WO2008087045A1

WO2008087045A1 - Valve device for a heat exchanger

Info

Publication number: WO2008087045A1
Application number: PCT/EP2008/000407
Authority: WO
Inventors: Hans-Peter Klein; Torsten-Andre Kunz
Original assignee: Behr Thermot-Tronik Gmbh
Priority date: 2007-01-19
Filing date: 2008-01-21
Publication date: 2008-07-24

Abstract

The invention relates to a valve device for a heat exchanger for controlling a fluid flow, in particular an exhaust gas flow or charge air flow, provided with a valve housing (2) comprising an inlet (4) for the fluid flow and a heat exchanger outlet (11), through which a larger or smaller liquid flow is guided to the heat exchanger, in particular a cooling agent, in accordance with the position of the valve body. The aim of the invention is to improve the valve device for a heat exchanger, in that is has a simple structure and is economical to produce. The valve housing (2) comprises an additional outlet, in particular a bypass outlet (12), through which a larger or smaller liquid flow is guided past the heat exchanger, in accordance with the position of the valve slide (16) which is arranged in the valve housing (2) that can be displaced back and forth between two open positions, from its rest position, in which a fluid flow channel is closed by the valve body.

Description

heat-exchanger

The invention relates to a heat exchanger valve device for regulating a fluid flow, in particular an exhaust or charge air flow, with a valve housing having an inlet for the fluid flow and a heat exchanger output, through which a heat exchanger, in particular a radiator, depending on the position of a valve body one more or less large fluid flow is supplied.

In conventional exhaust systems, an exhaust gas control valve is used to regulate the exhaust gas flow. For distributing the exhaust gas, an exhaust valve is used, which directs the exhaust gas flow either through the radiator or through a bypass on the radiator.

The object of the invention is to provide an improved heat exchanger valve device according to the preamble of claim 1, which is simple in construction and inexpensive to produce.

The object is with a heat exchanger valve device for regulating a fluid flow, in particular an exhaust gas or charge air flow, with a valve housing having an inlet for the fluid flow and a heat exchanger outlet through which a heat exchanger, in particular a cooler, in dependence on the position of Valve body more or less large fluid flow is supplied, achieved in that the valve housing has a further output, in particular a bypass outlet, through which, depending on the position of a valve spool, which closed out of a zero position in which a fluid flow passage through the valve spool is arranged between two open positions movable back and forth in the valve housing, a more or less large fluid flow is passed to the heat exchanger over. According to one essential aspect of the invention, the functions of regulating and distributing the fluid flow are combined in a single valve device. With the heat exchanger valve device according to the invention, it is possible to control the fluid flow entering through the inlet into the valve housing in a regulated manner to the heat exchanger outlet or to the bypass outlet. According to a further aspect of the invention, the input with the valve spool can also be completely closed. The valve spool can also be referred to as a valve body. The valve spool is actuated by electric actuators, in particular electromagnetic actuators, or by pneumatic actuators, in particular by at least one vacuum unit. The conventional exhaust valve can be omitted.

A preferred embodiment of the heat exchanger valve device is characterized in that the valve slide between a first extreme position in which the further output is closed and the heat exchanger outlet is open, and a second extreme position is movable back and forth, in which the further output is opened and the heat exchanger output is closed , By the valve spool, a sufficient tightness can be ensured even at high pressures.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the further output and the heat exchanger outlet are closed in a further valve division of the valve slide.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that in a further valve position the valve spool the other output and the heat exchanger output are partially open.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that in a further valve position of the valve slide the further outlet and the heat exchanger outlet are opened.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that, in a further valve position of the valve slide, the further outlet is in particular partially opened and the heat exchanger outlet is closed.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that, in a further valve position of the valve slide, the heat transfer output is in particular partially opened and the further output is closed.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the valve slide comprises a substantially circular-cylindrical closing body with a lateral surface which extends between two end faces. The closing body is received in a recess of the valve housing to and fro.

A further preferred embodiment of the heat exchanger valve device is characterized in that the closing body has a central through hole. The central through hole serves to pass through a piston rod, by means of which the closing body is coupled to a drive device.

Another preferred embodiment of the heat exchanger valve device is characterized in that the closing body has at least one end face a plurality of projections. The projections cken in the direction of movement of the closing body and serve to guide the closing body in the valve housing.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the closing body has a plurality of projections on both end faces. As a result, a stable guidance of the closing body in the valve housing is ensured even in the extreme positions of the reciprocating motion of the closing body.

A further preferred embodiment of the heat exchanger valve device is characterized in that the transitions between the lateral surface and the end faces of the closing body have at least one phase. Preferably, a phase is provided at both transitions. The phases may be performed circumferentially or interrupted, that is divided into segments.

A further preferred embodiment of the heat exchanger valve device is characterized in that the transitions between the lateral surface and the end faces have at least one rounding. Preferably, a rounding is provided at both transitions. The curves can be performed circumferentially or interrupted, that is divided into segments.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the rounding extends in a circular arc or elliptical or elliptical arc shape. The rounding creates a gentle and / or tangential transition between the lateral surface and the associated end face.

A further preferred embodiment of the heat exchanger valve device is characterized in that the transitions between the lateral surface and the end faces have at least one recess, preferably a plurality of depressions, which connects the lateral surface with the associated end face. The depression forms a notch or groove and creates a flow connection between the lateral surface and the associated end face.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the recess has an angular, in particular triangular, rectangular or trapezoidal, cross-section.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the depression has a round, in particular circular-arc-shaped or elliptical or elliptical arc-shaped, cross-section.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the recess has the shape of a straight line in a longitudinal section which rises obliquely in relation to the lateral surface.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the recess extends in a circular arc or elliptical or elliptical arc shape in longitudinal section.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that a plurality of depressions are arranged distributed in the circumferential direction, in particular uniformly. The distribution of the depressions is preferably symmetrical.

A further preferred embodiment of the heat exchanger valve device is characterized in that a transition between an inner surface and a side surface of the valve housing is designed as a control transition. The control transition allows a defined passage of fluid when the valve spool is moved from a zero position to one of the open positions. A further preferred embodiment of the heat exchanger valve device is characterized in that the control transition has a control edge for the valve slide.

A further preferred embodiment of the heat exchanger valve device is characterized in that the control transition has a phase. The inner edge of the phase forms the control edge.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the control transition has at least one rounding. The rounding can be performed circumferentially or interrupted, that is divided into segments.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the rounding extends in a circular arc or elliptical or elliptical arc shape.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the control transition has at least one depression, preferably a plurality of depressions, which connects the inner surface to the side surface. The recess forms a notch or groove and creates a flow connection between the inner surface and the side surface.

A further preferred embodiment of the heat exchanger valve device is characterized in that the recess has a polygonal, in particular triangular, rectangular or trapezoidal, cross-section.

A further preferred embodiment of the heat exchanger valve device is characterized in that the recess has a round, in particular circular arc-shaped or elliptical or elliptical arc-shaped, cross-section. A further preferred embodiment of the heat exchanger valve device is characterized in that the recess has in the longitudinal section the shape of a straight line which slopes away from the side surface obliquely to the inner surface.

A further preferred embodiment of the heat exchanger valve device is characterized in that the recess extends in a circular arc or elliptical or elliptical arc shape in longitudinal section.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the heat exchanger valve device has a stroke flow curve with a linear, progressive or sigmoidal profile.

A further preferred embodiment of the heat exchanger valve device is characterized in that the valve slide or valve piston is biased between two spring elements in a zero position in which the input is closed. If the valve spool, which is also referred to as a valve piston, is in its zero position, then the connection between the input and the outputs is interrupted by the closing body. The spring elements enable a fail-safe function.

A further preferred embodiment of the heat exchanger valve device is characterized in that the closing body is held by a symmetrically biased spring in the zero position, in which the input is closed. A further preferred embodiment of the heat exchanger valve device is characterized in that the closing body is guided by two bearing rings. The bearing rings are preferably formed of ceramic and fixed in each case between a shoulder in the valve housing and a retaining ring in the axial direction.

Another preferred embodiment of the heat exchanger valve device is characterized in that the valve slide is partially formed of ceramic. Stainless steel can also be used instead of ceramics. The valve spool may be partially or completely formed of stainless steel.

Another preferred embodiment of the heat exchanger valve device is characterized in that the valve housing is partially formed of ceramic. Preferably, the tread for the valve spool is formed of ceramic.

A further preferred embodiment of the heat exchanger valve device is characterized in that the valve slide is equipped with a sealing element for the input. Preferably, the entrance is equipped with a sealing seat for the sealing element.

A further preferred embodiment of the heat exchanger valve device is characterized in that the sealing element has a sealing surface facing the inlet, which has the shape of a spherical segment. By using a large diameter ball section, it is easier to move the valve spool.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the sealing element is guided to be movable back and forth on the valve slide. As a result, the closing of the entrance with the sealing element, which is also referred to as a closing element, simplified. A further preferred embodiment of the heat exchanger valve device is characterized in that the sealing element is biased by a spring device against the input. This allows a tight closure of the input.

Another preferred embodiment of the heat exchanger valve device is characterized in that the valve slide has a pressure equalization channel. As a result, the displacement of the valve spool in the valve housing is facilitated.

In a method for cleaning a heat exchanger valve device described above, the above-described object is achieved in that the valve slide is moved from an initial position once or several times back and forth. By the method of the valve spool deposited particles or deposited condensate are scraped off or peeled off. This ensures proper operation of the vehicle during operation. This cleaning procedure can also be used during or after engine shutdown.

A preferred embodiment of the method is characterized in that the position of the valve spool is detected by means of a sensor device. Possible contamination of the valve slide is preferably detected by a deviation of a sensor signal of the bearing feedback of a drive device of the valve slide detected by the sensor device.

A further preferred exemplary embodiment of the method is characterized in that a sensor signal detected by the sensor device is compared with a reference signal. The reference signal is preferably an electrical drive signal of the drive device of the valve slide.

The invention also relates to an exhaust gas recirculation system on or with an internal combustion engine, in particular an engine, which branches off at a point of removal and returns via a return point. guided exhaust gas is supplied. The object specified above is achieved in the exhaust gas recirculation system in that a previously described heat exchanger valve device is connected between the removal point and the return point.

A preferred embodiment of the exhaust gas recirculation system is characterized in that the heat exchanger valve device is connected to an exhaust gas cooling device. The exhaust gas cooling device serves to lower the temperature of the recirculated exhaust gas. The Wärmeübertrager- valve device may be cohesively or mechanically connected to the exhaust gas cooling device.

A further preferred exemplary embodiment of the exhaust gas recirculation system is characterized in that the heat exchanger valve device is integrated in the exhaust gas cooling device. It is advantageous, for example, if the housing or the downstream side of the heat exchanger valve device directly forms the inlet or outlet diffuser of the exhaust gas cooling device.

A further preferred embodiment of the exhaust gas recirculation system is characterized in that the heat exchanger valve device is materially connected to the exhaust gas cooling device. Alternatively, the heat transfer valve device may be mechanically, e.g. be connected by screws, positive locking, etc., with the exhaust gas cooling device.

A further preferred exemplary embodiment of the exhaust gas recirculation system is characterized in that the heat exchanger valve device has a bypass as a further outlet. The bypass serves, for example during a cold start of the engine, to pass the recirculated exhaust gas uncooled past the exhaust gas cooling device.

A further preferred exemplary embodiment of the exhaust gas recirculation system is characterized in that the exhaust gas cooling device has a U-flow

Cooler includes. The U-flow cooler is connected to the heat exchanger valve device in such a way that the recirculated exhaust gas is not exposed cools past the radiator can be passed through the heat exchanger valve device. On the other hand, the recirculated exhaust gas can be passed through the U-flow cooler by means of the heat transfer valve device and thus returned cooled. The U-Flow cooler has the advantage that a bypass can be omitted.

A further preferred exemplary embodiment of the exhaust gas recirculation system is characterized in that the heat exchanger valve device, viewed in the flow direction from the removal point to the return point, is arranged upstream or downstream of the exhaust gas cooling device. The heat exchanger valve device can therefore be arranged both in front of and behind the exhaust gas cooling device.

A further preferred exemplary embodiment of the exhaust gas recirculation system is characterized in that the heat exchanger valve device comprises a high-temperature exhaust gas cooler and a low-temperature exhaust gas cooler. Depending on the application, the two-stage cooling may be advantageous.

A further preferred embodiment of the exhaust gas recirculation system is characterized in that the heat transfer valve device, viewed in the flow direction from the extraction point to the return point upstream or downstream of the high-temperature exhaust gas cooler or the low-temperature exhaust gas cooler is arranged. The heat exchanger valve device can thus be arranged in front of or behind the high-temperature exhaust gas cooler or low-temperature exhaust gas cooler. However, the heat exchanger valve device can also be arranged between the high-temperature exhaust gas cooler and the low-temperature exhaust gas cooler.

A further preferred exemplary embodiment of the exhaust gas recirculation system is characterized in that the exhaust gas recirculation system is formed by a high-pressure exhaust gas recirculation system. The high-pressure exhaust gas recirculation system can be equipped with one-stage or two-stage cooling. A further preferred exemplary embodiment of the exhaust gas recirculation system is characterized in that the exhaust gas recirculation system is formed by a low-pressure exhaust gas recirculation system. The low-pressure exhaust gas recirculation system can be equipped with one-stage or two-stage cooling.

In a further embodiment, in the method for cleaning, in particular the heat transfer valve device, the heat exchanger outlet and the bypass outlet are closed. In particular, during the cleaning process, no medium, in particular no exhaust gas or no charge air, can be supplied to the heat exchanger through the heat exchanger outlet and to the bypass via the bypass outlet.

In a further embodiment, in the method for cleaning, in particular the heat transfer valve device, the heat exchanger outlet or the bypass outlet are closed. In particular, during the cleaning process, no medium, in particular no exhaust gas or no charge air, can be supplied to the heat exchanger through the heat exchanger outlet or to the bypass via the bypass outlet.

In a further embodiment, in the method for cleaning, in particular the heat transfer valve device, the method for cleaning starts as soon as a detected sensor signal of a sensor device, in particular for measuring a frictional resistance of a frictional resistance between at least one closing body and at least one housing guide section coincides with a reference signal , In particular, if the sensor signal exceeds the reference signal and / or falls within or coincides with this, the method for cleaning can be started. In particular, if the sensor signal exceeds and / or undershoots a second, different reference signal, the method for cleaning can be ended.

The invention also relates to a heat exchanger, in particular an exhaust gas heat exchanger, with a previously described Wärmeübertragerventi- leinrichtung. Further advantages, features and details of the invention will become apparent from the following description in which, with reference to the drawings, an embodiment is described in detail. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination. Show it:

1 shows a high-pressure exhaust gas recirculation system with a single-stage cooling, which includes a bypass.

FIG. 2 shows a high-pressure exhaust gas recirculation system with one-stage cooling with a U-flow cooler;

FIG. 3 shows a high-pressure exhaust gas recirculation system with a two-stage cooling;

FIG. 4 shows a low-pressure exhaust gas recirculation system with a one-stage cooling, which comprises a bypass;

FIG. 5 shows a low-pressure exhaust gas recirculation system with one-stage cooling with a U-flow cooler;

Figure 6 is a low-pressure exhaust gas recirculation system with a two-stage

Cooling;

FIG. 7 shows a heat exchanger valve device according to the invention in FIG

Longitudinal section;

Figure 8 is a sectional view taken along the line M-II in Figure 1;

9 shows a heat exchanger valve device according to a further embodiment in longitudinal section;

FIG. 10 shows a heat exchanger valve device according to a further exemplary embodiment in longitudinal section through the valve slide; 11 shows a closing body of the valve slide of the heat exchanger valve device from FIG. 10 according to a first exemplary embodiment;

Figure 12 is a side view of the closing body of Figure 11;

Figure 13 shows a similar closing body as in Figure 11 according to a further embodiment;

Figure 14 is a side view of the closing body of Figure 13;

Figure 15 shows a similar closing body as in Figures 11 and 13 according to a further embodiment;

Figure 16 is a side view of the closing body of Figure 15;

17 shows a heat exchanger valve device according to a further embodiment in a longitudinal section through the valve slide;

FIG. 18 shows a heat exchanger valve device according to a further exemplary embodiment in a longitudinal section through the valve slide;

19 shows a heat exchanger valve device according to another

Embodiment in longitudinal section through the valve spool;

FIG. 20 shows a closing body of the valve slide of the heat exchanger valve device from FIG. 19 according to an embodiment with one phase;

Figure 21 is a side view of the closing body of Figure 20;

FIG. 22 shows a closing body of the valve slide of the heat exchanger valve device from FIG. 19 according to an embodiment with circular-arc-shaped rounded transitions; Figure 23 is a side view of the closing body of Figure 22;

FIG. 24 shows a closing body of the valve slide of the heat exchanger valve device from FIG. 19 according to an embodiment with elliptically rounded transitions;

Figure 25 is a side view of the closing body of Figure 24;

FIG. 26 shows a closing body of the valve slide of the heat exchanger valve device from FIG. 19 according to an embodiment with depressions;

Figure 27 is a side view of the closing body of Figure 26;

Figures different cross-sections of wells; 28 to 33

Figures different longitudinal sections of wells; 34 to 36

FIG. 37 shows a valve housing section with a phase in longitudinal section;

FIG. 38 shows the valve housing section from FIG. 37 in a side view;

FIG. 39 shows a valve housing section with recesses in longitudinal section;

Figure 40 shows the valve housing portion of Figure 39 in cross section and

Figures different stroke-flow curves, which can be displayed with the erfindungsge- 41 to 44-dimensional heat exchanger valve device.

Various embodiments of a high-pressure exhaust gas recirculation system are shown in simplified form in FIGS. 1 to 3. Identical parts are provided with the same reference numerals. The performance of an internal combustion engine depends on displacement, speed and average gas pressure. By a When filling the engine, the filling can be considerably improved and the engine output can be increased. The fuel-air mixture or the air is completely or partially pre-compressed outside the cylinder. In an engine with an exhaust gas turbocharger, the exhaust gases drive the turbine and these drive the compressor. The compressor takes over the intake and delivers a pre-compressed fresh gas charge to the engine. An intercooler in the charging line dissipates the heat of compression to the ambient air. As a result, the cylinder filling is further improved.

The exhaust gas recirculation serves to cool the exhaust gas as far as possible. The recirculated exhaust gas no longer takes part in the combustion in the internal combustion engine, but heats up. Overall, the temperature in the internal combustion engine or the engine is lowered by the recirculated exhaust gas. Low temperatures in the engine can reduce the formation of nitrogen oxides, which is heavily dependent on the temperature in the engine.

The fuel-air mixture is sucked in via an air filter 101 from a compressor 102 and fed to a motor 104. From the engine 104, the exhaust gas reaches a turbine 106 which drives the compressor 102. Between the engine 104 and the turbine 106, which is also referred to as a turbocharger turbine, a removal point 108 is provided which communicates with a return point 109. About the return point 109, the exhaust gas is supplied to the motor 104 again. Between the removal point 108 and the return point 109, a heat transfer valve 111 according to the invention, which is also referred to as a combination valve, is arranged. The combination valve 111 communicates with an exhaust gas cooler 112, which includes a bypass. This bypass is made in one piece with the radiator housing. In another embodiment, not shown, the bypass is in particular a separate pipeline which bypasses the radiator. Between the compressor 102 and the return point 109, a charge air cooler 114 is connected.

The high-pressure exhaust gas recirculation systems illustrated in FIGS. 2 and 3 are similar to the exhaust gas recirculation system illustrated in FIG. To name like parts, like reference numerals are used. To avoid repetition, reference is made to the preceding description of FIG. In the following, only the differences between the individual embodiments will be discussed.

In the high-pressure exhaust gas recirculation system shown in FIG. 2, a heat transfer valve 121 according to the invention is connected between the removal point 108 and the return point 109, which is also referred to as a combination valve. The combination valve 121 is in communication with a U-flow cooler. Depending on the switching position of the combination valve 121, the recirculated exhaust gas passes either directly through the combination valve 121 uncooled from the sampling point 108 to the return point 109, or the recirculated exhaust gas is passed by means of the combination valve in the U-flow cooler 122, in the U-flow cooler 122 cooled and then passes to the return point 109th

In the high-pressure exhaust gas recirculation system illustrated in FIG. 3, a combination valve 131 having a two-stage cooling device, which comprises a high-temperature exhaust gas cooler 132 and a low-temperature exhaust gas cooler 133, is arranged between the removal point 108 and the return point 109.

In the figures 4 to 6 various embodiments of a low-pressure exhaust gas recirculation system are shown simplified. The fuel-air mixture is sucked in via an air filter 101 from a compressor 102 and fed to a motor 104. The exhaust of the engine 104 is expanded in a turbine 106 which drives the compressor 102. Downstream of the turbine 106, a removal point 108 is arranged, which communicates with a return point 109. The return point 109 is located upstream of the compressor 102. Between the compressor 102 and the engine 104, a charge air cooler 114 is connected. Between the turbine 106 and the removal point 108, a diesel particulate filter 140 is connected with Oxidationskatalysa- tor. Between the removal point 108 and the return point 109, a heat transfer valve 141, which is also referred to as a combination valve, connected. The combination valve 141 is connected to an exhaust gas 142, which is equipped with a bypass. Between the exhaust gas cooler 142 and the return point 109, a Kondensatabscheider 144 is connected. In the flow direction following the removal point 108, an exhaust gas back pressure valve 145 is arranged. Between the return point 109 and the air filter 101, a charge air throttle 147 is connected.

FIGS. 5 and 6 show similar low-pressure exhaust gas recirculation systems as shown in FIG. To designate the same parts, the same reference numerals are used. To avoid repetition, reference is made to the previous description of FIG. 4. In the following, only the differences between the individual embodiments will be discussed.

In the exemplary embodiment illustrated in FIG. 5, a heat transfer valve 151, which is also referred to as a combination valve, is connected between the removal parts 108 and the return point 109. The combination valve 151 is in communication with a U-flow cooler 152. Depending on the switching position of the combination valve 151, the recirculated exhaust gas passes either uncooled from the take-off point 108 to the return point 109 through the combination valve 151, or the recirculated exhaust gas is conducted by means of the combination valve into the U-flow cooler 152, in the U-flow Cooler 152 cooled and then passes first to the return point 109th

In the exemplary embodiment illustrated in FIG. 6, a combination valve 161 with a two-stage cooling device, which comprises a high-temperature exhaust gas cooler 162 and a low-temperature exhaust gas cooler 163, is arranged between the removal parts 108 and the return point 109.

In FIGS. 7 and 8, a heat exchanger valve device 1 according to the invention is shown in different views. The heat exchanger valve device 1 comprises a housing 2 with an inlet 4 for a fluid. The fluid is preferably exhaust gas or charge air. The inlet 4 is formed by an inlet connection 5, which essentially has the shape of a circular cylinder jacket, which is integral with the housing. housing 2, which is also referred to as a valve housing, is connected and comprises a circular inlet opening 6.

Furthermore, the valve housing 2 has a radiator outlet opening 10 in a radiator outlet 11, which communicates with a radiator (not shown). In addition, the valve housing 2 has a bypass outlet 12 which communicates with a bypass line (not shown) via which fluid is led past the radiator. The radiator outlet 11 is formed by a radiator outlet 13, which is formed integrally with the valve housing 2 and widens outwardly in a funnel shape. The bypass outlet 12 is formed by a Bypassaustrittsstut- zen 14 which is integrally formed with the valve housing 2 and a bypass outlet opening 15 has. The respective cross sections of the lines are the same size. This leads to a smaller adjustment, since the exit area can be smaller in diameter. Preferably, the adjustment paths are the same. The result is that the outlet has a diameter twice as large as the inlet and thus has four times the area.

In the valve housing 2, a valve spool 16 is guided back and forth movable. The valve spool 16 has a valve spool rod 18 at one end of which a closing body 20 is formed. In the closing body 20, a pressure compensation bore 22 is provided which allows pressure equalization when the closing body 20 is moved in the valve housing 2 in the direction of a double arrow 23 back and forth. On the closing body 20, a sealing element 24, which comprises a sealing sleeve 25, guided perpendicular to the double arrow 23 back and forth. On its side facing away from the closing body 20, the sealing element 24 has a sealing surface 26, through which the inlet opening 6 of the inlet 4 for the fluid is closed. The sealing sleeve 25 is guided in an annular space 28, which is recessed in the Schiießkör- by 20, moved back and forth. The annular space 28 is bounded radially inwardly by a substantially circular cylindrical projection 29. The end face of the projection 29 facing the inlet 4 forms a stop for the sealing element 24. In addition, a helical compression spring 30 is provided in the annular space 28, through which the sealing element 24 is biased with its sealing surface 26 against the inlet opening 6 of the inlet 4 for the fluid.

The valve housing 2 is closed by a valve housing cover 32, which has a guide stub 34. Through the guide sleeve 34, the valve spool rod 18 extends out of the valve housing 2 to the outside. About the valve spool rod 18, the closing body 20 can be moved in the valve housing 2 in the direction of the double arrow 23 back and forth.

In the position of the closing body 20 shown in FIG. 7, the inlet opening 6 is closed by the sealing surface 26 of the sealing element 24. The radiator outlet opening 10 and the bypass outlet opening 15 are closed by the closing body 20. When the closing body 20 is moved towards the valve housing cover 32, then both the inlet opening 6 and the radiator outlet opening 10 are opened, so that fluid from the inlet 5 to the radiator outlet 11 passes. The size of the passage cross section for the fluid depends on the position of the closing body 20 in the valve housing 2. When the closing body 20 is moved away from the valve housing cover 32 from the position shown in FIG. 1, both the inlet opening 6 and the bypass outlet opening 15 are opened.

By means of the heat exchanger valve device according to the invention, the distribution and regulation of fluid flows, in particular of exhaust gas flows or charge air flows, with high tightness is ensured in a simple manner. The heat exchanger valve device according to the invention has the advantage that only one actuator is needed. In addition, the heat exchanger valve device according to the invention has inexpensive to produce components that are less susceptible to contamination. The closing body is preferably made of ceramic and preferably runs in a precise fit in order to keep the adjusting force of the actuator as small as possible. The environment, which represents the running surface for the sealing element or the closing body, may also be formed of ceramic. Stainless steel can also be used instead of ceramic. The closing body has provided over the area of the sealing of the inlet opening. For example, a straight shape. The region which lies in the exhaust gas stream after the start of the displacement preferably has a shape which allows a gradual connection of the exhaust gas flow into the corresponding branch, for example the shape of a ball, which initially makes it possible to generate a high pressure loss For example, to achieve a low return rate is necessary.

The helical compression spring 30 is preferably dimensioned such that the inlet counterpressure is overcome by the spring force and the valve device closes tightly even under these conditions. Instead of the helical compression spring and a bellows can be used which has a similar spring characteristic as the spring. Such a bellows has advantageously for pressure relief, for example in the middle, an opening. To ensure a constant cross-section in the flow, it may be advantageous that the annular inlet into the heat exchanger only has a diameter larger by a factor of 1.41 than the entrance from the exhaust side to divide the flow between the bypass and the radiator. This space can be saved.

FIG. 9 shows a longitudinal section of a heat exchanger valve device according to a further exemplary embodiment. The heat exchanger valve device shown in FIG. 9 is similar to the heat exchanger valve device shown in FIG. To designate the same parts, the same reference numerals are used. To avoid repetition, reference is made to the preceding description of FIG. In the following, only the differences between the two embodiments will be discussed.

In the embodiment shown in Figure 9, a bellows 41 is used as a sealing element. The bellows 41 has an end 43 which is welded to the closing body 20 over the entire circumference of the bellows. The other end 45 of the bellows 41 abuts against the circular inlet opening 6. The use of the bellows 41 provides the advantage that the bellows 41, which is open at one end, is pressurized on the inside. As a result, the spring load can be lower. FIG. 10 shows a heat exchanger valve device 51 according to a further exemplary embodiment. The heat transfer valve device 51 comprises a housing 52 with an inlet 54 for a fluid. The fluid is preferably exhaust gas or charge air. The inlet 54 is formed by an inlet port 55, which has substantially the shape of a circular cylinder jacket, which is integrally connected to the housing 52, which is also referred to as a valve housing, and comprises a circular inlet opening 56. The inlet opening 56 opposite is recessed in the valve housing 52 has a recess 58, whose function will be explained later.

Furthermore, the valve housing 52 has a radiator outlet opening 60 in a radiator outlet 61 which communicates with a radiator (not shown). In addition, the valve housing 52 has a bypass port 62 which communicates with a bypass line (not shown) via which fluid is conducted past the radiator. The radiator outlet 61 is formed by a radiator outlet port 63, which is integrally connected to the valve housing 52. The bypass outlet 62 is formed by a bypass outlet connection piece 64, which likewise is connected in one piece with the valve housing 52 and has a bypass outlet opening 65. The respective cross sections of the lines are the same size.

In the valve housing 52, a valve spool 66 is guided back and forth. The valve spool 66 comprises a valve spool rod 68, at one end of which a closing body 70 is fastened. By the inlet opening 56 opposite recess 58 in the valve housing 52 ensures that the closing body 70 is completely surrounded in the circumferential direction of the medium present in the inlet 54. By a double arrow 69, the reciprocating motion of the closing body 70 is indicated, which is transmitted via the valve slide rod 68, which can also be referred to as a piston rod, by a drive device (not shown) onto the closing body 70, which is also referred to as a piston becomes. Depending on the position of the closing body 70, the input 54 can be connected to the radiator outlet 61 or the bypass outlet 62. In the in 10 illustrated position of the closing body 70 is no connection between the input 54 and the outputs 61, 62nd

In FIGS. 11 and 12, the closing body 70 is shown in different views. The closing body 70 comprises a main body 71, which the

Has the shape of a straight circular cylinder. At its front ends is the

Base body 71 each provided with a circumferential rounding 73, 74.

In addition, the main body 71 has a central through hole 75. At the ends of the through hole 75, a chamfer 76, 77 is provided in each case.

FIGS. 13 and 14 show a closing body 80 according to a further exemplary embodiment in different views. The closing body 80 comprises a main body 81, which has the shape of a straight circular cylinder. An end face of the main body 81 is provided with a circumferential rounding 83. The rounding 83 has the shape of an elliptical arc in cross section. In the main body 81, a central through hole 85 is recessed. The ends of the through hole 85 are each provided with a chamfer 86, 87. At the end of the through hole 85 with the chamfer 87 two projections 88, 89 are formed on the associated end face of the base body 81, which extend in the axial direction of the base body 81. The projections 88, 89 are bounded radially inwardly and radially outwardly by circular arcs. The radially outer arc of the projections 88, 89 has the same radius as the base body 81. The projections 88, 89 serve to improve the guidance of the closing body 80 in the valve housing.

FIGS. 15 and 16 show a closing body 90 according to a further exemplary embodiment in different views. The closing body 90 comprises a base body 91, which has the shape of a straight circular cylinder. In the main body 91, a central through-hole 95 is recessed, which has a respective chamfer 96, 97 at the ends. At both end sides of the base body 91 are each three projections 201, 202, 203; 204, 205 formed. The protrusions 201 to 205 have the same shape as the protrusions 88, 89 in the embodiment shown in FIG. For example, and also serve to better guide the closing body 90 in the valve housing. The projections 201 to 203 and 204 to 205 are arranged distributed uniformly over the circumference of the closing body 90 at its end faces.

The accumulated under the given operating conditions of an exhaust gas recirculation system particle and Kondensatablagerungen the valve spool of the heat exchanger valve device, the function of the heat exchanger valve device, which is referred to as a valve, influence. According to an essential aspect of the invention, in a motor vehicle operated with a diesel combustion method, a cleaning process or a cleaning mechanism is carried out before the engine is put into operation or in the pre-glow phase. In a vehicle operated according to the Otto combustion method, this cleaning method or this cleaning mechanism should also take place before the engine is put into operation, for example when the fuel pump and / or other auxiliary units are put into operation. Here, the actuator of the heat exchanger valve device, in particular the valve spool with the closing body, once or several times to be moved back and forth and then back to the starting position in which the valve is closed, return. By this method of the actuator deposited particles or deposited condensate are scraped off or peeled off. This ensures proper operation of the vehicle during operation. The cleaning mechanism or the cleaning method may or may also take place during or after the engine has been switched off.

In particularly designed actuators that allow movement of the actuator without opening the valve seat, that is, without permitting a gas flow, such as in a previously described valve spool, the cleaning mechanism or the cleaning process can also take place during operation of the motor of the shape that at Engine operating conditions in which there is no exhaust gas recirculation, the actuator moves back and forth so that the valve still remains closed. The initiation of the cleaning mechanism preferably takes the form that a possible contamination is detected by a deviation of a sensor signal of the bearing feedback of a drive device of the heat exchanger valve device for a given electrical drive signal from a stored sensor signal at selbigem drive signal. Depending on the operating state of the vehicle, one of the two previously described cleaning mechanisms or cleaning processes is carried out.

In both cleaning mechanisms or cleaning method, a repetitive deflection of the closing body from the zero position or initial position in one and then beyond the zero position out in the other direction a cleaning is achieved. The deflection path depends on vehicle-specific aspects, in particular the design of the exhaust gas recirculation. Depending on the size of the closing body, the deflection path is only a certain percentage of the maximum possible deflection. In the former cleaning mechanism, however, it is essential that the closing body, which is also referred to as a piston, at least partially releases one or the other opening. In the second cleaning method or cleaning mechanism described above, it is essential that the valve piston or valve closing body always keeps the two openings closed.

The adjustment speed during cleaning can be slower, faster or the same speed as the adjustment speed of the closing body under normal conditions. It is crucial that the electric drive of the closing body can briefly apply a higher adjustment than under normal conditions to overcome caused by the pollution, possible higher friction or resistance forces.

FIG. 17 shows a heat exchanger valve device 211 according to a further exemplary embodiment. The heat transfer valve device 211 comprises a housing 212 with an inlet 214 ^' for a fluid. The fluid is preferably exhaust gas or charge air. The inlet 214 is formed by an inlet nozzle 215, which is essentially the Has a shape of a circular cylinder jacket, which is integrally connected to the housing 212, which is also referred to as a valve housing, and an inlet opening 216 comprises. At the inlet opening 216, the inlet 214 opens into an annular space 218.

Furthermore, the valve housing 212 has a radiator outlet opening 220 in a radiator outlet 221 which communicates with a radiator (not shown). In addition, the valve housing 212 has a bypass outlet 222, which communicates with a bypass line (not shown), via which fluid is conducted past the cooler. The radiator outlet 221 is formed by a radiator outlet 223, which is integrally connected to the valve housing 212. The bypass outlet 222 is formed by a bypass outlet port 224, which is also integrally connected to the valve housing 212 and has a bypass exit opening 225. The radiator outlet 221 has a larger cross section than the bypass outlet 222 on the outside.

In the valve housing 212, a valve piston or valve slide 226 is guided to and fro movable, as indicated by a double arrow 229. The valve spool 226 includes a valve piston rod 228 at one end of which a closing body 230 is attached. The annular space 218 surrounds the closing body 230. The annular space 218 ensures that the closing body 230 is completely surrounded in the circumferential direction by the medium or fluid present in the inlet 214. The closing body 230 is driven via the valve slide rod or valve piston rod 228 by a drive device (not shown). Depending on the position of the closing body 230, the inlet 214 is connected to the radiator outlet 221 or the bypass outlet 222. In the position of the closing body 230 shown in FIG. 17, there is no connection between the inlet 214 and the exits 221, 222. This position of the closing body 230 is also referred to as zero position.

The closing body 230 has the shape of a straight circular cylinder whose

Each end face is provided with a circumferential rounding. At the end sides of the closing body 230 are each three projections 231, 232; 233 234, which extend in the axial direction of the closing body 230 and of which in FIG. 17 only two projections per end face are visible. The projections 231 to 234 serve to improve the guidance of the closing body 230 in the valve housing 212 when the closing body 230 is moved from the zero position shown in FIG. 17 to the right or to the left. In addition, the projections 231 to 234 allow the passage of medium or fluid from the entrance 214 to the exits 221, 222, when the closing body 230 is moved to the right or left.

Between the right end of the closing body 230 and the valve housing 212, a spring 236 is clamped. One end of the spring 236 abuts against the associated end face of the closing body 230. The other end of the spring 236, which is designed as a helical compression spring, is received in a recess 237 in the housing 212. The other end face, that is, in Figure 17, the left end face of the closing body 230 is acted upon by a further spring 239, which is also designed as a helical compression spring. The helical compression spring 239 is clamped between the closing body 230 and the valve housing 212 or a plain bearing bush 250, the function of which will be explained below. The spring 236 and 239 have the same spring characteristic and cause an equally large but acting in the opposite direction biasing force on the closing body 230. By the biasing forces of the springs 236, 239 of the closing body 230 is biased to its zero position shown in FIG. This bias to the zero position ensures a fail-safe function. For example, if the drive via the valve spool 226 fails, then it is ensured by the bias caused by the springs 236, 239 that the closing body 230 closes the input 214.

The valve housing 212 is closed by a housing cover 241 in the region of the valve piston rod or valve slide rod 228. Between the housing cover 241 and the valve housing 212, a seal 242 is clamped. The housing cover 241 is fastened to the valve housing 212 by means of screws 243, 244. In addition, the housing cover 241 has a bearing neck 248 through which the valve spool rod 228 extends. The valve spool rod 228 is using the Plain bearing bush 250 stored in the bearing neck 248. The plain bearing bushing 250 allows the valve spool rod 228 to reciprocate with the closure body 230 in the valve housing 212, as indicated by the double arrow 229. The interior of the housing 212 is sealed by a sealing ring 252, which surrounds the valve slide rod 228 at the end of the bearing neck 248.

The closure member 230 is slidably mounted in two bearing rings 261, 262 made of ceramic in the axial direction. The bearing ring 261 is fixed in the axial direction between a shoulder 264 and a retaining ring 265, which is designed as a snap ring. The bearing rings 261, 262 each have a rectangular cross-section. The locking ring 265 also has a rectangular cross-section. The bearing ring 262 is fixed in the axial direction between a shoulder 267 and a retaining ring 268, which is designed as a snap ring and has a circular cross-section.

FIG. 18 shows a heat exchanger valve device 300 according to a further exemplary embodiment. Identical features are denoted by the same reference numerals as in the previous figures. In particular, in contrast to FIG. 17, the heat exchanger valve device 300 has at least one spring 303, which is designed as a helical compression spring and / or helical tension spring. The valve piston or the valve rod 301 is formed substantially like the valve piston or valve rod 226. The heat transfer valve device 300 comprises a closing body 302, which is formed substantially like the closing body 230. On the valve piston rod 228 at least one cleaning sleeve is arranged for cleaning and / or lubrication of the piston rod 228. The housing 212 is formed in particular as a cast housing.

FIGS. 10, 17 and 18

The valve spool 66, 226, 301 is formed as a solid body or at least partially as a hollow body.

In FIGS. 1-18, in another embodiment, the heat transfer valve device, in particular the housing 2, 52, 212 and / or the valve spool 16, 66, 226 and / or in particular the closing body of a metal and / or of a sintered material such as ceramic and / or magnesium and / or aluminum and / or steel, such as stainless steel, and / or of a plastic, in particular a synthetic material whose melting temperature is higher than the temperature of the medium to be cooled, in particular the exhaust gas, the charge air, the oil, etc., and / or formed from a fiber composite material.

The at least one housing 2, 52, 212 is formed for example of at least one sheet and has a material, in particular aluminum or an aluminum alloy, plastic, ceramic or a fiber composite material or steel whose melting temperature above, in particular well above, the temperature of the cooled Medium such as exhaust gas, charge air, oil, coolant, etc. is located. The at least one housing 2, 52, 212 is provided with at least one coolant channel, in particular with two, three or more than three coolant channels in which coolant such as a water-containing fluid and / or a gas such as air or CO 2 flows and the at least one housing 2 , 52, 212 cools particularly advantageous, in particular below the melting temperature of the material, in particular aluminum or aluminum alloy, plastic, magnesium, ceramic or fiber composite material or steel, cools, so that the strength properties such as stiffness, tensile and / or compressive strength, fatigue strength, Interchangeability of at least one housing 2, 52, 212 are not degraded by the temperature of the uncooled medium such as exhaust gas, charge air, oil, coolant.

The housing 2, 52, 212 is in this case by means of an original manufacturing process, such as casting, injection molding, etc. and / or by means of a transforming manufacturing process, such as bending, pressing, stamping and / or by means of material bonding, such as welding, soldering, gluing, etc. produced.

The closing body, in particular the piston, has an unspecified piston diameter. Furthermore, the guide section for guiding the closing body, in particular of the piston, has a guide section diameter of the guide opening. The double slit width is the subtraction of the piston diameter from the guide section diameter.

The following values are given in micrometers: The gap width assumes in particular values between 10 μm to 55 μm, in particular between 15 μm to 50 μm, in particular between 20 μm to 40 μm, in particular 30 μm to 35 μm. The gap width in particular assumes values between 5 μm to 55 μm, in particular between 8 μm to 25 μm, in particular between 10 μm to 15 μm.

The at least one helical compression and / or helical tension spring 236, 239, 303, in particular the two or more than two helical compression and / or Schraubenzugfedern 236, 239, 303, close the valve in the de-energized state. The at least one helical compression and / or helical tension spring 236, 239, 303, in particular the two or more helical compression springs and / or helical tension springs 236, 239, 303, are preferably helical springs.

The at least one helical compression and / or helical tension spring 236, 239, 303, in particular the two or more than two Schraubendruck- and / or

Schraubenzugfedern 236, 239, 303, are in the gas space or outside the

Gas space arranged. The at least one screw pressure and / or

Bolt tension spring 236, 239, 303, in particular the two or more than two helical compression and / or Schraubenzugfedern 236, 239, 303, are arranged in another embodiment in the drive unit.

The at least one valve spool 226 is depressurized in the closed position, thus requiring less force to actuate the valve spool than is known in the art. In particular, the size of the drive unit can be reduced and space can advantageously be saved in this way. The drive unit used is at least one DC motor (DC direct current direct current) and in another embodiment a brushless DC motor and / or at least one torque and / or at least one linear drive, in particular at least one linear direct drive and / or at least one lifting magnet. The heat transfer valve device 11, 121, 131, 141, 151, 161, 211, 300 is at least one combination valve, so that in particular the exhaust gas recirculation (exhaust gas recirculation function) of recirculated, cooled or to be cooled medium such as exhaust gas, charge air, coolant, oil, etc. and a Bypass (bypass function) of medium such as exhaust gas, charge air, coolant, oil, etc. around the at least one radiator so that the medium such as exhaust gas, charge air, coolant, oil, etc. is not cooled with the heat transfer valve device 11, 121, 131 , 141, 151, 161, 211, 300 is controlled and / or regulated.

The heat transfer valve device 11, 121, 131, 141, 151, 161, 211, 300 is in another embodiment only an exhaust gas recirculation valve, so that in particular the exhaust gas recirculation (exhaust gas recirculation function) of recirculated, cooled or to be cooled medium such as exhaust gas, charge air, coolant, oil, etc. controlled and / or regulated. The heat exchanger valve device 11, 121, 131, 141, 151, 161, 211, 300 is depressurized in the closed position.

The heat transfer valve device 11, 121, 131, 141, 151, 161, 211, 300 is in another embodiment, only a bypass valve (bypass function). Returned, cooled or to be cooled medium such as exhaust gas, charge air, coolant, oil, etc. is bypassed around the at least one radiator, so that the medium such as exhaust gas, charge air, coolant, oil, etc. is not cooled. With the heat transfer valve device 11, 121, 131, 141, 151, 161, 211, 300, the leakage is particularly advantageously reduced. Namely, in the prior art, a leakage current flows to medium such as exhaust gas, charge air, coolant, oil in bypassing (bypass function) due to the poor seal by the radiator or the cooling function by the bypass. This leakage current is particularly advantageously reduced when using the heat transfer valve device 11, 121, 131, 141, 151, 161, 211, 300 as a bypass valve, so that the leakage current only 0.5% to 10%, especially 0.5% to 7% , in particular 0.5% to 5%, in particular 0.5% to 3%, in particular 0.5% to 2% of the medium flowing into the heat exchanger valve device 11, 121, 131, 141, 151, 161, 211, 300, such as exhaust gas , Charge air, coolant, oil, etc. is. FIG. 19 shows a section through a heat exchanger valve device 401 according to a further exemplary embodiment. The heat transfer valve device 401 comprises a housing 402 with an inlet 404 for a fluid. The input 404 communicates with a port for an exhaust pipe or for a charge air line. The input 404 can be connected via passages 406, 407 to a heat exchanger outlet 411 or to a bypass outlet 412. In the passages 406, 407, an actuator 416 is guided to and fro movable. The actuator 416 is also referred to as a spool or valve spool. The valve spool 416 is attached to one end of a piston rod 418. The other end of the piston rod 418 is arranged in a drive device 420. The heat transfer valve device 401 functions in the same manner as the previously described heat transfer valve devices.

When the spool 416 is in its (not shown) zero position, then the two passages 406, 407 are closed by the piston valve 416, so that the exhaust gas recirculation line connected to the input 404 is closed. By a movement of the actuator or spool 416 of the drive means 420 away, that is to the left, the exhaust gas recirculation line is opened to the heat exchanger outlet 411 so that the exhaust gas can flow through an associated exhaust gas heat exchanger. By moving the actuator 416 out of the zero position in the other direction, that is, toward the drive device 420 toward the right, the exhaust gas recirculation line is opened to the bypass port 412. Then, as shown, the exhaust gas may flow from the inlet 404 through the passage 407 to the bypass outlet 412 and bypass the exhaust gas heat exchanger. The size of the stroke sets the amount of recirculated exhaust gas.

In order to achieve a minimum amount of regulation of the recirculated exhaust gas necessary in certain operating conditions of the internal combustion engine, the actuator 416 is designed according to one of the embodiments described below. The actuator 416 includes a closing body 422, which has substantially the shape of a circular cylinder. In FIGS. 20 to 27, various closing bodies 430; 440; 450 and 460 each shown alone in different views. To denote the same parts, the same reference numerals are used. The closing bodies illustrated in FIGS. 20 to 27 each comprise an essentially circular-cylindrical base body 431 with a lateral surface 432 and two end faces 433, 434. In addition, the main body 431 comprises a central through-hole 437 which is provided with phases 438, 439 at the ends and serves to receive the piston rod end.

In the exemplary embodiment illustrated in FIGS. 20 and 21, the base body 431 is provided with a respective phase 435, 436 at the transitions between the lateral surface 432 and the front sides 433, 434. The phases 435, 436 are executed circumferentially in the illustrated embodiment. However, the phases 435, 436 can also be subdivided into two or more segments.

In the exemplary embodiment illustrated in FIGS. 22 and 23, the transition of the lateral surface 432 of the main body 431 to the two end faces 433, 434 is in each case provided with a circular arc-shaped curve 445, 446. The curves 445, 446 may be circumferential (as shown) or divided into two or more segments, respectively.

In the exemplary embodiment illustrated in FIGS. 24 and 25, the transition of the lateral surface 432 to the two end faces 433, 434 has in each case an elliptical curve 455, 456. The two curves 455, 456 may be circumferential, or each divided into two or more segments.

In the exemplary embodiment illustrated in FIGS. 26 and 27, it is shown that the transitions between the lateral surface 432 and the front sides 433, 434 have one or more, symmetrically arranged recesses 462, 463, 464.

In FIGS. 28 to 33, it is indicated that the depressions can have different cross-sectional shapes 465 to 470. Thus, the have a triangular cross section 465, a rectangular cross section 466, a trapezoidal cross section 467, a circular arc-shaped cross section 468, or different elliptical cross sections 469 and 470.

In FIGS. 34 to 36 it is indicated that the depressions can also be designed differently in longitudinal section. In FIG. 34 it can be seen that the depression in longitudinal section has the shape of a straight line which rises from the end face 434 to the lateral surface 432. In FIG. 35 it can be seen that the depression can also have a circular arc-shaped course 472 in longitudinal section. In FIG. 36 it can be seen that the depression has an elliptical profile 473 in longitudinal section.

Furthermore, control edges can be provided in the housing, through which the valve slide is guided. In FIGS. 37 and 38, a part or section of a housing 475 with a circular-cylinder jacket-shaped inner surface 476 and a side surface 477 is shown in different views. At the transition between the side surface 477 to the inner surface 476, a phase 478 is provided. The phase 478 has a control edge 479 radially inward. Instead of the phase 478 may also be provided a circular arc or an elliptical curve. The phase 478 or the rounding can be divided circumferentially or into two or more segments.

In Figs. 39 and 40, a portion or portion of a housing 481 having an inner surface 482 and a side surface 483 is shown in various views. In the transition region between the side surface 483 and the inner surface 482 depressions 484 to 486 are provided in the form of notches. The recesses 484 to 486 have a circular arc-shaped cross section and an elliptical longitudinal section.

Four different coordinate diagrams are shown in FIGS. 41 to 44, in each of which the flow rate D is plotted over the stroke H of a previously described heat exchanger valve device. With the measures described above, it is possible, the flow rate D each to adjust the size of the displacement of the actuator, so the stroke-flow characteristics of the heat exchanger valve device according to the invention to a desired level. As can be seen, linear (FIG. 41), progressive (FIG. 42), degressive (FIG. 43) and sigmoidal (FIG. 44) curves of the stroke-flow curve can easily be achieved.

Claims

Patent claims

A heat transfer valve device for controlling a fluid flow, in particular an exhaust or charge air flow, comprising a valve housing (2; 52; 212; 402; 475; 481) having an inlet (4; 54; 214; 404) for the fluid flow and a heat exchanger outlet (11, 61, 221, 411), by means of which a heat exchanger, in particular a cooler, depending on the position of a valve body, a more or less large fluid flow is supplied, characterized in that the valve housing (2, 52, 212, 402 475; 481) has a further outlet, in particular a bypass outlet (12; 62; 222; 412), by which, as a function of the position of a valve slide (16; 66; 226; 416), which projects from a zero position in which a fluid flow passage is closed by the valve slide, is arranged between two open positions movable in the valve housing (2; 52; 212; 402; 475; 481), a more or less large fluid flow past the heat exchanger tbar is.

2. Heat exchanger valve device according to claim 1, characterized in that the valve slide (16; 66; 226) between a first extreme position in which the further output (12; 62; 222) is closed and the heat exchanger outlet (11; 61; 221) is opened , and a second extreme position is movable back and forth, in which the further output (12; 62; 222) is opened and the heat exchanger output (11; 61; 221) is closed.

3. Heat exchanger valve device according to one of the preceding claims, characterized in that in a further valve Position of the valve spool, the other output (12, 62, 222) and the heat exchanger outlet (11, 61, 221) are closed.

4. Heat exchanger valve device according to one of the preceding claims, characterized in that in a further valve position of the valve slide, the further output (12; 62; 222) and the heat exchanger outlet (11; 61; 221) are at least partially opened.

5. Heat exchanger valve device according to one of the preceding claims, characterized in that in a further valve position of the valve slide the further output (12; 62; 222) and the heat exchanger outlet (11; 61; 221) are opened.

6. Heat exchanger valve device according to one of the preceding claims, characterized in that in a further valve position of the valve slide the further output (12; 62; 222) is in particular partially opened and the heat exchanger outlet (11; 61; 221) is closed.

7. Heat exchanger valve device according to one of the preceding claims, characterized in that in a further valve position of the valve slide the heat exchanger outlet (11; 61; 221) is in particular partially opened and the further outlet (12; 62; 222) is closed.

8. The heat exchanger valve device according to claim 1, wherein the valve slide (66; 432) extending between two end faces (433, 434).

9. Heat exchanger valve device according to claim 8, characterized in that the closing body (70; 80; 90; 230) has a central passage hole (75; 85; 95).

10. Heat exchanger valve device according to claim 8 or 9, characterized in that the closing body (80; 90; 230) has at least one end face a plurality of projections (88,89; 201-203; 231,232).

11. Heat exchanger valve device according to one of claims 8 to

10, characterized in that the closing body (90; 230) has a plurality of projections (201-205; 231-234) on both end faces.

12. Heat exchanger valve device according to one of claims 8 to

11, characterized in that the transitions between the lateral surface (432) and the end faces (433,434) of the closing body (430) have at least one phase (435,436).

13. Heat exchanger valve device according to one of claims 8 to

12, characterized in that the transitions between the lateral surface (432) and the end faces (433, 434) have at least one rounding (445, 455, 455, 456).

14. Heat exchanger valve device according to claim 13, characterized in that the rounding (445, 446, 455, 456) extends in a circular arc or ellipse.

15. Heat exchanger valve device according to one of claims 12 to 14, characterized in that the transitions between the lateral surface (432) and the end faces (433.434) at least one recess (462-464), preferably a plurality of recesses, having the lateral surface (432) with the associated end face (433,434) connects.

16, heat exchanger valve device according to claim 15, characterized in that the recess has a polygonal, in particular triangular (465), rectangular (466) or trapezoidal (467), cross-section.

17, heat exchanger valve device according to claim 15, characterized in that the recess has a round, in particular circular arc-shaped (468) or elliptical, cross-section (469.470).

18. Heat exchanger valve device according to one of claims 15 to 17, characterized in that the recess in the longitudinal section has the shape of a straight line (471) which increases obliquely to the lateral surface (432).

19. Heat exchanger valve device according to one of claims 15 to 17, characterized in that the recess in the longitudinal section of a circular arc (472) or elliptical (473) extends.

20. Heat exchanger valve device according to one of claims 15 to 19, characterized in that a plurality of depressions (462-464) are arranged distributed in the circumferential direction, in particular evenly.

21. Heat exchanger valve device according to one of the preceding claims, characterized in that a transition between an inner surface (476; 482) and a side surface (477; 483) of the valve housing (472; 481) is designed as a control transition.

22, heat exchanger valve device according to claim 21, character- ized in that the control transition has a control edge (479) for the valve spool.

23. Heat exchanger valve device according to claim 21 or 22, characterized in that the control transition has a phase (478).

24. Heat exchanger valve device according to claim 21 or 22, characterized in that the control transition has at least one rounding.

25. heat exchanger valve device according to claim 24, characterized in that the rounding is circular arc or elliptical.

26, heat exchanger valve device according to one of claims 21 to 25, characterized in that the control transition at least one recess (484-486), preferably a plurality of recesses, which connects the inner surface (482) with the side surface (483).

27, heat exchanger valve device according to claim 26, characterized in that the recess has a polygonal, in particular triangular, rectangular or trapezoidal, cross-section.

28, heat exchanger valve device according to claim 26, characterized in that the recess (484-486) has a round, in particular circular arc-shaped or elliptical, cross-section.

29. Heat exchanger valve device according to one of claims 26 to 28, characterized in that the recess in longitudinal section the

Has a shape of a straight line which slopes from the side surface obliquely to the inner surface.

30. Heat exchanger valve device according to one of claims 26 to 28, characterized in that the recess (484-486) extends in a longitudinal section circular arc or elliptical.

31, heat exchanger valve device according to one of claims 26 to 30, characterized in that a plurality of depressions (484-486) are arranged distributed in the circumferential direction, in particular evenly.

32. Heat exchanger valve device according to one of the preceding claims, characterized in that the heat transfer valve Leinrichtung has a stroke-flow curve with a linear, progressive or sigmoidal course.

33. Heat exchanger valve device according to one of claims 8 to 32, characterized in that the valve slide (226) by means of at least one spring element (236,239,303), in particular biased by a symmetrically biased spring or between two spring elements (236,239), in a zero position or in a zero position is held in which the input (214) is closed.

34. Heat exchanger valve device according to one of claims 8 to 33, characterized in that the closing body (230) through two bearing rings (261, 262) is guided.

35. Heat exchanger valve device according to one of the preceding claims, characterized in that the valve slide (16; 66) is at least partially made of ceramic and / or steel.

36. Heat exchanger valve device according to one of the preceding claims, characterized in that the valve housing (2, 52) is at least partially made of ceramic and / or steel.

37. Heat exchanger valve device according to one of the preceding claims, characterized in that the valve slide (16) is equipped with at least one sealing element (24) for the input (4).

38. heat exchanger valve device according to claim 37, characterized in that the at least one sealing element (24) has an input (4) facing the sealing surface (26) having the shape of a ball portion, a ball, a cylinder, a cone o- of a truncated cone Has.

39. Heat exchanger valve device according to claim 37 or 38, characterized in that the at least one sealing element (24) on the valve spool (16) is guided back and forth movable.

40. Heat exchanger valve device according to one of claims 37 to 39, characterized in that the at least one sealing element (24) by a spring means (30) is biased against the input (4).

41. Heat exchanger valve device according to one of the preceding claims, characterized in that the valve slide (16) has at least one pressure equalization channel (22).

42. A method for cleaning a heat exchanger valve device according to one of the preceding claims, characterized in that the valve slide (16; 66) is moved from a starting position once or several times back and forth.

43. The method according to claim 42, characterized in that during the method for cleaning the heat exchanger output

(11; 61; 221) and / or the bypass outlet (12; 62; 222) are closed.

44. The method according to claim 42 or 43, characterized in that the method for cleaning is started as soon as a detected sensor signal of a sensor device, in particular for measuring a frictional resistance force of a frictional resistance between at least one closing body (230, 302) and at least one housing guide portion (350) , coincides with a reference signal.

45. Heat exchanger, in particular exhaust gas heat exchanger, with a heat exchanger valve device (1) according to one of claims 1 to 41.

46. Exhaust gas recirculation system with or on an internal combustion engine, in particular an engine, which is or at a sampling point (108) diverted and fed back via a return point (109) exhaust gas, characterized in that between see the removal point (108) and the return point (109) a

Heat exchanger valve device (111, 121, 131, 141, 151, 161) is connected according to one of claims 1 to 41.

47. Exhaust gas recirculation system according to claim 23, characterized in that the heat exchanger valve device

(111, 121, 131, 141, 151, 161) is connected to an exhaust gas cooling device (112, 122, 132, 133, 142, 152, 162, 163).

48. Exhaust gas recirculation system according to one of claims 46 to 47, characterized in that the heat exchanger valve device

(111, 121, 131, 141, 151, 161) is integrated into the exhaust gas cooling device (112, 122, 132, 133, 142, 152, 162, 163).

49. Exhaust gas recirculation system according to one of claims 46 to 48, characterized in that the heat exchanger valve device

(111, 121, 131, 141, 151, 161) is integrally connected to the exhaust gas cooling device (112, 122, 132, 133, 142, 152, 162, 633).

50. Exhaust gas recirculation system according to one of claims 46 to 49, characterized in that the exhaust gas cooling device

(112,132,133,142, 162,163) has a bypass.

51. Exhaust gas recirculation system according to one of claims 46 to 50, characterized in that the exhaust gas cooling device (122, 152) comprises a U-flow cooler.

52. Exhaust gas recirculation system according to one of claims 46 to 51, characterized in that the heat transfer valve device (111, 121, 131, 141, 151, 161), viewed in the flow direction from the removal point (108) to the return point (109), upstream to the exhaust gas cooling device (112,122,132,133,142,152,162,163) is arranged.

53. Exhaust gas recirculation system according to one of claims 46 to 52, characterized in that the heat exchanger valve device

(111, 121, 131, 141, 151, 161), viewed in the flow direction from the extraction point (108) to the return point (109), downstream of the exhaust gas cooling device (112,122,132,133,142,152,162,163) is arranged.

54. Exhaust gas recirculation system according to one of claims 46 to 53, characterized in that the heat transfer valve device (131, 161) comprises a high-temperature exhaust gas cooler (132, 162) and a low-temperature exhaust gas cooler (133, 163).

55. Exhaust gas recirculation system according to one of claims 46 to 54, characterized in that the heat transfer valve device (131, 161) viewed in the flow direction from the removal point (108) to the return point (109), upstream or downstream of the high-temperature exhaust gas cooler (132,162) or the low-pressure exhaust gas cooler (133, 163) is arranged.

56. Exhaust gas recirculation system according to one of claims 46 to 55, characterized in that the exhaust gas recirculation system is formed by a high-pressure exhaust gas recirculation system.

57. Exhaust gas recirculation system according to one of claims 46 to 55, characterized in that the exhaust gas recirculation system is formed by a low-pressure exhaust gas recirculation system.