DE102011055406B4 - Valve device for an oil supply device of a motor vehicle internal combustion engine - Google Patents

Abstract

Valve device (100) for an oil supply device of a motor vehicle internal combustion engine comprising a bushing (102) with fluid connections (172, 174, 176, 178), a piston device (134) adjustably received in the bushing (102) and an actuating device (166) for adjusting the piston device (134) between actuating positions, wherein the piston device (134) has a piston portion (136) and a sleeve portion (138), wherein the sleeve portion (138) with the piston portion (136) is positively, positively and / or materially connected, wherein actuation position-dependent with the valve device (100) the flow direction and / or the flow rate of a first fluid flow is changeable and a second fluid flow is releasable or lockable, wherein the first fluid flow for controlling an oil pump or a heat exchanger bypass and / or the second fluid flow for controlling a Cooling is used, the piston device (134) m ithilfe the actuator (166) against the force of a spring (164) is adjustable and the piston means (134) is adjusted in inactive actuator in an actuated position in which the second fluid flow is released.

Description

The invention relates to a valve device for an oil supply device of a motor vehicle internal combustion engine comprising a bushing with fluid connections, a piston device adjustably received in the bush and an actuating device for adjusting the piston device between actuation positions.

From the DE 10 2005 006 054 A1 Method for operating a reciprocating internal combustion engine is known with at least one guided in a cylinder piston, an oil supply circuit, a device for cooling the piston by means of oil, a control device and a switching valve for controlling the amount of oil for cooling the piston wherein the switching valve is controlled by the control unit and the Oil flow through the device for cooling the piston operating point-dependent controls by the switching valve is closed, when at another point of the reciprocating internal combustion engine, a temporarily increased oil consumption is detected by the controller to provide a method for operating an internal combustion engine, wherein a cooling of a piston with operating point dependent oil.

From the DE 10 2009 060 188 A1 an adjusting valve for a positive displacement pump is known, the adjusting valve comprising a valve housing having a pressure chamber having an inlet and an outlet for the pressurized fluid, a first valve body which is acted upon by at least one control force, a relative to the first valve body movable second valve body, which is movable in a first direction to a first position and in a second direction to a second position, and which has a valve body surface which can be acted upon by the pressurized fluid in the second direction, and at least one restoring member acting on the second valve body, which counteracts the pressure fluid, wherein the inlet and the outlet of the pressure chamber are separated from each other in befindlichem in the first position second valve body and connected to each other in the second position second valve body to the delivery volume of a positive displacement pump to the e ines to be supplied by the pump to be supplied unit. Of the DE 10 2009 060 188 A1 Accordingly, the first valve body has a connection channel connecting the inlet to the outlet when the second valve body occupies the second position, and is closed by the second valve body when the second valve body occupies the first position.

From the alien US 4 245 465 A a valve device for a lubricating oil supply of a gas turbine is known. In accordance with the invention, this valve means comprises a bushing with fluid ports and a piston means adjustably received in the bushing. For adjusting the piston device between actuation positions, an oil pressure is provided at the inlet channel of the valve device. The piston device has a piston portion and a sleeve portion, which are mutually displaceable. In this case, a spring is provided between the piston portion and the sleeve portion.

The US 3,043,092 A relates to a valve device for a lubricating device of a supercharged internal combustion engine. In this case, the valve device has a piston device with a piston portion and a sleeve portion, which are mutually displaceable. In this case, a spring is provided between the piston portion and the sleeve portion.

The DE 10 2009 060 188 A1 relates to a valve device for an oil supply device of a motor vehicle internal combustion engine. In this case, the valve device has a piston device with a piston portion and a sleeve portion, which are mutually displaceable. In this case, a pressure chamber is provided between the piston portion and the sleeve portion.

The invention has for its object to provide an aforementioned valve means for an oil supply device of a motor vehicle internal combustion engine with increased functionality and reduced construction costs.

The object is achieved with a valve device for an oil supply device of a motor vehicle internal combustion engine comprising a bushing with fluid connections, an adjustably received in the jack piston means and an actuator for adjusting the piston means between actuation positions, wherein the piston means comprises a piston portion and a sleeve portion.

Motor vehicle internal combustion engines may have an oil supply device. With such an oil supply device, the internal combustion engine and / or units can be supplied for example with lubricating oil, cooling oil and / or working oil. The valve device may be a cartridge valve or a cartridge valve. The valve device can be mounted on a control block. The piston device may be adjustable relative to the socket. The piston device can be adjustable in the axial direction. The piston device can be displaceable. The actuator may be an electromagnetic actuator. The actuating device may comprise an electromagnet. The actuating device can have a proportional magnet. The Valve device may have an electrical plug connection. The actuating device may have a housing. The valve device may have a fastening section. The valve device may have a valve longitudinal axis. The piston device may have a Kolbeneinrichtungslängsachse. The valve assembly longitudinal axis and the piston assembly longitudinal axis may be identical.

With the valve device according to the invention a design freedom in the design of the valve device, in particular the piston device is increased. A manufacturing effort for the production of the valve device, in particular the piston device, is reduced. At the piston device undercuts can be produced in a simple manner. Channels in the piston device in the direction of the Kolbeneinrichtungslängsachse can be produced in a simple manner.

The piston portion may include a first portion having a first piston portion outer diameter and a second portion having a second piston portion outer diameter, wherein the first piston portion outer diameter may be larger than the second piston portion outer diameter, the sleeve portion may have a sleeve outer diameter and a sleeve inner diameter and the outer diameter of the sleeve at least approximately corresponding to the first piston portion outer diameter and the sleeve inner diameter may at least approximately correspond to the second piston portion outer diameter.

The first portion and the second portion of the piston portion may be arranged one behind the other in the direction of the piston assembly longitudinal axis. The piston portion may include a first end portion and a second end portion. The first portion may be disposed at the first end portion. The second portion may be disposed at the second end portion. The piston portion may be adjustably guided by the first portion and by means of the sleeve portion in the sleeve. A difference between the first piston portion outer diameter and the second piston portion outer diameter may at least approximately correspond to a wall thickness of the sleeve portion. The sleeve portion may have the same length or a smaller length than the second portion of the piston portion. The sleeve portion may be aligned with the second portion of the piston portion in the direction of the piston longitudinal axis. For the defined aligned arrangement of the sleeve portion at the second portion of the piston portion in the direction of the piston assembly longitudinal axis of the sleeve portion and the piston portion may have corresponding reference marks. Fiducial marks can be edges, heels or openings. Fiducial marks may be present anyway or may be specially attached for this purpose.

E can thus be formed between the second portion of the piston portion and the sleeve portion a fit. It may be formed between the first portion of the piston portion and the sleeve and between the sleeve portion and the socket a fit.

The sleeve portion may be positively, positively and / or materially connected to the piston portion. The sleeve portion may be locked to the piston portion. The sleeve portion may be connected to the piston portion by means of a press fit. The interference fit can be an interference fit. The sleeve portion may be glued to the piston portion. The sleeve portion may be welded to the piston portion. For a displacement of the sleeve portion and the piston portion is prevented during operation of the valve device. It is ensured easy manufacturability.

The piston portion may have a third portion with a third piston portion outer diameter, wherein the third piston portion outer diameter may be smaller than the second piston portion outer diameter, and between the sleeve portion and the third portion of the piston portion, a longitudinal channel of the piston device may be formed. There may be a longitudinal channel of the piston device between the sleeve inner diameter and the third piston portion outer diameter. A longitudinal channel may be a channel that extends in the direction of the Kolbeneinrichtungslängsachse. The at least one longitudinal channel may have an annular cross-section. The at least one longitudinal channel may have a circular cross-section-like cross-section.

The sleeve portion may have at least one control edge. The sleeve portion may have end portions. At least one end portion may be arranged a control edge. There may be a control edge disposed in a portion between the end portions. The at least one control edge of the sleeve portion may cooperate with at least one control edge of the sleeve.

At least one transverse channel may be formed in the sleeve section. A transverse channel may be a channel extending transversely to the piston longitudinal axis. The at least one transverse channel may have a circular cross-section exhibit. The at least one transverse channel can open into a longitudinal channel. The at least one transverse channel can connect longitudinal channels with each other. The at least one transverse channel may be disposed in a portion between the end portions of the sleeve portion. The at least one transverse channel can be arranged in a middle section of the sleeve section.

Depending on the operating position, the flow direction and / or the flow quantity of a first fluid flow can be changeable with the valve device, and a second fluid flow can be releasable or lockable. A fluid stream may be a fluid stream flowing through a port of the bushing. A flow direction may be a flow direction through a port of the socket. There may be a first flow direction and a second flow direction. The first flow direction and the second flow direction may be opposite to each other. With the valve device according to the invention, a first fluid flow and a second fluid flow can be controlled by means of a single sleeve, a single piston and a single actuator. It may be omitted a separate socket, a separate piston and a separate actuator. It can be omitted a separate electrical connector. It can account for a separate power supply. The first fluid flow and the second fluid flow can be controlled at least approximately independently of one another, at least in the relevant operating positions.

The first fluid flow can be used to control an oil pump or a heat exchanger bypass and / or the second fluid flow can serve for cooling. This can be controlled with a single valve device, two separate fluid streams. For example, an oil pump or a heat exchanger bypass and a piston cooling can be controlled. For example, an oil pump or a heat exchanger bypass and an auxiliary heating circuit can be controlled. For example, an oil pump or a heat exchanger bypass and another device can be controlled. With the valve device, two otherwise structurally separate valves can be replaced.

The oil pump can serve to supply the internal combustion engines and / or aggregates with lubricating oil, cooling oil and / or working oil. The oil pump can be a positive displacement pump. The oil pump may be a rotary piston pump. The oil pump may be a rotary vane pump or a gear pump. The oil pump can be regulated. A change in the direction of flow and / or the flow rate may cause a change in the flow rate of the oil pump. With the valve device according to the invention can thus be made a control of a controllable oil pump.

The first fluid stream may serve to control a bypass valve. The first fluid stream may serve to control or regulate a bypass valve. By means of the by-pass valve, a heat exchanger bypass fluid flow can be controllable. The first fluid stream may be a control fluid stream. The first fluid stream may be a heat exchanger bypass fluid stream. The first fluid stream may be a working fluid stream. The working fluid may be a lubricating oil, cooling oil and / or working oil. The heat exchanger may be an oil cooler. The heat exchanger may be a heater core. By means of the heat exchanger, an interior of the motor vehicle can be heated. With the aid of the heat exchanger, a pane, in particular a windshield, of the motor vehicle can be heated. With the valve device according to the invention thus a temperature of a working fluid is controllable. There may be omitted control elements, such as wax element or bimetallic element.

The cooling may be a cooling of pistons of the internal combustion engine. For piston cooling, a piston cooling device may be provided. The piston cooling device may have at least one spray nozzle for injecting a piston and / or cylinder surface of the internal combustion engine. Injection can be continuous or intermittent. The second fluid stream may have an alternating pressure level. The piston cooling device may have at least one fluid channel for the fluid-conducting connection of the at least one spray nozzle to the second fluid flow. With the valve device according to the invention can thus be carried out a control of a piston cooling device. The second fluid stream may be a working fluid stream. The second fluid flow may be a pilot flow for pilot control of a main valve. The main valve may control a working fluid flow of a piston cooling device. With the second fluid flow is then an indirect control. This allows control of large working fluid flow rates.

The piston device can be adjusted by means of the actuating device against the force of a spring and the piston device can be adjusted in an inactive actuator in an actuating position in which the second fluid flow is released. This is given inactive actuator, especially in case of failure or failure of the actuator, a preferred position of the valve device. In the preferred position, a first working device assigned to the first fluid flow is subjected to a fluid in a first flow direction, in which damage is limited or prevented. In the preferred position, a second working fluid associated with the second fluid flow is subjected to fluid, so that damage is limited or prevented. It is given a reliability.

The valve device may be a four port proportional directional control valve. The valve device may be a continuous valve, which allows not only discrete switching positions, but a steady transition of the valve opening. The bushing may have four fluid ports. At least one fluid port may be formed by means of a groove extending in the circumferential direction of the bushing. The groove can be arranged on the bushing radially on the outside. The bush may have radially outwardly three grooves extending in the circumferential direction of the bush, with which three fluid ports are formed as ring channels. Alternatively, the bush may also have axially spaced transverse bores forming the three fluid ports. These transverse bores can also be arranged circumferentially offset from one another in addition to the axial offset. A fluid port may be formed by means of a passageway extending in the axial direction of the sleeve. The bushing may have an axially directed end portion. The passage may be disposed at an end portion of the socket. Thus, the valve device according to the invention has a particularly compact design.

The socket may have a supply connection, a first working connection, a second working connection and a tank connection. The supply connection can be fluid-conductively connected to a pump. Through the first working port, the first fluid flow can flow. The first working connection can be fluid-conductively connected to a first working device. Through the second working port, the second fluid stream can flow. The second working connection can be fluid-conductively connected to a second working device. The tank connection can be fluid-conductively connected to a reservoir. The fluid flow passing through the first working port may be the first fluid flow. The fluid flow passing through the second working port may be the second fluid flow. The valve device according to the invention thus makes it possible to control the fluid flows between the supply connection, the first working connection, the second working connection and the tank connection. Variable volume flows can be controlled.

The piston device may be adjustable between a first end position and a second end position relative to the socket. The first end position may be a maximum retracted position of the piston device. The second end position may be a maximum extended position of the piston device. Positions may be present between the first and second end positions in which the piston device is partially extended, for example 25%, 50% and 75%. In the first end position, the first fluid flow in a first flow direction and the second fluid flow can be released. In a position in which the piston device is extended 25%, the first fluid flow in the first flow direction can be released and the second fluid flow can be blocked. In a position in which the piston device is extended 50%, the first fluid flow in the first flow direction can be released and the second fluid flow can still be blocked. In a position in which the piston device is extended 75%, the first fluid flow can be blocked and the second fluid flow can be released. In the second end position, the first fluid flow can be released in a second flow direction and the second fluid flow can be released.

In summary, and in other words thus results from the invention, inter alia, a structural design of a cartridge valve for oil pump actuation or actuation of an oil cooler bypass valve and piston cooling, the combined valve both the control of the oil pump or the oil cooler bypass and the switching of Piston cooling can take over. The valve can be a proportional valve with which the oil cooler bypass is controllable. Thus, as part of a heat management, an oil cooler can be controlled / regulated, in particular to improve the efficiency / efficiency and, for example, to allow thawing of a windscreen in winter, even if the engine is still quite cold and slowly heats up due to high efficiency.

Hereinafter, embodiments of the invention will be described with reference to figures. From this description, further features and advantages. Concrete features of these embodiments may represent general features of the invention. Features associated with other features of these embodiments may also constitute individual features of the invention.

They show schematically and by way of example:

1 a proportional valve for controlling an oil pump or an oil cooler bypass and for controlling a piston cooling,

2 a diagram with characteristics of a proportional valve for controlling an oil pump or an oil cooler bypass and to control a piston cooling,

3 a diagram with characteristics of a proportional valve for controlling an oil pump or an oil cooler bypass and for controlling a piston cooling and

4 a diagram with characteristics of a proportional valve for controlling an oil pump or an oil cooler bypass and for controlling a piston cooling.

1 shows as an example of a valve device according to the invention, a proportional valve for controlling an oil pump, not shown here or an oil cooler bypass not shown here and for controlling a piston cooling also not shown here.

The valve 100 is a longitudinal slide valve. The valve 100 has a socket 102 on. The socket 102 has a tubular shape. The socket 102 has two end sections 104 . 106 on. The end section 104 is an outside end section. The end section 106 is an inside end section.

The socket 102 has radially outward in the circumferential direction of the socket 102 extending grooves 108 . 110 . 112 on. The grooves 108 and 112 have a rectangular cross-section. The groove 110 is designed in accordance with its groove bottom. The socket 102 has three grooves 108 . 110 . 112 on. The grooves 108 . 110 . 112 are in the direction of the axis 114 the socket 102 spaced at least approximately equidistant from each other. At the outside end portion 106 has the socket 102 a groove 116 for receiving a seal, such as O-ring seal on.

At its inside end portion 106 has the socket 102 one in the direction of the axis 114 extending opening. In this opening is an insert 118 used, in turn, one in the direction of the axis 114 extending opening 120 having.

The socket 102 has an outer radius 122 on. The valve 100 can be used in a control block, not shown here. The control block has for a recording with an inner contour, with the outer radius 122 the socket 102 corresponds geometrically and functionally. The in the groove 116 received seal then seals between the control block and the socket 102 , When the valve 100 inserted in a control block, the grooves can 108 . 110 . 112 be covered with the control block so that with the grooves 108 . 110 . 112 Ring channels are formed. The control block can be designed separately. The control block can be integrated in a machine housing. The control block can be integrated in an internal combustion engine housing. The control block may be integrated in a crankcase of an internal combustion engine.

At the bottom of each groove 108 . 110 . 112 are related to the axis 114 radially extending passages 124 . 126 . 128 available. The passages 124 . 126 . 128 allow passage to the interior of the socket 102 , The passages 124 . 126 . 128 are present holes.

The socket 102 has an inner radius 130 on. The socket 102 has radially inward in the circumferential direction of the socket 102 extending groove 132 on. Between the groove 132 and the passages 126 . 128 on the one hand and the inner radius 130 on the other hand edges are formed. These edges are executed here sharp-edged. However, in another embodiment, the edges may also be chamfered or axial scored.

In the socket 102 is precisely a piston device 134 added. The piston device 134 is in the socket 102 in the direction of the axis 114 displaceable. Between the piston device 134 and the inner radius 130 the socket 102 is a given game available. The inner radius 130 corresponds geometrically and functionally with the piston device 134 , The piston device 134 has a piston portion 136 and a sleeve section 138 on. The piston device 134 has two end sections 140 . 142 on. The end section 140 is an outside end section. The end section 142 is an inside end section.

The piston section 136 has a first outer diameter 144 , a second outer diameter 146 and a third outer diameter 148 on. The first outer diameter 144 is larger than the second outer diameter 146 , The second outer diameter 146 is larger than the third outer diameter 148 , The piston section 136 points in the direction of inside end section 142 the piston device 134 the first outer diameter 144 on. Towards the outside end portion 140 the piston device 134 follows a section that has a second outer diameter 146 having. Continue towards the outside end section 140 the piston device 134 follows a section that has a third outer diameter 148 having. Continue towards the outside end section 140 the piston device 134 follows a section, again a second outer diameter 146 having. At its towards the outside end section 140 the piston device 134 facing end, the piston portion 136 one opposite the second outer diameter 146 reduced diameter.

The piston section 136 is a hollow piston with an interior 150 executed. That towards the outside end portion 140 the piston device 134 pointing end of the piston section 136 is closed. That towards the inside end section 142 the piston device 134 pointing end of the piston section 136 it is open. At its towards the outside end section 140 the piston device 134 facing end, the piston portion 136 one transverse to the axis 114 extending opening 152 on. The opening 152 extends to the interior 150 of the piston section 136 and forms a channel.

The sleeve section 138 has an inner diameter and an outer diameter. The outer diameter of the sleeve section 138 corresponds to the first outer diameter 144 of the piston section 136 , The inner diameter of the sleeve section 138 corresponds to the second outer diameter 146 of the piston section 136 , The sleeve section 138 has on the outside a circumferential groove 154 on. The groove 154 has a rectangular cross-section. At a bottom of the groove 154 is an opening 156 arranged, extending up to the inner diameter of the sleeve portion 138 extends. The opening 156 forms one transverse to the axis 114 running channel.

The sleeve section 138 is at the in the direction of the outside end portion 140 the piston device 134 pointing end portion of the piston portion 136 arranged. Between the sleeve section 138 and the piston portion 136 is formed a press fit. This is the sleeve section 138 and the piston section 136 positively connected firmly. A section of the inner diameter of the sleeve section 138 that is not on the sleeve section 138 has an exemption. This is a joining of sleeve section 138 and piston section 136 facilitated.

In the direction of the axis 114 is the sleeve section 138 so to the piston portion 136 arranged that one edge of the opening 156 of the sleeve section 138 at least approximately flush with an edge of the portion of the piston device 134 that has the third outside diameter 148 has, runs. That towards the outside end portion 140 the piston device 134 pointing end of the piston section 136 is something about the end of the sleeve section 138 above.

The sleeve section 138 covered in the direction of the axis 114 the section of the piston section 136 that has the third outside diameter 148 such that one in the direction of the axis 114 running channel 158 the piston device 134 is formed. The opening 156 forms a first opening of the channel 158 , The sleeve section 138 covered in the direction of the axis 114 the section of the piston section 136 that has the third outside diameter 148 not completely. This is a second opening of the channel 158 educated. The channel 158 has a ring-like cross-section.

The piston device 134 has an outer radius. The outer radius of the piston device 134 is with the first outside diameter 144 the piston device 134 and outer diameter of the sleeve portion 138 educated. The piston device 134 has radially outwardly extending in the circumferential direction grooves 160 . 162 on. Between the grooves 160 . 162 and the outer radius of the piston device 134 Control edges are formed. At the inside end portion 142 the piston device 134 a control edge is formed. The control edges are executed here sharp-edged. However, in another embodiment, the edges may also be chamfered or axial scored.

At the inside end portion 142 the piston device 134 supports a coil spring 164 with her one end off. With its other end, the coil spring is supported 164 on the insert 118 from. With the coil spring 164 is the piston device 134 in the direction of the axis 114 to the outside end portion 140 the socket 102 biased towards.

The control edges of the socket 102 and the control edges of the piston device 134 can vary depending on a position of piston device 134 and socket 102 Cover relative to each other and open or block flow channels. There may be positive coverage, negative coverage, and / or zero coverage.

At the outside end portion 140 the socket 102 is an electromagnetic actuator 166 arranged. An actuator of the actuator 166 is with the piston device 134 kinematically connected. Using the actuator 166 is the piston device 134 continuously adjustable. The actuating device has a proportional magnet. With the actuating device 166 can the piston device 134 relative to the socket 102 be adjusted. In this case, an actuating force of the actuating device acts 166 against the force of the coil spring 164 , If no actuating force is applied, the piston device shifts 134 under the action of the force of the helical compression spring 164 to the outside end portion 140 the socket 102 out. This position is in 1 shown. The actuating device 166 is in a housing 168 arranged and has an electrical connector. On the case 168 is a mounting section 170 for fastening the valve 100 provided on the control block.

The groove 110 forms a supply connection 172 of the valve 100 , The opening 120 forms a tank connection 174 of the valve 100 , The groove 112 forms a first work connection 176 of the valve 100 , The groove 108 forms a second work connection 178 of the valve 100 ,

At the first work connection 176 of the valve 100 is connected to an oil pump of a motor vehicle internal combustion engine, not shown here. Dependent on a direction of flow at the working connection 176 of the valve 100 the flow rate of the oil pump can be increased or decreased. This allows a regulation of the oil pump.

At the second work connection 178 of the valve 100 is connected to a not shown piston cooling of a motor vehicle internal combustion engine. When a flow through the second working port 178 is released, a piston cooling can take place. When a flow through the second working port 178 is locked, a piston cooling can be omitted.

In the in 1 shown operating position is a flow between the first working port 176 and the tank connection 174 and between the supply connection 172 and the second work connection 178 Approved.

2 shows a diagram 200 with characteristics of a proportional valve, such as valve 100 according to 1 , for controlling an oil pump or oil cooler bypass and for controlling a piston cooling. On the x-axis, an adjustment of a piston device of the proportional valve is applied to a socket. The piston device is between one position 202 minimal adjustment and one position 204 adjustable maximum adjustment. In between lies a position 206 in which the piston means starting from the position 202 about 25% of their maximum possible adjustment is adjusted, one position 208 in which the piston device is adjusted about 50% and a position 210 in which the piston device is adjusted about 75%. On the y-axis are a characteristic 212 to a flow amount of a first fluid flow in a first flow direction, a characteristic 214 to a flow amount of a first fluid flow in a second flow direction and a characteristic curve 216 applied to a flow amount of a second fluid stream. The first fluid flow is used to control an oil pump or oil cooler bypass. The second fluid flow is used to control a piston cooling.

At position 202 the first fluid flow has a maximum flow quantity in the first flow direction. With adjustment of the piston device on the positions 206 and 208 to the position 210 decreases the flow rate in the first flow direction. At position 210 if the flow quantity has dropped to zero, the first fluid flow in the first flow direction is blocked. In a further adjustment of the piston device to the position 204 the first fluid flow in the first flow direction remains blocked. The characteristic 212 indicates starting from position 202 , in which a maximum value is present, a linear falling course and reaches at position 210 a zero value. In the further course to the position 204 the characteristic remains 212 at zero.

At position 202 the first fluid flow is blocked in the second flow direction. With adjustment of the piston device on the positions 206 and 208 to the position 210 the first fluid flow in the second flow direction remains blocked. In a further adjustment of the piston device starting from position 210 in the direction of position 204 the first fluid flow in the second flow direction is released and the flow rate increases up to the position 204 , The characteristic 214 runs from position 202 to the position 210 at zero. In the further course, the characteristic curve 214 starting from position 210 to the position 204 a linear rising course and achieved at position 204 a maximum value.

At position 202 the second fluid flow has a first flow rate. With adjustment of the piston device in the direction of position 206 decreases the flow rate. In the middle between position 202 and position 206 if the flow volume has dropped to zero, the second fluid flow is blocked. In a further adjustment of the piston device to the position 208 the second fluid flow remains blocked. In a further adjustment of the piston device starting from position 208 in the direction of the positions 210 . 204 the second fluid flow is released again and the flow rate increases up to the position 204 , At position 204 the second fluid flow has a second flow rate. The second flow is greater than the first flow. The second flow rate is about twice as large as the first flow rate. The characteristic 216 indicates starting from position 202 a linear falling course and reaches approximately midway between position 202 and position 206 a zero value. In the further course to the position 208 the characteristic remains 212 at zero. In the further course, the characteristic curve 216 starting from position 208 over position 210 to the position 204 a linear rising course and achieved at position 204 a maximum value.

3 shows a diagram 300 with characteristics of a proportional valve to control an oil pump or oil cooler bypass and to control a piston cooling. On the x-axis, an adjustment of a piston device of the proportional valve is applied to a socket. The piston device is between one position 302 minimal adjustment and one position 304 adjustable maximum adjustment. In between lies a position 306 in which the piston device starting from the position 302 about 25% of their maximum possible adjustment is adjusted, one position 308 in which the piston device is adjusted about 50% and a position 310 in which the piston device is adjusted about 75%. On the y-axis are a characteristic 312 to a flow amount of a first fluid flow in a first flow direction, a characteristic 314 to a flow amount of a first fluid flow in a second flow direction and a characteristic curve 316 applied to a flow amount of a second fluid stream. The first fluid flow is used to control an oil pump or oil cooler bypass. The second fluid flow is used to control a piston cooling.

In deviation to the diagram 200 according to 2 the second fluid flow remains at an adjustment of the piston device starting from position 302 only up to a position approximately midway between position 306 and position 308 blocked. In a further adjustment of the piston device in the direction of the positions 310 . 304 the second fluid flow is released again from this position and the flow rate increases up to the position 304 , The characteristic 316 already points from the position approximately midway between position 306 and position 308 a linearly increasing course. Incidentally, on 2 and the related description.

4 shows a graph of characteristics of a proportional valve for controlling an oil pump or an oil cooler bypass and for controlling a piston cooling. On the x-axis, an adjustment of a piston device of the proportional valve is applied to a socket. The piston device is between one position 402 minimal adjustment and one position 404 adjustable maximum adjustment. In between lies a position 406 in which the piston means starting from the position 402 about 25% of their maximum possible adjustment is adjusted, one position 408 in which the piston device is adjusted about 50% and a position 410 in which the piston device is adjusted about 75%. On the y-axis are a characteristic 412 to a flow amount of a first fluid flow in a first flow direction, a characteristic 414 to a flow amount of a first fluid flow in a second flow direction and a characteristic curve 416 applied to a flow amount of a second fluid stream. The first fluid flow is used to control an oil pump or oil cooler bypass. The second fluid flow is used to control a piston cooling.

In deviation to the diagram 200 according to 2 is the first fluid flow in the first flow direction in an adjustment from position 402 already from a position approximately midway between position 406 and position 408 blocked. The first fluid flow in the second flow direction is already released from this position. At position 402 the second fluid flow has a high flow rate. With adjustment of the piston device on the positions 406 and 408 up to a position approximately midway between position 408 and position 410 decreases the flow rate. In this position, the flow amount has dropped to zero, the second fluid flow is blocked. In a further adjustment of the piston device to the position 404 the second fluid flow remains blocked. The characteristic 412 indicates starting from position 402 , in which a maximum value is present, a linearly falling course and reaches at a position approximately midway between position 408 and position 410 a zero value. In the further course to the position 404 the characteristic remains 412 at zero. Incidentally, on 2 and the related description.

LIST OF REFERENCE NUMBERS

100

Valve

102

Rifle

104

end

106

end

108

groove

110

groove

112

groove

114

axis

116

groove

118

commitment

120

opening

122

outer radius

124

passage

126

passage

128

passage

130

inner radius

132

groove

134

piston device

136

piston section

138

sleeve section

140

end

142

end

144

outer diameter

146

outer diameter

148

outer diameter

150

inner space

152

opening

154

groove

156

opening

158

channel

160

groove

162

groove

164

Coil spring

166

actuator

168

casing

170

attachment section

172

supply terminal

174

tank connection

176

working port

178

working port

200

diagram

202

position

204

position

206

position

208

position

210

position

212

curve

214

curve

216

curve

300

diagram

302

position

304

position

306

position

308

position

310

position

312

curve

314

curve

316

curve

400

diagram

402

position

404

position

406

position

408

position

410

position

412

curve

414

curve

416

curve

Claims (7)

Valve device ( 100 ) for an oil supply device of a motor vehicle internal combustion engine having a socket ( 102 ) with fluid connections ( 172 . 174 . 176 . 178 ), one in the socket ( 102 ) adjustably received piston device ( 134 ) and an actuating device ( 166 ) for adjusting the piston device ( 134 ) between actuation positions, wherein the piston device ( 134 ) a piston portion ( 136 ) and a sleeve section ( 138 ), wherein the sleeve portion ( 138 ) with the piston portion ( 136 ) is positively, positively and / or materially connected, wherein actuation position dependent with the valve device ( 100 ), the flow direction and / or the flow rate of a first fluid flow is changeable and a second fluid flow is releasable or lockable, wherein the first fluid flow for controlling an oil pump or a heat exchanger bypass and / or the second fluid flow for controlling a cooling, wherein the piston device ( 134 ) using the actuating device ( 166 ) against the force of a spring ( 164 ) is adjustable and the piston device ( 134 ) is adjusted in an inactive actuator in an operating position in which the second fluid flow is released. Valve device ( 100 ) according to claim 1, characterized in that the piston portion ( 136 ) a first portion having a first piston portion outer diameter ( 144 ) and a second section having a second piston section outer diameter ( 146 ), wherein the first piston section outer diameter ( 144 ) greater than the second piston section outer diameter ( 146 ), the sleeve section ( 138 ) has a sleeve outer diameter and a sleeve inner diameter and the sleeve outer diameter of the first piston portion outer diameter ( 144 ) corresponds at least approximately and the sleeve inner diameter of the second piston section outer diameter ( 146 ) at least approximately. Valve device ( 100 ) according to one of the preceding claims, characterized in that the sleeve section ( 138 ) with the piston portion ( 136 ) is connected by means of a press fit. Valve device ( 100 ) according to any one of claims 2-3, characterized in that the piston portion ( 136 ) a third section having a third piston section outer diameter ( 148 ), wherein the third piston section outer diameter ( 148 ) smaller than the second piston section outer diameter ( 146 ), and between the sleeve portion ( 138 ) and the third section of the piston section ( 136 ) a longitudinal channel ( 158 ) of the piston device ( 134 ) is formed. Valve device ( 100 ) according to one of the preceding claims, characterized in that the sleeve section ( 138 ) has at least one control edge. Valve device ( 100 ) according to one of the preceding claims, characterized in that in the sleeve section ( 138 ) at least one transverse channel ( 156 ) is formed. Valve device ( 100 ) according to one of the preceding claims, characterized in that the valve device ( 100 ) a four-port proportional directional control valve ( 172 . 174 . 176 . 178 ).

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