DE102019111829B4 - Control valve for controlling coolant flow in a cooling system - Google Patents

Abstract

Control valve (26) for controlling a coolant flow in a cooling system (10), in particular in a cooling system (10) for cooling a plurality of heat sources (11, 12), with a valve housing (31) which has at least two inlet openings (32, 33) for supply a first and a second coolant flow (36, 37), with a fluid space (29) which is in flow connection with the at least two inlet openings (32, 33), and with at least one outlet opening (34) which is separated from the fluid space (29 ), wherein the at least two inlet openings (32, 33) are each assigned a valve (38, 39) which can be arranged at least in an open position (49) and a closed position (48), the positions of the valves (38, 39 ) can be adjusted independently of one another for independently controlling the coolant streams (36, 37) flowing through the inlet openings (32, 33), with a filter element (30) in the fluid chamber (29) for filtering the coolant flowing out of the outlet opening (34). Lmittel is present, which extends into the fluid space (29), wherein the fluid space (29) is formed substantially cuboid.

Description

The invention relates to a control valve for controlling a coolant flow in a cooling system, in particular in a cooling system for cooling a plurality of heat sources.

From the DE 10 2014 009 772 A1 an electric vehicle is known which is driven by an electric drive machine. To increase the range, the electric vehicle also includes a fuel cell as a so-called "range extender". During operation, the electric drive motor and the fuel cell generate heat, which is dissipated by a common cooling system. After a cold start of the electric vehicle, the coolant initially only flows through the electric drive unit. This achieves rapid heating of the coolant and the drive machine. A thermostatic valve is provided between the drive motor and the fuel cell, which supplies at least a partial volume flow of the coolant to the fuel cell after a defined coolant temperature has been reached. To control the coolant temperature, the thermostatic valve can also feed a partial volume flow of the coolant to a cooler via a bypass. This cooling system means that the electric drive machine and the fuel cell are thermally dependent, since the temperature of the coolant supplied to the fuel cell depends on the outlet temperature of the coolant from the drive machine.

the DE 10 2010 034 484 A1 discloses a cooling system for an electric vehicle with at least two components to be cooled. In this case, one of the components to be cooled is preceded by a valve arrangement made up of two separate control valves, which enables mixing of coolant flows at different temperatures.

the U.S. 2003/0 070 714 A1 shows a valve unit with a rotatable valve part with passage openings. The valve part can be controlled by means of a servo motor. The valve unit is not designed as a mixing valve.

the DE 103 23 900 A1 shows a multi-way valve with a valve body, a valve chamber, at least three main valve connections leading to the valve chamber and a rotatable, cylindrical valve member arranged in the valve body. Due to the common valve element, the main valve positions are coupled to one another and the valves cannot be adjusted independently of one another.

In the DE 102 19 481 A1 an internal combustion engine with a cooling water circuit is specified. The volumetric flow is controlled by a water pump. The cooling water circuit includes, among other things, two mixing valves, by means of which temperature control can be carried out. The mixing valves can, for example, be designed as thermostatic valves or rotary slides. Further details on the structure of the mixing valves are not disclosed.

In the JP H07-293 243 A a submersible line with an outlet is specified within a storage tank. A mains filter is arranged in the immersion line. A control valve with two inlet openings and one outlet opening is not specified.

The object of the present invention is to propose a control valve for controlling a coolant flow in a cooling system which contributes to optimized cooling of the components arranged in the cooling circuit.

According to the invention, this object is achieved by a control valve according to the features of claim 1 . Particularly preferred embodiments of the invention are specified in the dependent claims.

According to the invention, it is provided that the control valve has at least two inlet openings, each of which is assigned a valve which can be arranged at least in an open position and in a closed position, and possibly in intermediate positions between the open position and the closed position, with the position of the valves being independent is adjustable (controllable or adjustable) from one another for the independent regulation of the coolant streams flowing through the inlet openings.

By arranging the valves in the open and/or closed position and/or intermediate position, each valve can be fully closed or (fully) opened independently of one another. If one valve is in the open position and the other valve is in the closed position, only one of the two coolant streams flows through the open valve into the fluid chamber and leaves the control valve through the outlet opening. If both valves are arranged in the open position, both coolant streams flow through the valves and are combined in the common fluid space to form a coolant mixed stream. The fluid space then acts as a mixing chamber.

By arranging at least one of the valves in at least one intermediate position, the (partial) volume flows of the two coolant flows can be regulated independently of one another. In particular, coolant streams are supplied to the control valve via the inlet openings have different temperatures. Since the volume flows of the coolant flows can be regulated separately from one another, the mixing ratio between the two coolant flows can be changed. The coolant temperature of the mixed coolant flow can be adjusted by the mixing ratio of the two coolant flows. By being able to adjust the individual (partial) volume flows of the two coolant flows, the volume flow of the mixed coolant flow can be set independently of its temperature. The temperature and/or the volume flow of the mixed coolant flow can thereby be adapted to a required coolant temperature and/or a required coolant volume flow for a heat source to be cooled.

In an advantageous development of the control valve, it can be provided that the valve has a valve seat and a movable valve element with a coolant passage is arranged in the valve seat, and the coolant passage preferably forms a flow cross section that is the same size as or larger than a flow cross section of the inlet opening. A control valve with three chambers is thus obtained, the chambers being flow-mechanically decoupled from one another downstream of the inlet openings, formed by the coolant passages. The fluidic coupling takes place downstream in the fluid chamber as the third chamber. As a result, a valve can be formed which, with a good mixing effect, has a large flow cross section for the coolant flowing through. This results in a low flow resistance or pressure loss for the coolant flow through the valve.

In a development of the control valve, it can be provided that the valve element is designed as a cylindrical body and the valve seat has a cylindrical inner contour, the valve element being provided in the valve seat such that it can rotate about its longitudinal axis. With such a design of the valve element, the least possible deflection of the coolant flow in the valve can be achieved. As a result, the pressure loss through the valve can be further reduced. In addition, due to the cylindrical shape, a small construction volume can be achieved, so that the control valve can also be integrated within a heat source with a small space requirement. The longitudinal axis is preferably aligned transversely to the main direction of flow. The valve element can be adjusted radially in a space-saving and efficient manner by means of an electric actuator, for example a servo motor, arranged on its end face.

In a particularly preferred embodiment of the control valve it can be provided that the valve element is designed as a cylindrical hollow body, the coolant passage having two opposing, z. B. circular, fluid openings in the shell of the hollow body and a cavity in the hollow body or is formed therefrom. Due to the design of the valve element as a hollow body, a low weight of the valve element can be achieved. The execution of an actuating movement of the valve element is thus made possible with a low actuating force. In addition, the cavity offers a large flow volume for the coolant flowing through the valve, which can result in a further reduction in pressure loss.

An advantageous development of the control valve provides that an inside diameter _{D H} of the hollow body and/or the fluid openings is designed to be the same size or larger than the flow cross section DE of the inlet opening and/or the feed lines to the control valve _DE . For example, the ratio D _H /D _E can be between 1 and 1.5, e.g. B. be 1.2. Such a configuration allows the largest possible flow volume for the coolant to be formed within the hollow body. This also ensures that the coolant flow is influenced as little as possible, with the aim of achieving as little pressure loss as possible.

Provision can preferably be made for the valve elements to be designed in the same way. As a result, the simplest possible structural design of the control valve can be achieved. In addition, the similar design of the valve elements simplifies coordinated regulation of the two coolant flows.

In a development of the valve, it can be provided that at least one of the valve elements is arranged as a fit in the valve seat with an exact fit, but still rotatable. As a result, a sufficient tightness of the valve can be achieved even without using a sealing element for sealing the valve in the closed position and/or the two chambers or coolant passages against one another.

In an alternative development of the valve, provision can be made for a clearance fit to be provided between at least one of the valve elements and the valve seat, so that in the closed position of the at least one valve element a residual flow of coolant can flow through the valve. With a valve seat designed as a cylindrical bore and a cylindrical valve element, a clearance fit of z. B. H11/d9 (tolerance class combination) turned out to be suitable. Due to the residual flow of coolant flowing through the valve, particularly in in aviation, with operation at high altitudes and thus low temperatures, but also during winter operation of a vehicle, freezing of the valve and the heat source arranged downstream at low temperatures in the closed position can be prevented. At the same time, the residual flow can act as a lubricant.

The valve elements and/or the valve seats can preferably each be made of the same material. The valve element and at least the valve seat are preferably made of a light metal, plastic, composite material or similar material with a low intrinsic weight. Aluminum (alloy), e.g. B. with a coating, z. B. an anodized layer, but also other light metals such as magnesium (alloy) can be used. Due to the same pairing of materials, the valve element and at least the valve seat have the same thermal expansion coefficients. This results in the same or at least similar expansion properties when the temperature changes, so that the valve element is prevented from jamming in the valve seat and, if there is a defined loose fit for a residual flow, this is maintained.

In a particularly preferred embodiment of the control valve, an electric actuator can be assigned to the valve elements, in particular each one, by means of which an actuating movement of the valve elements can be controlled independently of one another by an electric actuator and a controller can preferably be provided which controls the actuator as a function of a control parameter , in particular a temperature value and/or a volume flow value. The actuator can z. B. space-saving and efficiently formed by a (servo) motor, which can be arranged on the end face of the valve element and the valve element can be adjusted radially. As a result, a thermally controlled and/or volume flow-controlled control valve is available, which enables volume flow control as a function of a parameter, in particular an external parameter. This external parameter can be, for example, an operating temperature, in particular an optimal operating temperature, of the heat source or a parameter of the coolant volume flow flowing through the heat source. In this way, the coolant temperature and/or the coolant volume flow of the coolant flow can be adjusted to the optimal operating temperature of the heat source.

In a further development of the control valve, it can be provided that the actuator can be controlled by the control in such a way that the valve element can be moved between the open position and the closed position or an intermediate position in between, for control of a continuous volume flow, or between the open position and the closed position , to generate a pulsating flow of coolant, is adjustable. For pulsating control z. B. comparatively simply designed, inexpensive and / or robust valves can be used. The setting of the individual volume flows results from the temporal frequency of the pulsation. The fluid chamber as a "buffer volume" results in a continuous coolant mixed flow from the outlet opening.

In a development of the control valve according to the invention, there is a filter element in the fluid space for filtering the coolant flowing out of the outlet opening, which extends into the fluid space, the fluid space being essentially cuboid. The filter element is preferably made of a fluid permeable material, e.g. B. from sintered metal or a fine-mesh screen formed. Such a filter element can ensure that the heat source downstream of the control valve is supplied only with a correspondingly filtered flow of coolant. Due to the fact that the filter element extends into the fluid space and the fluid flows through it from the outside to the inside, the filter surface can be enlarged, which results in a lower pressure loss through the filter element. For this purpose, the filter element can be pot-shaped, conical, truncated, pyramid-shaped or similar.

A compact design results when the valve housing is essentially cuboid (i.e. apart from attachments such as line connections and/or fastening points). For example, the valve housing can have a length of around 150 mm and a height and depth of less than half the length, e.g. B. have a height of 55 mm and a depth of about 60 mm. The valve element can z. B. an outer diameter of about 40 mm, z. B. 38 mm, and have a height of about 50 mm. The dimensions result in particular from the application.

If the inlet openings and the outlet opening are arranged in relation to the fluid space in such a way that during operation the main flow direction of the coolant flowing into the fluid space is aligned at right angles to the main flow direction of the coolant flowing out of the fluid space, good mixing of the coolant flows with low pressure loss can be achieved with a compact design of the control valve can be achieved in the fluid space. This is particularly the case when e.g. B. the inlet openings on the same side open into the fluid space and the flow cross sections of the inlet openings at their mouths more than 50%, z. B. take up 70% of the corresponding side surface of the fluid space. The mouth of the outlet opening preferably occupies more than 50% of another side surface of the fluid chamber, preferably aligned at right angles to the other side surface. The fluid space is at least essentially cuboid in shape, which offers manufacturing advantages in the design of the sealing surfaces.

• 1 ein exemplarisches Schaltschema eines Kühlsystems zum Kühlen mehrerer Wärmequellen mit zwei erfindungsgemäßen Regelventilen,
• 2 eine schematische Schnittansicht eines der Regelventile gemäß 1,
• 3 eine perspektivische Detailansicht eines Ventilelements des Regelventils gemäß 2,
• 4 eine erste Schaltstellung des Regelventils in einer stark schematisierten Darstellung,
• 5 eine zweite Schaltstellung des Regelventils in einer stark schematisierten Darstellung und
• 6 eine dritte Schaltstellung des Regelventils in einer stark schematisierten Darstellung.

The invention and other advantageous embodiments and developments thereof are described and explained in more detail below with reference to the examples shown in the figures. The features to be found in the description and the drawings can be used according to the invention individually or collectively in any combination. Show it:

• 1 an exemplary circuit diagram of a cooling system for cooling multiple heat sources with two control valves according to the invention,
• 2 a schematic sectional view of one of the control valves according to FIG 1 ,
• 3 a detailed perspective view of a valve element of the control valve according to FIG 2 ,
• 4 a first switching position of the control valve in a highly schematic representation,
• 5 a second switching position of the control valve in a highly schematic representation and
• 6 a third switching position of the control valve in a highly schematic representation.

1 shows an example of a cooling system 10 for cooling two heat sources 11, 12 in a common cooling circuit 13. This cooling system 10 enables the provision of different coolant temperatures and/or coolant volume flows, so that the heat sources 11, 12 can be individually controlled for cooling. In particular, the heat sources 11, 12 can be operated at different operating temperatures. With a corresponding extension of the cooling system 10, more than two heat sources 11, 12 can be provided in the cooling circuit 13.

The heat sources 11, 12 can be designed as thermal combustion engines, as fuel cells, as an electric motor or as power electronics that require cooling. In particular, a combination of different heat sources 11, 12 is provided in the cooling system 10, for example a combination of a thermal combustion engine with a fuel cell or an electric motor. The cooling system 10 with the heat sources 11, 12 can be designed as a hybrid system. Such cooling systems with different heat sources 11, 12 are increasingly being used in aircraft, in particular in airplanes. In an aircraft with such a cooling system, for example, thermal turbomachines take over the function of the drive and an additional fuel cell takes over the electrical supply of the on-board systems when the aircraft is on the ground. However, such hybrid systems with different heat sources 11, 12 are also increasingly being used in motor vehicles and/or ships.

In aircraft, there is a continuous effort to reduce both the weight and the cost of cooling systems 10 . This can be done by reducing the number of components, with individual components of the cooling system 10 being used jointly. Reducing the number of components also reduces the probability of failure, so that safety advantages are also achieved.

The heat sources 11, 12 are thermally connected to one another by the common cooling circuit 13, but form separate mechanical and/or electrical systems. A coolant circulates in the cooling circuit 13 and flows through the two heat sources 11, 12 for cooling. A coolant pump 14 is provided downstream of the heat sources 11, 12 to convey the coolant. The cooling circuit 13 is connected to an expansion tank 15 . This is used to compensate for changes in the volume of the coolant in the cooling circuit 13 and to store coolant. In order to avoid excess pressure in the cooling circuit 13 , the cooling circuit 13 also has a bypass line 23 with a pressure relief valve 24 .

The coolant pump 14 is connected to a cooling device 21 and to two control valves 26 according to the invention. At least a partial volume flow of the coolant heated by the heat sources 11, 12 can be fed to the cooling device 21 through the connection to the coolant pump 14. The coolant heated by the heat sources 11 , 12 is cooled by the cooling device 21 and then a cold coolant flow 36 is supplied to the control valves 26 via a coolant supply 22 .

The control valves 26 are also flow-connected to the coolant pump 14, so that in addition to the cold coolant flow 36, at least a partial volume flow of the warm coolant flow 37 heated by the heat sources 11, 12 can be fed to them. Each of the control valves 26 is assigned to a heat source 11, 12 in each case. Each of the control valves 26 is connected to the heat source 11 , 12 associated with the respective control valve 26 via a separate coolant flow path 18 , 19 .

2 shows a schematic sectional view of one of the control valves 26. The control valve 26 has a valve housing 31 with an essentially cuboid external shape, on which two inlet openings 32, 33 and one outlet opening 34 are provided on two side walls arranged at right angles to one another. The valve housing 31 can have a cover with which the valve housing 31 can be closed. For example, the cold coolant flow 36 can be fed to the control valve 26 via the first inlet opening 32 and the warm coolant flow 37 can be fed via the second inlet opening 33 . A first valve 38 and a second valve 39 are provided in the housing 31 . The valves 38, 39 are each assigned to one of the inlet openings 32, 33. As in 2 shown, the inlet openings 32, 33 can each form a channel in which one of the valves 38, 39 is arranged. The valves 38, 39 allow the inlet openings 32, 33 to be opened or closed independently of one another.

In the housing 31 there is an essentially cuboid fluid space 29 via which the inlet openings 32, 33 and the outlet opening 34 are in flow communication with one another. The fluid chamber 29 is arranged downstream of the valves 38,39. In the fluid space 29, the cold and warm coolant streams 36, 37 are brought together, flowing into the fluid space 29 from a side wall for a compact configuration. This results in the coolant flows 36 , 37 being mixed to form a mixed coolant flow 40 . This mixed coolant flow 40 can exit from the fluid chamber 29 through the outlet opening 34 . For a good mixing effect with a compact design, the outlet opening is arranged in particular on a side wall of the fluid space arranged at right angles to the other side wall.

The valves 38, 39 are each formed, for example, by a cylindrical valve seat 41 and by a valve element 42, for example cylindrical, arranged in the valve seat 41. In the valves 38, 39 sensor elements such. B. for flow and / or temperature measurement, be present (not shown here). The valve seat 41 is formed in the housing 31 as a cylindrical bore, for example. In particular, the valve seat 41 has, for example, a cylindrical inner contour. Although the following explanations are limited to the cylindrical design of the valves 38, 39, the valve elements 42 can also be designed as spherical valve elements, which are arranged in a spherical valve seat, or have any other desired design.

A detailed perspective view of the cylindrical valve element 42 is shown in FIG 3 shown. The valve element 42 is designed as a cylindrical hollow body 43 . The hollow body 43 can be a sleeve, for example. The end faces of the hollow body 43 can be open or closed. A cavity 44 is formed within the hollow body 43 . In the jacket of the cylindrical hollow body 43, two fluid openings 46, 47 are provided. These fluid openings 46, 47 are in particular made opposite one another in the jacket of the hollow body 43. Likewise, the fluid openings 46, 47 can be arranged at an angle to one another and/or at different heights. Through the fluid openings 46, 47 and the cavity 44, a coolant passage 28 for the coolant is formed. The flow cross section _{D F} of the fluid openings 46, 47 is preferably designed to be the same size or larger than the flow cross section DE of the inlet openings 32, 33 and/or the supply lines to the control valve. The inner diameter D _H of the cavity 44 is preferably formed larger than the flow cross section _DE of the inlet openings 32, 33 and/or the feed lines to the control valve.

The valve element 42 is rotatably mounted in the valve seat 41 about its longitudinal axis L. To reduce friction during rotation, a bearing is preferably present at a suitable point (not shown here), z. B. may include a sliding disk or may be formed by a needle bearing. The bearing can be provided in particular on a front closure cap of the valve element 42, with the jacket of the cylindrical hollow body 43 being pressed against the closure cap during operation.

Due to the rotatable mounting of the valve element 42, a closed position 48 and an open position 49 of the valve element 42 can be assumed by a rotary movement of the valve element 42. In the open position 49, the fluid openings 46, 47 and the inlet opening 32, 33 are arranged at least essentially congruently with one another. This allows the coolant to flow through the coolant passage 28 . In the open position 49, the largest flow cross section of the valve 38, 39 is formed. This corresponds z. B. the flow cross section DE of the inlet openings 32, 33 and/or the flow cross section _{D F} of the fluid openings 46, 47. The actuating movement of the valve element 42 causes the fluid openings 46, 47 of the valve element 42 to move towards the inlet opening 32, 33, as a result of which the flow cross section of the valve 38, 39 is gradually decreased. This results in a reduction in the volume flow that flows through the valve 38, 39.

The rotational movement of the valve elements 42 is controlled in each case by an electric actuator, not shown in detail. This actuator includes an actuating device which is connected to the valve elements 42 and enables the valve elements 42 to be controlled independently. The actuator is a servo motor, for example, which is arranged on the end face of each of the valve elements 42 and causes a radial adjustment movement. The actuator is controlled in particular by a controller 25 . The controller 25 controls the actuator depending on a control parameter. This control parameter is, in particular, a detected temperature value and/or a volume flow in the cooling circuit 13. In particular, the control parameter is an operating temperature of the heat source 11, 12 assigned to the respective control valve 26, an inlet or outlet temperature of the coolant of this heat source 11, 12 and/or an optimal one Operating temperature or an optimal operating temperature range of this heat source 11, 12 or a coolant volume flow value of the coolant flowing through the heat source 11, 12.

The valve elements 42 and at least the valve seat 41 and/or the housing 31 are made of the same material. As a result, the valve elements 42 and the valve seat 41 have the same thermal expansion coefficient. The valve elements 42 and at least the valve seat 41 and/or the housing 31 are preferably made of a light metal, for example an aluminum or magnesium alloy. Likewise, the valve elements 42 and at least the valve seat 41 and/or the housing 31 can be formed from a plastic or from a composite material or the like. In the event of temperature fluctuations, the same pairing of materials prevents the valve element 42 from jamming in the valve seat 41 . The two valve elements 42 are in particular of the same design.

The valve elements 42 can be arranged in the valve seat 41 with an exact fit or with a loose fit. In both embodiments, no seal between the valve element 42 and the valve seat 41 is required. If the valve element 42 is provided with a loose fit in the valve seat 41, a small residual flow of coolant can also flow through the valve 38, 39 when the valve element 42 is in the closed position. This can prevent freezing of the valve 38, 39 and downstream heat sources at low temperatures.

A filter element 30 for filtering the coolant is provided in the fluid space 29 . The filter element 30 is arranged at the outlet opening 34 of the fluid space 29 . The filter element 30 is designed, for example, in the shape of a pot and extends into the fluid chamber 29. A large filter surface is thereby formed, which reduces the pressure loss through the filter element 30. The filter element 30 can also have any other desired geometry. The filter element 30 is in particular made of a sintered metal.

the 4 until 6 show examples of different switching positions of the control valve 26 in a highly schematic representation.

In the first switching position according to 4 the valve element 42 of the first valve 38 is arranged in the open position 49 and the valve element 42 of the second valve 39 is arranged in the closed position 48 . In the open position 49, the first valve 38 is completely open, so that the cold coolant flow 36 flows completely through the inlet opening 32 into the fluid chamber 29. The second valve 39 is completely closed in the closed position 48 so that the warm coolant flow 37 does not flow through the inlet opening 33 . If the valve element 42 is arranged with a loose fit in the valve seat 41, a small residual flow of coolant still flows through the second valve 39 in the closed position 48. In this switching position, the mixed coolant flow 40 is thus formed by the cold coolant flow 36.

5 shows a second switching position of the control valve 26. In this second switching position, the valve element 42 of the first valve 38 is in the closed position 48 and the valve element 42 of the second valve 39 is in the open position 49. As a result, the first valve 38 for the cold coolant flow 36 is complete closed, the second valve 39, however, fully opened for the warm coolant flow 37. In this switching position, the mixed coolant flow 40 is thus formed by the warm coolant flow 37 .

6 shows an example of a third switching position of the control valve 26 in which the valve elements 42 of the valves 38, 39 are each arranged in an intermediate position 51. This intermediate position 51 can be any angular position of the valve element 42 between the closed position 48 and the open position 49 . In this way, stepless adjustment of the valve element 42 is possible. By changing the angular position of the valve element 42, the flow cross section of the coolant passage 28 is reduced or increased, so that a precise volumetric flow control of the coolant flows 36, 37 is made possible.

The valve elements 42 can assume different intermediate positions 51 independently of one another. As a result, the volume flows of the warm coolant flow 37 and the cold coolant flow 36 can be regulated independently of one another. A mixing ratio between the warm coolant flow 37 and the cold coolant flow 36 can be changed by controlling the volume flows. By changing the mixing ratio between the warm coolant flow 37 and the cold coolant flow 36, a mixed coolant flow 40 can be generated with a coolant temperature which lies between the coolant temperature of the cold and the warm coolant flow 36, 37. The coolant temperature and the volume flow of the mixed coolant flow 40 can be controlled simultaneously and/or independently of one another by the control valve 26 .

If, for example, the valve elements 38, 39 are adjusted synchronously with one another, for example both valve elements 42 are opened or closed in the same ratio, the volume flow of the mixed coolant flow 40 changes, but the temperature of the mixed coolant flow 40 remains constant, since the mixing ratio between the cold and warm coolant flow 36 , 37 is not changed by the synchronous adjustment of the valve elements 42. On the other hand, through a coordinated, asynchronous adjustment of the valve elements 42, for example one valve element 42 is opened and the other valve element 42 is closed in the same ratio, the coolant temperature of the coolant mixed flow 40 can be increased or decreased due to the changed mixing ratio between the warm and cold coolant flows 36, 37 , The volume flow of the mixed coolant flow 40 remains constant due to the coordinated adjustment of the valve elements 42 . In addition, the coolant temperature of the mixed coolant flow 40 can be increased or decreased by a corresponding asynchronous adjustment of the valve elements 42 and at the same time the volume flow of the mixed coolant flow 40 can be increased or decreased.

The control valve 26 according to the invention provides a mixing device that contributes to optimized cooling of the components arranged in the cooling circuit due to the separate controllability of the cold and warm coolant flow. Due to the construction space and weight-optimized design, the control valve can be used particularly advantageously in aviation.

Reference List

10

cooling system

11

heat source

12

heat source

13

cooling circuit

14

coolant pump

15

surge tank

18

coolant path

19

coolant path

21

cooling device

22

coolant supply

23

bypass line

24

pressure relief valve

25

regulation

26

control valve

28

coolant passage

29

fluid space

30

filter element

31

Housing

32

intake port

33

intake port

34

exhaust port

36

cold coolant stream

37

warm coolant stream

38

Valve

39

Valve

40

mixed coolant flow

41

valve seat

42

valve element

43

hollow body

44

cavity

46

fluid port

47

fluid port

48

closed position

49

open position

51

intermediate position

Claims (13)

Control valve (26) for controlling a coolant flow in a cooling system (10), in particular in a cooling system (10) for cooling a plurality of heat sources (11, 12), with a valve housing (31) which has at least two inlet openings (32, 33) for supply a first and a second coolant flow (36, 37), with a fluid space (29) with the at least two inlet openings (32, 33) is flow-connected, and with at least one outlet opening (34) which discharges from the fluid chamber (29), with each of the at least two inlet openings (32, 33) being assigned a valve (38, 39) which has at least can be arranged in an open position (49) and a closed position (48), the positions of the valves (38, 39) being adjustable independently of one another for the independent regulation of the coolant streams (36, 37) flowing through the inlet openings (32, 33). , wherein in the fluid space (29) there is a filter element (30) for filtering the coolant flowing out of the outlet opening (34), which extends into the fluid space (29), the fluid space (29) being essentially cuboid. control valve claim 1 , characterized in that the valve (38, 39) has a valve seat (41) and a movable valve element (42) with a coolant passage (28) is arranged in the valve seat (41) and the coolant passage (28) has a flow cross section (D _F ) which is equal to or larger than a flow cross section (D _E ) of the inlet opening (32, 33). control valve claim 2 , characterized in that the valve element (42) is designed as a cylindrical body and the valve seat (41) has a cylindrical inner contour, the valve element (42) being arranged in the valve seat (41) such that it can rotate about its longitudinal axis (L). control valve claim 2 or 3 , characterized in that the valve element (42) is designed as a cylindrical hollow body (43), wherein the coolant passage (28) (43) has two opposite, z. B. circular, fluid openings (46, 47) in the jacket of the hollow body (43) and a cavity (44) in the hollow body (43). control valve claim 4 , characterized in that an inner diameter (D _H , D _F ) of the hollow body (43) and/or the fluid openings (46, 47) is designed to be the same size or larger than the flow cross section (D _E ) of the inlet opening (32, 33). Control valve according to one of claims 2 until 5 , characterized in that the valve elements (42) are designed in the same way. Control valve according to one of claims 2 until 6 , characterized in that at least one of the valve elements (42) is arranged with a precise fit in the valve seat (41). Control valve according to one of claims 2 until 6 , characterized in that a clearance fit is provided between at least one of the valve elements (42) and the valve seat (41), so that in the closed position (48) of the at least one valve element (42) a residual flow of the coolant through the valve (38, 39) , In particular between the valve element (42) and the valve seat (41), can flow. Control valve according to one of claims 2 until 8th , characterized in that the valve elements (42) and / or the valve seats (41) are each formed from the same material, preferably from a light metal, plastic, composite material or the like. Control valve according to one of claims 2 until 9 , characterized in that the valve elements (42), in particular each, is assigned an electric actuator, by means of which an actuating movement of the valve elements (42) can be controlled independently of one another and a controller (25) is provided, which controls the actuator as a function of a control parameter , in particular a temperature value and/or a volume flow value. control valve claim 10 , characterized in that the actuator can be controlled by the controller (25) in such a way that the valve element (42) moves between the open position (49) and the closed position (48) or an intermediate position (51) in between, or between the open position ( 49) and the closed position (48) is adjustable. Control valve according to one of the preceding claims, characterized in that the valve housing (31) is essentially cuboid. Control valve according to one of the preceding claims, characterized in that the inlet openings (32, 33) and the outlet opening (34) are arranged in relation to the fluid space (29) such that during operation the main flow direction of the coolant flowing into the fluid space (29) is perpendicular to is aligned with the main direction of flow of the coolant flowing out of the fluid space (29).

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