling medium pump 4 can be set between the bypass fluid path volume flow and cooler path volume flow.

[0072] The annular slide 24 has a cylindrical shell surface section 25 along with a floor section 26 oriented perpendicular thereto, wherein the latter once again is provided with openings 27, so as to join the valve chamber 20 with the outlet 15 in a directly fluid-conducting manner.

[0073] In order to displace the adjustment element 17 in a first displacement direction, i.e., upwardly in the drawing plane, the control chamber 19 has to be supplied with cooling medium from the pressure side of the cooling medium circuit 3 (see FIGS. 1 and 2). This is realized via the control valve 11 here exemplarily designed as a solenoid 3/2-way valve. To this end, the latter has the pressure port PA denoted by an arrow, by way of which the pressure-side cooling medium can flow in. The inflow takes place from the pressure port PA via the working port A.sub.A of the control element 11 as well as the connecting line 10 designed as a bore or channel in the housing 13. Depending on the valve position, cooling medium from the control chamber 19 can again be discharged via the connecting line 10, specifically by way of the outflow port T.sub.A of the control valve 11 and the connecting channel 29 (diverting line) in a chamber 28 designed as an annular chamber inside of the housing 13. On the other hand, the cooling medium volume flow from the cooler fluid path flowing in by way of the inlet 14 also flows in the chamber 28. By discharging cooling medium from the control chamber 19 into the suction-side chamber 28 that can be joined with the outlet 15 in a fluid-conducting manner, the pressure in the control chamber 19 can be reduced, so that the adjustment element 17 is displaced via the return spring 21 in the second displacement direction, i.e., downwardly in the drawing plane, which in turn results in a displacement movement of the annular slide 24.

[0074] In the depicted, preferred embodiment variant, because the control chamber 19 can be supplied with cooling medium from the pressure side P of the cooling medium circuit via the control valve 11 for displacing the adjustment element 17 in the first displacement direction, and the valve chamber 20 lies at suction pressure or on the suction side of the cooling medium circuit 3, the pressure-exposed surface of the adjustment element in the control chamber 19 and the pressure-exposed surface of the adjustment element in the valve chamber 20 facing away from the latter are equally large, as is preferred. If the control chamber 19 is supplied with cooling medium lying at another pressure level and/or the valve chamber 20 is secured to the cooling circuit at another location, the setting force necessary for displacing the adjustment element 17 can be generated by realizing pressure-exposed surfaces of varying size.

[0075] As evident from FIG. 3, the control valve 11 or its [missing word] communicates with the control chamber 19 via a connecting channel 29 inside of the housing 13.

[0076] If the cooling capacity is now to be increased, the control valve 11 is actuated in such a way as to open a fluid connection between the inlet 14 (outlet of the cooler fluid path) and the cooling medium pump or (even wider) the outlet (15). This is done by the control valve 11 assuming a valve position upon its actuation, which ensures that the pressure-side cooling medium waiting at the pressure port PA can flow through the control valve 11 and via the working port AA into the connecting channel 29 and by way of the latter into the control chamber 19. The pressure in the control chamber 19 rises, so that the adjustment element 17 is activated upwardly in the drawing plane in a first displacement direction. As a result, the annular slide 24 is also moved downwardly in the drawing plane, and the distance between the annular slide 24 and a housing-side control edge 30 increases, so that the free flow cross section enlarges a connection between the chamber 28 and outlet 15, ensuring that the cooling medium pump 4 can siphon more cooling medium per unit of time out of the cooler fluid path 7 either now or depending on the previous position, i.e., the large cooling circuit is opened (further).

[0077] A cooling medium leakage from the control chamber 19 by the adjustment element 17 and to the valve chamber 20 is acceptable.

[0078] In the specific exemplary embodiment, enlarging the aforementioned free flow cross section between the cooler fluid path 7 and cooler medium pump, in particular between the chamber 28 and outlet 15, diminishes a free cross section between the outlet 15 and bypass fluid path (not marked). This is specifically resolved by displacing the annular slide 24 (or an alternative final control element) in the first displacement direction so as to reduce the free cross section out of a chamber 16 supplied via the bypass fluid path 5 and the outlet, in particular to the same extent as the free flow cross section between the chamber 28 and outlet 15 is enlarged.

[0079] In order to reduce the cooling capacity, cooling medium is diverted out of the control chamber 19 via the connecting channel 29 and the control valve 11 via the connecting line 10 into the cooling medium circuit, specifically into the chamber 28 of the cooling medium valve 8. FIG. 3 denotes the location of a position sensor marked 31, which is used to detect the position of the adjustment element 17 for preparation as the input signal for regulating the volume flow ratio or cooling medium temperature by means of a control unit (not shown).

[0080] In an embodiment variant not shown in detail with a discretely switching switch valve as the control valve, the latter is preferably activated by way of a thermal switch, wherein the actuator array for displacing the adjustment element 17 can remain unchanged. This alternative embodiment eliminates the need for a position sensor for detecting the position of the adjustment element.

[0081] FIG. 4 presents an alternative embodiment of a cooling circuit arrangement 1 designed based on the inventive concept, in particular for integration into a motor vehicle (MV).

[0082] In evidence is an engine 2 to be cooled, for example here designed as a combustion engine, which is integrated in a known manner into a cooling medium circuit 3. This cooling medium circuit 3 consists of a cooling medium pump 4 that is preferably driven by the engine, and conveys cooling medium from a suction side S of the cooling medium circuit 3 to a pressure side P.

[0083] After the engine, the cooling circuit branches into a bypass fluid path 5, which in the specific exemplary embodiment completely bypasses a cooler 6 (radiator), and a cooler fluid path 7 that flows through the cooler 6.

[0084] Both the bypass fluid path 5 and cooler fluid path 7 are routed to a cooling medium valve 8, which is shown as an equivalent circuit diagram on the right of the illustration, and once again in terms of structural design in the middle area of the drawing, so that the adjustment element 17 and the annular slide 24 (or an alternative final control element) displaceable by it for pressure flow variation can be discerned by the cooler fluid path and bypass fluid path. The cooling medium valve 8 can be used to set the volume flow ratio of the cooling medium volume flows flowing through the fluid paths 5, 7. In an alternative embodiment variant (not shown), the cooling medium valve can also be incorporated after the engine where the cooling medium circuit 3 branches into the bypass fluid path 5 and cooler fluid path 7, and set the inflow in at least one of these paths.

[0085] The cooling medium valve consists of a control valve 11, which is designed as a 4/3-way valve in the specific exemplary embodiment. This 4/3-way functionality can be realized by using a corresponding proportional valve, or alternatively by wiring two discretely switching valves, in particular two 3/2-way switch valves or also proportional valves. An embodiment as a multi-seat valve yet to be explained below is especially preferred, in which two valve bodies can be activated with a shared actuator.

[0086] In any event, the control valve 11 consists of a pressure port P.sub.A, which is hooked up to the pressure side P of the cooling circuit 3. The control valve further consists of a first working port B and a second working port A, as well as an outflow port T.sub.A, by way of which cooling medium can be diverted to the suction side S of the cooling circuit 3. As evident, the first working port B is joined in a fluid-conducting manner with the control chamber 19 of the cooling medium valve 8, which is bordered from one side of the adjustment element 17, while the second working port A is joined in a fluid-conducting manner with the valve chamber 20, which is bordered by the side of the adjustment element 17 facing away from the control chamber 19, so that the adjustment element 17 can as a result be driven like a dual-action piston cylinder drive. To this end, the adjustment element 17 is incorporated in a cylinder. Similarly to the exemplary embodiment according to FIG. 3, an annular slide 24 (mentioned above) can be displaced via the adjustment element 17, so as to thereby set the volume flow ratio between the cooling medium volume flows flowing between the bypass fluid path 5 and the cooler fluid path 7. The cooling medium valve 8 is shown twice on FIG. 4 to illustrate its function and/or structural design (even though only present once, of course), specifically the structural configuration as a piston-cylinder regulator on the left of the illustration, and as a hydraulic equivalent circuit diagram integrated into the cooling medium circuit on the right of the drawing plane.

[0087] The left half of the drawing on FIG. 4 depicts various switching states of the control valve 11, three in the specific exemplary embodiment. The currently switched, right switching state joins the first working port B with the pressure port P.sub.A, and hence with the pressure side P of the cooling circuit, causing pressure-side cooling medium to flow into the control chamber 19. At the same time, the second working port A is joined with the outflow port T.sub.A, so that cooling medium can be discharged from the valve chamber 20 via the outflow port T.sub.A to the suction side S of the cooling medium circuit. As a consequence, the adjustment element 17, and hence the annular slide 24 as well, moves to the right in the drawing plane in a first translational displacement direction in the depicted displacement position. The large coolant circuit shown on the right of the drawing plane is switched into the latter by means of the annular slide 24, so that all of the cooling medium flows over the cooling fluid path 7, and the bypass fluid path 5 is blocked.

[0088] In the switching position on the left side of the drawing plane, the control chamber 19 is joined with the suction side and the valve chamber 20 with the pressure side P of the cooling medium circuit, so that the adjustment element 17 is displaced to the left in the drawing plane in a second displacement direction, wherein, in the specific exemplary embodiment, all cooling medium flows through the bypass fluid path and completely circumvents the cooler 6 in the then resulting extreme switching position of the adjustment element, and hence of the annular slide 26. The control valve 11 is designed in such a way that, given a failure in energizing the valve actuator 32, here a solenoid actuator, the switching state of the control valve 11 described first and marked on FIG. 4 arises, thereby ensuring a fail-safe functionality in which the entire cooling medium volume flow flows over the cooler 6.

[0089] The control valve 11 can also be used to set another, here a middle switching position, in which both working ports B, A are joined with the outflow port T.sub.A of the control valve 11, and hence with the suction side S. As a result, the respective current position of the adjustment element, which if necessary can be detected via a path or position sensor, is kept, so that basically any intermediate position of intermediate volume flow ratios can be kept.

[0090] The left switching position of the control valve 11 includes the right switching position of the cooling medium valve or of its annular slide 24 (very basically, it is of course also possible, depending on the configuration of the cooling medium valve, to use final control elements other than an annular slide to switch the fluid flow in the cooling circuit).

[0091] FIGS. 5 to 7 show a preferred embodiment variant for a preferably used control valve 11 with 4/3-way functionality. The control valve 11 can be activated with a single control valve actuator 32, and consists of two valve bodies, specifically a first valve body 33 and a second valve body 34, which each can be displaced between two switching positions or valve seats 35, 36, 37, 38 by means of the valve actuator 32.

[0092] Located between the valve actuator 32 and first valve body 33 is a first spring I, which is supported at one end against the first valve body 33. The first spring I along with the first valve body 33 are penetrated by a rod- or piston-shaped adjusting part 39, which can be translationally displaced by the actuator 32. The adjusting part 39 is supported against the second valve body 34 in order to displace it, and penetrates a second spring II that impinges on the first valve body 33 on the drawing plane toward the right, against the valve seat 35. To this end, the second spring II is supported against a thrust bearing (not shown) penetrated by the adjusting part 39. The third valve body 34 is also impinged to the right in the drawing plane, specifically against the valve seat 37 by a third spring.

[0093] The control valve 11 consists of a pressure port PA and an outflow port T.sub.A, along with a first and second working port B, A, which are joined with the control chamber or valve chamber, as described in conjunction with FIG. 4. The control valve can be used to join the two working ports B, A alternatingly with the pressure port PA and outflow port T.sub.A, and in a switching position simultaneously with the outflow port T.sub.A, as has yet to be explained below (wherein an embodiment in which both working ports can be simultaneously joined with the pressure port PA is realizable).

[0094] In the switching position depicted on FIG. 5, which corresponds to the right switching position of the control valve 11 according to FIG. 4, all springs I to III are only tensioned with their spring preload. The pressure port P.sub.A is joined with the first working port B, and thus with the control chamber 19, while the fluid-conducting connection between the pressure port PA and second working port A is interrupted, but in return the second working port A is joined in a fluid-conducting manner with the outflow port T.sub.A by way of the second valve body 34. The (minimal) spring forces of the springs I, II and III acting in this switching position are shown in the spring force diagram according to FIG. 8, specifically at operation point O.sub.1 in the diagram, where the spring forces F of the three springs along with the sum of spring forces over the adjustment path of the valve actuator 32 or adjusting part 39 are recorded.

[0095] FIG. 6 shows an operation point O.sub.2 or the middle switching position of the control valve according to FIG. 4, in which both working ports B, A are joined with the outflow port T.sub.A, and hence with the suction side of the fluid circuit, while the pressure port P.sub.A is completely blocked. As evident, the actuator 32 or a final control element of the actuator is displaced further to the left in the drawing plane, and hence the spring I [presses] the first valve 33 against the valve seat 36, which lies opposite the valve seat 35. The position of the second valve body 34 is unchanged. The resulting spring forces are here visible on FIG. 8 given O.sub.2. In the position depicted, the adjustment element remains in the respectively current position, with there being no hydraulically resulting adjustment force.

[0096] FIG. 7 now shows a valve position of the control valve 11 that corresponds to the illustration on the left of FIG. 4, in which the valve chamber 20 is joined with the pressure side of the cooling circuit, and the control chamber with the suction side. This is achieved by having the adjusting part 39 that penetrates the first valve body 33 displace the second valve body 34 against its valve seat 38 lying opposite the valve seat 37. As a consequence, the connection between the second working port A and pressure port T.sub.A is interrupted, and the second working port A is joined with the pressure port P.sub.A in a fluid-conducting manner, while the first working port A remains joined with the outflow port T.sub.A by comparison with the working position O.sub.2. The corresponding active spring forces can be read from the diagram according to FIG. 8 at O.sub.3.

[0097] Shown on FIGS. 9 to 11 is an alternative, preferred embodiment variant of a preferably used control valve 11 with a 4/3-way functionality. The latter is configured in particular for a pressure-side use of the cooling medium valve in a cooling medium circuit, since, as has yet to be explained below, both the control chamber and valve chamber are joined with the pressure side of the cooling medium circuit in the middle control valve switching position. When interchanging the outflow port and pressure port, the control valve is designed in particular for a suction-side use of the cooling medium valve in a cooling medium circuit. The control valve can be activated with a single control valve actuator 32 (not shown in detail), and consists of two valve bodies, specifically a first valve body 33 and a second valve body 34, wherein the first valve body 33 closer to the actuator 32 can be displaced between two valve seats (switch valve seats) 35, 36, and the second valve body 34 can be displaced between a (switch) valve seat 37 and a valve seat 38 that can have a sealing function, but does not have to, based on the slider functionality yet to be explained. In this case, the other valve seat 38 is a stop, which limits the maximum displacement movement of the second valve body 34.

[0098] As evident from FIG. 9, the depicted control valve configured as a combined slide-multi-seat switch valve makes do with only two springs, specifically a first spring I and a second spring IIthe additional spring referred to as the first spring and provided in the exemplary embodiment described before can be eliminated, since the adjusting part 39 is fixedly joined with the valve body 34 or monolithically configured with it in the embodiment according to FIGS. 9 to 11. In the exemplary embodiment described previously, however, the rod- or piston-shaped adjusting part 39, which can be displaced by means of the actuator 32, penetrates the first valve body 34, i.e., is displaceable relative thereto.

[0099] The first spring I is supported at one end against a thrust bearing 40 arranged between the valve bodies 33, 34, which is fixedly arranged relative to a control valve housing 41 via fixing means (not shown). At the other end, the first spring I is supported against the first valve body 33, and impinges the latter against the valve seat 35 immediately adjacent to the actuator 32 on the right of the drawing plane. The second spring II is supported at one end against another fixed thrust bearing 42, and at the other end on the second valve body 34, and impinges the latter together with the final control element 39 to the right in the drawing plane, or the second valve body 34 against its valve seat 37.

[0100] As in the exemplary embodiment described above, the control valve 11 consists of a pressure port P.sub.A, an outflow port T.sub.A as well as a first and second working port B, A, wherein the first working port B is joined with the control chamber, and the second working port A is joined with the valve chamber. The control valve 11 can be used to alternatingly join the two working ports B, A with the pressure port P.sub.A and outflow port T.sub.A, and in a switching position (see FIG. 10) simultaneously with the pressure port PA (wherein an embodiment can be realized here as well in which both working ports are simultaneously joined with the outflow port T.sub.A).

[0101] In the switching position shown on FIG. 9, both springs I and II are only tensioned with their spring preload. The pressure port P.sub.A is joined with the first working port B, and hence with the control chamber 19, while the fluid-conducting connection between the pressure port P.sub.A and second working port A is interrupted. However, the second working port is joined in a fluid-conducting manner with the outflow port T.sub.A via radial bores 43 in the adjusting part 39. Therefore, as opposed to the exemplary embodiment described above, a valve slide function is assigned to the adjusting part 39. For this purpose, an axial through bore 44 (through channel) is provided in the adjusting part 39, which is permanently joined in a fluid-conducting manner with the outflow port T.sub.A, and which in the switching position depicted is joined with the second working port A via the radial bores 43. The (minimal) spring forces exerted by springs I and II in the switching position shown are depicted in the spring force diagram according to FIG. 12, specifically at operation point O.sub.1 in the diagram, at which the spring forces F of the three springs along with the sum of spring forces is recorded over the of the adjustment path of the valve actuator 32 or adjusting part 39.

[0102] FIG. 10 shows an operation point O.sub.2 or a middle switching position of the control valve 11 in which both working ports B, A are joined with the pressure port P.sub.A, and hence with the pressure side of the fluid circuit, while the outflow port T.sub.A is completely blocked. As evident, the actuator 32 or the adjusting part 39 has been displaced further to the left in the drawing plane through displacement of the actuator 32, so that the radial bores 43 are sealed by an (inner) circumferential wall 45 of a guiding channel 46 for the adjusting part 39 leading to the working port T.sub.A in a fluid-conducting manner. The above illustrates the valve slide functionality of the adjusting part 39, which in the middle position shown interrupts the fluid-conducting connection between the second working port A, and hence the valve chamber and the outflow port T.sub.A. At the same time, the second valve body 34 was axially lifted from is valve seat 37, thereby resulting in a fluid-conducting connection between the second working port A and pressure port P.sub.A. Due to the unchanged valve position of the first valve body 33, the pressure port P.sub.A remains joined with the first working port B in a fluid-conducting manner, so that both working ports A, B (as opposed to the exemplary embodiment according to FIGS. 5 to 7) are joined with the pressure side of the cooling medium circuit. The surfaces on the adjustment element are designed in such a way that no hydraulic adjustment force on the latter results in the respective adjustment element position at the operation point O.sub.2 shown.

[0103] FIG. 11 now depicts a (completely through connected) valve position of the control valve 11, in which the valve chamber 20 is joined with the pressure side of the cooling circuit, and the control chamber with the suction side. Expressed differently, a fluid-conducting connection between the second working port A and pressure port PA exists in the operation point O.sub.3 shown (see also spring force characteristic on FIG. 12), while the pressure port PA is decoupled from the first working port B, and hence from the control chamber. The latter is joined in a fluid-conducting manner with the outflow port T.sub.A via the through bore 44 in the adjusting part 39. The existing interaction with the circumferential wall 45 of the guiding channel 46 keeps the radial bores 43 sealed.

[0104] In order to reach the valve position O.sub.3 shown, the actuator 32 was used to displace the actuating part 39 further to the left in the drawing plane by comparison to the operation point O.sub.2 according to FIG. 10, specifically until it hits the second valve body 34 against its stop or valve seat 38. Further displacing the adjusting part 39 causes it to take along the first valve body 33 toward the left in the drawing plane, i.e., lifting it from the valve seat 35, and displace it against the axially opposing additional valve seat 36. For example, this entrainment takes place via an annular element (not shown), which to this end is held in a circumferential annular groove 47 in the adjusting part 39. As a result, this interrupts the fluid-conducting connection between the pressure port PA and the first working port B, and opens the fluid-conducting connection between the first working port B and the outflow port T.sub.A, since a control valve chamber 48 is permanently connected with the outflow port T.sub.A in a fluid-conducting manner via the axial through bore 44, and is now joined with the first working port B in a fluid-conducting manner due to the valve body 33 being displaced away from the valve seat 35.

[0105] As in the exemplary embodiment according to FIGS. 5 to 7, the adjusting part 39 penetrates the first valve body 33, and can be displaced relative to it via the shared actuator 32, wherein the valve body 33 for the adjusting part 39 is axially entrained in a last adjusting strokebecause the second valve body 34 is integrally designed with the adjusting part 39, two of the valve bodies 34 and the adjusting part 39 are positively coupledthe closure functionality for decoupling the outflow port T.sub.A from the second working port is there realized via the slider functionality of the adjusting part 39, as explained.

[0106] In an alternative embodiment variant, the outflow port T.sub.A and pressure port PA and/or the working ports can be changed out. If the outflow port T.sub.A and pressure port PA are interchanged in the control valve shown, both the control chamber 19 and valve chamber 20 of the cooling medium valve 8 are joined with the suction side of the cooling medium circuit in the middle switching position of the control valve 11, so that the control valve 11 can then be integrated into a cooling medium circuit in the manner depicted on FIG. 4. The switching position of the control valve according to FIG. 11 (with outflow and pressure ports interchanged) then corresponds to the right switching position of the control valve on FIG. 4. The middle switching position according to FIG. 10 (also once again with outflow and pressure port interchanged) corresponds to the middle switching position of the control valve 11 according to FIG. 4, and the switching position according to FIG. 9 (with outflow and pressure port interchanged) corresponds to the left switching position of the control valve according to FIG. 4.

REFERENCE LIST

[0107] 1 Cooling circuit arrangement [0108] 2 Engine [0109] 3 Cooling medium circuit [0110] 4 Cooling medium pump [0111] 5 Bypass fluid path [0112] 6 Cooler [0113] 7 Cooler fluid path [0114] 8 Cooling medium valve [0115] 9 Hydraulic actuator [0116] 10 Connecting line [0117] 11 Control valve [0118] 12 Outlet opening [0119] 13 Housing [0120] 14 Inlet [0121] 15 Outlet [0122] 16 Chamber [0123] 17 Adjustment element [0124] 18 Cylinder [0125] 19 Control chamber [0126] 20 Valve chamber [0127] 21 Return spring [0128] 22 Thrust bearing [0129] 23 Through opening [0130] 24 Annular slide [0131] 25 Shell surface section [0132] 26 Floor section [0133] 27 Openings [0134] 28 Chamber [0135] 29 Connecting channel (diverting line) [0136] 30 Control edge [0137] 31 Position sensor [0138] 32 Valve actuator [0139] 33 First valve body [0140] 34 Second valve body [0141] 35 Valve seat [0142] 36 Valve seat [0143] 37 Valve seat [0144] 38 Valve seat [0145] 39 Adjusting part [0146] 40 Thrust bearing [0147] 41 Control valve housing [0148] 42 Thrust bearing [0149] 43 Radial bore [0150] 44 Through bore [0151] 45 (Inner) circumferential wall [0152] 46 Guiding channel [0153] 47 Annular groove [0154] 48 Control valve chamber [0155] A.sub.A Working port of control valve [0156] P.sub.A Pressure port of control valve [0157] T.sub.A Outflow port of control valve [0158] P Pressure side [0159] S Suction side [0160] B First working port [0161] A Second working port [0162] F Spring force [0163] I First spring [0164] II Second spring [0165] III Third spring [0166] First operation point [0167] Second operation point [0168] Third operation point