GB2552348A

GB2552348A - Multiple 5 temperature level rotary valve

Info

Publication number: GB2552348A
Application number: GB1612544.5A
Authority: GB
Inventors: H Brinker Michael; A Gatowski Jan; V Gonze Eugene
Original assignee: GM Global Technology Operations LLC
Current assignee: GM Global Technology Operations LLC
Priority date: 2016-07-19
Filing date: 2016-07-19
Publication date: 2018-01-24
Also published as: GB201612544D0; GB201614792D0; GB2552391A

Abstract

A rotary valve 2 comprises a rotatable shaft 8 extending into a first chamber 10 and a second chamber 12. The first chamber 10 has a fluid outlet port 20, a first inlet port 42 and a second inlet port 46. The second chamber 12 has a fluid outlet port 22 and an inlet port 52. The first chamber 10 has a first rotatable shutter 16 provided with fluid conduits 58, 60. The second chamber 12 has a second rotatable shutter 18 provided with at least a fluid conduit 62. The first rotatable shutter 16 and the second rotatable shutter 18 are both coupled to the rotatable shaft 8. The fluid conduits 58, 60, 62 of the first and second rotatable shutters 16, 18 provide a first A, a second C, D and a third B, E angular intervals of rotation A of the shaft 8 to selectively control the flow of fluid through the first and/or second chambers depending on the rotation of the shaft.

Description

(54) Title of the Invention: Multiple 5 temperature level rotary valve Abstract Title: Rotary valve (57) A rotary valve 2 comprises a rotatable shaft 8 extending into a first chamber 10 and a second chamber 12. The first chamber 10 has a fluid outlet port 20, a first inlet port 42 and a second inlet port 46. The second chamber 12 has a fluid outlet port 22 and an inlet port 52. The first chamber 10 has a first rotatable shutter 16 provided with fluid conduits 58, 60. The second chamber 12 has a second rotatable shutter 18 provided with at least a fluid conduit 62. The first rotatable shutter 16 and the second rotatable shutter 18 are both coupled to the rotatable shaft 8. The fluid conduits 58, 60, 62 of the first and second rotatable shutters 16, 18 provide a first A, a second C, D and a third B, E angular intervals of rotation A of the shaft 8 to selectively control the flow of fluid through the first and/or second chambers depending on the rotation of the shaft.

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FIG.l

FIG.2

145

2/8

m

Fig. 3

3/8

4/8

5/8

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Fig. 6

6/8

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7/8

Ο

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8/8

500

Fig. 9

Intellectual

Property

Office

Application No. GB1612544.5

RTM

Date :3 November 2016

The following terms are registered trade marks and should be read as such wherever they occur in this document:

WiFi

Intellectual Property Office is an operating name of the Patent Office www.gov.uk/ipo

MULTIPLE TEMPERATURE LEVEL ROTARY VALVE

TECHNICAL FIELD

The technical field relates to automotive technology and in particular to the cooling of an internal combustion engine which can be used in an automotive system. More in detail, the technical field relates to rotary valves intended to selectively control the fluid flow in a cooling system for an internal combustion engine.

BACKGROUND

Various engines for automobiles and other motor vehicles utilize a cooling system wherein a coolant is circulated, usually by means of a coolant pump so as to reach various engine components, thus maintain the temperature within acceptable limits.

Known cooling systems for an internal combustion engine are also provided with one or more heat exchanger, e.g. a radiator, wherein the coolant exchange thermal energy with another fluid, such as for example ambient air.

In known cooling system the circulation of the coolant is advantageously controlled depending on the engine operating conditions. For example, during warm-up of the engine, coolant is generally not needed to be provided to the radiator, so as to reduce the warm-up time by avoiding thermal exchange with the ambient air, but coolant should desirably be provided to the radiator during normal operation. Further, when an engine reaches a high temperature, additional coolant fluid should desirably be delivered to the radiator or other component requiring cooling.

In today’s advancing automotive technology, engines include various other components such as oil heat exchangers and other devices that operate at high temperatures, and these components also require cooling. The coolant fluid is generally delivered to the component requiring cooling and, in general its circulation is controlled, by a valve and an associated actuator. The valve may be a rotary valve that includes a single chamber through which coolant passes when the valve is opened, and the actuator generally includes an associated controller. The rotary valve allows only for a single coolant fluid at a single temperature, to be delivered to the desired component. In engines in which multiple components require cooling, and in general in cooling system aiming at controlling the coolant flow in different branches of the cooling system, a valve with an associated actuator has to be provided for each component and/or for each branches. This means that each valve requires a separate control and therefore separate wiring. As engines increase in performance and complexity, they tend to include multiple components to which coolant has to be selectively delivered. This requires the utilization of multiple valves, multiple actuators. This also requires additional wiring as each actuator and controller must be separately wired.

Valve modules having two fluidically separated chambers are also known, see for example document WO2015/013273. Even if this valve module allows to control fluid flow in two separate chambers while simplify the wiring by possibly allowing the use of one actuator, there is still the need of improving the desired control of the coolant through the chambers of the valve so as to effectively supply it to multiple components of the engine and/or of the cooling system. SUMMARY

These and other objects are achieved by a rotary valve according to embodiments of the disclosure as defined in the independent claim. The dependent claims include preferred and/or advantageous aspects and features. According to another aspect, a cooling system for an internal combustion engine is provided.

In particular, disclosed is a rotary valve comprising:

a rotatable shaft extending at least into a plurality of chambers including a first chamber and a second chamber, said first chamber having a fluid outlet port, a first inlet port and a second inlet port, said second chamber having a fluid outlet port and an inlet port, the first chamber having therein a first rotatable shutter provided with coolant conduits, the second chamber having therein a second rotatable shutter provided with at least a coolant conduit, the first rotatable shutter and the second rotatable shutter being both coupled to said rotatable shaft, wherein the coolant conduits of the first and second rotatable shutters are configured in such a way that:

- in a first angular interval of rotation of the shaft, fluid passage between the inlet ports and the outlet port of the first chamber and between the inlet port and the outlet port of the second chamber is inhibited,

- in a second angular interval of rotation of the shaft, at least one of the coolant conduits of the first rotatable shutter allows fluid passage between at least one of the inlet ports and the outlet port of the first chamber and the coolant conduit of the second rotatable shutter allows fluid passage between the inlet port and the outlet port of the second chamber, and

- in a third angular interval of rotation of the shaft, at least one of the coolant conduits of the first rotatable shutter allows fluid passage between at least one of the inlet ports and the outlet port of the first chamber and fluid passage between the inlet port and the outlet port of the second chamber is inhibited.

An advantage of the above embodiment is that a single actuator can be used to control the coolant flow for a multiplicity of functions, for example for the radiator and for the oil heat exchanger. Additionally, the opening/closure characteristic over the shutters positions according to the first, second and third angular interval of rotation of the shaft allow to improve the fluid control through the first and second chambers. In fact, in the second and third angular intervals not only allow to control the coolant flow from the first and/or secondo inlet of the first chamber, but at the same time allows to control the coolant flow through the second chamber.

By doing so, a desired thermal control strategy can be obtained, thus providing coolant to different components such as for example an oil heat exchanger connected to the outlet of the first chamber and a coolant radiator connected to the outlet of the second chamber.

Advantageously, the second angular interval allows to provide coolant from a first inlet port (e.g. connect to a hot coolant source) or coolant from the second inlet port (e.g. connected to a cold coolant source) to the oil heat exchanger connected to the outlet of the first chamber, while the fluid flow through the second chamber (e.g. coolant flow to the radiator) is prevented.

Advantageously, the third angular interval allows to provide coolant from a first inlet port (e.g. connect to a hot coolant source) or coolant from the second inlet port (e.g. connected to a cold coolant source) to the oil heat exchanger connected to the outlet of the first chamber, while the fluid flow through the second chamber (e.g. coolant flow to the radiator) is also allowed.

According to an embodiment, the second angular interval of rotation of the shaft comprises a first sub-interval in which a first coolant conduit of the first rotatable shutter allows fluid passage between the first inlet port and the outlet port of the first chamber and the coolant conduit of the second rotatable shutter allows fluid passage between the inlet port and the outlet port of the second chamber providing the advantage of additional versatility.

According to another embodiment, the second angular interval of rotation of the shaft comprises a second sub-interval in which a second coolant conduit of the first rotatable shutter allows fluid passage between the first inlet port and the outlet port of the first chamber and the coolant conduit of the second rotatable shutter allows fluid passage between the inlet port and the outlet port of the second chamber. This advantageously provides for different fluid paths through a chamber depending on the position of the rotatable shutters and the conduits.

According to another embodiment, the third angular interval of rotation of the shaft comprises a third sub-interval in which a first coolant conduit of the first rotatable shutter allows fluid passage between the first inlet port and fluid passage between the inlet port and the outlet port of the second chamber is inhibited, providing one advantageous use of the valve.

According to another embodiment, the third angular interval of rotation of the shaft comprises a fourth sub-interval in which a second coolant conduit of the first rotatable shutter allows fluid passage between the first inlet port and the outlet port of the first chamber and the outlet port of the second chamber is inhibited.

According to another embodiment, the first and second sub-interval are not adjacent.

According to another embodiment, the third and fourth sub-interval are not adjacent.

According to another embodiment, the coolant conduit of the second rotatable shutter is positioned in such a way as to make only a portion of coolant conduit coincident with the outlet port of the second chamber.

An advantage of this embodiment is that the volume of flow passing through the respective chamber of the valve, i.e, flow rate, is controlled.

Also disclosed is a cooling system that comprises at least one rotary valve. The disclosed cooling system provides the advantage that a single valve is used to provide coolants at different temperatures to various engine components.

According to an embodiment, the valve is in fluid communication with an oil heat exchanger and also in fluid communication with a radiator and provides the advantage that a single valve has different chambers that are in fluid communication with different components of the cooling system. This provides the advantage that a single valve is used to provide coolants to various engine components.

According to an embodiment, the different inlet coolant sources are at different temperatures to advantageously provide coolants of different temperatures to different engine components.

A method of operating a cooling system for an internal combustion engine is also disclosed, the method comprising the steps of selectively rotating the rotatable shaft of the valve to selectively carry out one or more phase of:

- oil heating by allowing a fluid flow from the first fluid source through the first inlet port and the outlet port of the first chamber towards the oil heat exchanger and inhibiting fluid flow between the inlet port and the outlet port of the second chamber;

- selectively controlling oil heating by allowing a fluid flow from the first fluid source through the first inlet port and the outlet port of the first chamber towards the oil heat exchanger and allowing or preventing fluid flow between the inlet port and the outlet port of the second chamber towards the radiator or selectively controlling oil cooling by allowing a fluid flow from the second fluid source through the second inlet port and outlet port of the first chamber towards the oil heat exchanger and allowing or preventing fluid flow between the inlet port and the outlet port of the second chamber towards the radiator;

- oil cooling by allowing a fluid flow from the first fluid source through the first inlet port and the outlet port of the first chamber towards the oil heat exchanger and allowing fluid flow between the inlet port and the outlet port of the second chamber towards the radiator.

BRIEF DESCRIPTION OF THE DRAWINGS

Other features, advantages and details appear, by way of example only, in the following detailed description of embodiments, with reference to the accompanying drawings, in which:

Figure 1 schematically shows an automotive system belonging to a motor vehicle;

Figure 2 is the section A-A of an internal combustion engine belonging to the automotive system of Figure 1;

Figure 3 shows a schematic view of the rotary valve according to an embodiment and an associated plan view of the shutters of the rotary valve, i.e. a view wherein the external shutter surface is shown in a plan along its complete extension between 0 and 360 degrees;

Figure 4 shows the rotary valve of Figure 3 in a first operating position;

Figure 5 shows the rotary valve of Figure 3 in another operating position;

Figure 6 shows the rotary valve of Figure 3 in another operating position;

Figure 7 shows the rotary valve of Figure 3 in yet another operating position;

Figure 8 shows the rotary valve of Figure 3 in still another operating position;

Figure 9 is a schematic showing a block diagram of a cooling assembly according to various embodiments of the disclosure.

DETAILED DESCRIPTION

Exemplary embodiments will now be described with reference to the enclosed drawings without intent to limit application and uses.

The disclosure provides a rotary valve that can be operated by an actuator and multiple chambers. A single rotary valve and actuator controls the delivery of multiple fluids which may be at multiple temperature levels, to multiple components such as within an automotive engine. More particularly, the disclosure provides for selectively controlling the delivery of multiple coolants from different fluid sources to desired components such as within an automotive engine, through a single rotary valve operated by a single actuator.

The automotive system shown in Figures 1 and 2, is presented by way of example only and the rotary valve embodiments of the present disclosure may find application in various environments including but not limited to the automotive system application described below.

Some embodiments may include an automotive system 100, as shown in Figures 1 and 2, that includes an internal combustion engine (ICE) 110 having an engine block 120 defining at least one cylinder 125 having a piston 140 coupled to rotate a crankshaft 145. A cylinder head 130 cooperates with the piston 140 to define a combustion chamber 150.

A fuel and air mixture (not shown) is disposed in the combustion chamber 150 and ignited, resulting in hot expanding exhaust gasses causing reciprocal movement of the piston 140.

The fuel is provided by at least one fuel injector 160 and the air through at least one intake port 210. The fuel is provided at high pressure to the fuel injector 160 from a fuel rail 170 in fluid communication with a high pressure fuel pump 180 that increase the pressure of the fuel received from a fuel source 190. Each of the cylinders 125 has at least two valves 215, actuated by a camshaft 135 rotating in time with the crankshaft 145. The valves 215 selectively allow air to flow into the combustion chamber 150 from the port 210 and alternately allow exhaust gases to exit through a port 220. In some examples, a cam phaser 155 may selectively vary the timing between the camshaft 135 and the crankshaft 145.

^r The air may be distributed to the air intake port(s) 210 through an intake manifold 200. An air intake duct 205 may provide air from the ambient environment to the intake manifold 200. In other embodiments, a throttle body 330 may be provided to regulate the flow of air into the manifold 200. In still other embodiments, a forced air system such as a turbocharger 230, having a compressor 240 rotationally coupled to a turbine 250, may be provided. Rotation of the compressor 240 increases the pressure and temperature ofthe air in the duct 205 and manifold 200. An intercooler 260 disposed in the duct 205 may reduce the temperature of the air. The turbine 250 rotates by receiving exhaust gases from an exhaust manifold 225 that directs exhaust gases from the exhaust ports 220 and through a series of vanes prior to expansion through the turbine 250. This example shows a variable geometry turbine (VGT) with a VGT actuator 290 arranged to move the vanes to alter the flow of the exhaust gases through the turbine 250. In other embodiments, the turbocharger 230 may be fixed geometry and/or include a waste gate.

The exhaust gases exit the turbine 250 and are directed into an exhaust system 270. The exhaust system 270 may include an exhaust pipe 275 having one or more exhaust after treatment devices 280. The after treatment devices may be any device configured to change the composition of the exhaust gases. Some examples of after treatment devices 280 include, but are not limited to, catalytic converters (two and three way), oxidation catalysts, lean NOx traps, hydrocarbon adsorbers, selective catalytic reduction (SCR) systems, and particulate filters. Other embodiments may include an exhaust gas recirculation (EGR) system 300 coupled between the exhaust manifold 225 and the intake manifold 200. The EGR system 300 may include an EGR cooler 310 to reduce the temperature of the exhaust gases in the EGR system 300. An EGR valve 320 regulates a flow of exhaust gases in the EGR system 300.

The automotive system 100 may further include an electronic control unit (ECU) 450 in communication with one or more sensors and/or devices associated with the ICE 110. The ECU 450 may receive input signals from various sensors configured to generate the signals in proportion to various physical parameters associated with the ICE 110. The sensors include, but are not limited to, a mass airflow and temperature sensor 340, a manifold pressure and temperature sensor 350, a combustion pressure sensor 360, coolant and oil temperature and level sensors 380, a fuel rail pressure sensor 400, a cam position sensor 410, a crank position sensor 420, exhaust sensors 430 for detecting e.g. temperature, pressure, composition of exhaust gases, an EGR temperature sensor 440, and an accelerator pedal position sensor 445. Furthermore, the ECU 450 may generate output signals to various control devices that are arranged to control the operation ofthe ICE 110, including, but not limited to, the fuel injectors 160, the throttle body 330, the EGR valve 320, the VGT actuator 290, and cam phaser 155. Note, dashed lines are used to indicate communication between the ECU 450 and the various sensors and devices, but some are omitted for clarity.

Turning now to the ECU 450, this apparatus may include a digital central processing unit (CPU) in communication with a memory system and an interface bus. The CPU is configured to execute instructions stored as a program in the memory system 460, and send and receive signals to/from the interface bus. The memory system 460 may include various storage types including optical storage, magnetic storage, solid state storage, and other non-volatile memory. The interface bus may be configured to send, receive, and modulate analog and/or digital signals to/from the various sensors and control devices.

The program may embody the methods disclosed herein, allowing the CPU to carryout out the steps of such methods and control the ICE 110.

The program stored in the memory system 460 is transmitted from outside via a cable or in a wireless fashion. Outside the automotive system 100 it is normally visible as a computer program product, which is also called computer readable medium or machine readable medium in the art, and which should be understood to be a computer program code residing on a carrier, said carrier being transitory or non-transitory in nature with the consequence that the computer program product can be regarded to be transitory or non-transitory in nature.

An example of a transitory computer program product is a signal, e.g. an electromagnetic signal such as an optical signal, which is a transitory carrier for the computer program code. Carrying such computer program code can be achieved by modulating the signal by a conventional modulation technique such as QPSK for digital data, such that binary data representing said computer program code is impressed on the transitory electromagnetic signal. Such signals are e.g. made use of when transmitting computer program code in a wireless fashion via a WiFi connection to a laptop.

In case of a non-transitory computer program product the computer program code is embodied in a tangible storage medium. The storage medium is then the non-transitory carrier mentioned above, such that the computer program code is permanently or non-permanently stored in a retrievable way in or on this storage medium. The storage medium can be of conventional type known in computer technology such as a flash memory, an Asic, a CD or the like.

Now turning to the other figures, Figure 3 shows a possible embodiment of the rotary valve. The disclosure provides for selectively delivering fluids from multiple sources through rotary valve 2 and to one or more desired engine components with which rotary valve 2 is in fluid communication. The multiple coolants, may be at different temperature levels and therefore the rotary valve delivers fluids at multiple temperature levels. It has to be noted that the expression multiple coolants, or different coolants, is also used to indicate a coolant provided by different parts or area of the cooling system, which therefore can be provided with different temperatures depending on the temperature of the coolant at said part or area of the cooling system from which the coolant is taken and then supplied to the inlet(s) of the rotary valve.

Rotary valve 2 is associated with actuator 4 intended to operate a shaft 8 of the valve that extends through first chamber 10 and into second chamber 12. Figure 3 shows that shaft 8 extends completely through first chamber 10 and into second chamber 12 but in other embodiments, shaft 8 may extend completely through each of first chamber 10 and second chamber 12. Each of first chamber 10 and second chamber 12 is provided with a rotatable shutter coupled to shaft 8, and which may be rotated by actuator 4 which is coupled to shaft 8. In some embodiments, the rotatable shutter may be a rotary slider, as for example shown in the figure, i.e. hollow cylindrical body. Actuator 4 has an associated controller, not shown in the figures, and the controller and actuator 4 have dedicated wiring.

First chamber 10 is provided with a rotatable shutter hereinafter referred to as first rotatable shutter 16. First rotatable shutter 16 is coupled to shaft 8 and second chamber 12 is provided with a rotatable shutter hereinafter referred to as second rotatable shutter 18, also coupled to shaft 8. Each of first rotatable shutter 16 and second rotatable shutter 18 are components internal to first chamber 10 and second chamber 12, respectively. First chamber 10 comprises first outlet port 20 and second chamber 12 comprises second outlet port 22. First outlet port 20 is defined by an opening in wall 24 of first chamber 10 and second outlet port 22 is defined by an opening in wall 26 of second chamber 12. First outlet port 20 enables coolant flow 30 to be delivered to first component 32 and second outlet port 22 enables coolant flow 38 to be delivered to second component 40. First chamber 10 is therefore in fluid communication with first component 32 and second chamber 12 is therefore in fluid communication with second component 40. First component 32 and second component 40 may represent any of the various components that require cooling or which utilize a coolant fluid for heat exchange for other purposes. In some embodiments, first component 32 may be an oil heat exchanger and second component 40 may be a radiator but other components may have coolant 38 and 30 delivered to them according to other embodiments.

According to an embodiment, first chamber 10 comprises two inlet ports. First inlet port 42 allows for the entry of a first coolant or other fluid, as indicated by the flow arrow 44, from first fluid source 45 and second inlet port 46 allows for the entry of a second coolant fluid from second fluid source 47 (or the same coolant coming from another area or part of the cooling circuit), as indicated by associated flow arrow 48. For brevity, the inlet fluid flows are hereinafter referred to as first coolant fluid flow 44 and second coolant fluid flow 48. Second chamber 12 comprises inlet port 52 that enables the delivery of a coolant fluid as indicated by associated flow arrow 54 such as may be from third fluid source 55. Fluid sources including first fluid source 45, second fluid source 47 and third fluid source 55 may represent various different components of an engine or various fluids reservoirs or containers, or part of area of the cooling circuit and each of the fluids provided by the respective fluid sources, may be coolants, as will be referred to hereinafter, but as already mentioned above, the sources can be different parts or different area of the same coolant circuit. In some embodiments, the coolants of first coolant fluid flow 44 and second coolant fluid flow 48 are different coolants. In some embodiments, the coolants of first coolant fluid flow 44 and second coolant fluid flow 48 are at different temperatures.

According to an embodiment, the first fluid source 45 provides coolant at high temperature and is for example a part or area of cooling circuit close to the exhaust gas manifold or conduit of the engine, the second fluid source 47 provides coolant at low temperature and is for example a part or area of cooling circuit at the output of the coolant pump, and third fluid source 55 provides coolant at medium temperature and is for example a part or area of cooling circuit at the cylinder head.

Coolant fluid flow 54 may be the same or different coolant material as first coolant fluid flow 44 or second coolant fluid flow 48 and each of the coolant fluids may be at different temperatures according to various embodiments. One advantage of the present disclosure is that different coolant fluid and/or coolants at different temperatures may be delivered through first chamber 10 of rotary valve 2. Another advantageous aspect according to the disclosure is that a single rotary valve along with a single actuator and controller (not shown) provide for the delivery of different coolants and or coolants at different temperatures, to different engine parts,

i.e. to first component 32 and second component 40, through multiple chambers. Multiple valves are not required, nor are multiple actuators and controllers with associated wiring. In some embodiments, first inlet port 42 and second inlet port 46 are each formed by a circular or other opening in wall 24 of first chamber 10 and inlet port 52 is formed by a circular or other opening in wall 26 of second chamber 10.

One or both of first rotatable shutter 16 and second rotatable shutter 18 may rotate about shaft 8 as indicated by arrow 36. In various embodiments, first rotatable shutter 16 and second rotatable shutter 18 are fixed to shaft 8 and rotate in unison.

Aspects of first rotatable shutter 16 and second rotatable shutter 18 are for example shown on the left-hand side of the Figures 3-8 showing the lateral surface 68 of the shutter in plane (i.e. the circular surface of the shutter is shown in plane). First rotatable shutter 16 comprises two conduits, including first coolant conduit 58 and second coolant conduit 60. Second rotatable shutter 18 comprises conduit 62. Conduits 58, 60, 62 comprises a passagway or opening on the surface 68 of the shutter, as for example shown in the left-hand view of the figures 3-8.

The rectangular cross-sectional shape of the opening provided on the surface 68 of the shutter of the first and second coolant conduits 58 and 60 and the hexagonal cross-sectional shape the opening provided on the surface 68 of the shutter of conduit 62 are rather arbitrary and represent only a particular cross-section of the conduit which may change shape and include other configurations as it extends through the respective rotatable shutter. In some embodiments, the conduits extend straight through the associated rotatable shutter and in other embodiments, the conduits may have an arcuate or other shape such that fluid entering the conduit and the associated rotatable shutter in one direction may exit the associated rotatable shutter in a different flow direction, such as indicated by flow direction arrows 64 and 66. For example, fluid entering second chamber 12 as coolant fluid flow 54 enters second chamber 12 in a vertical direction according to the configuration of Figure 1 but then exits second chamber 12 as coolant flow 38, in a horizontal direction. Fluid enters the associated chamber 10, 12 through the indicated inlet port and exits through the indicated first and second outlet ports and may flow through and/or around the associated rotatable shutter 16, 18, in various embodiments. For example, in some embodiments, coolant flow enters second chamber 12 as coolant fluid flow 54 and exits at second outlet port 22 but may enter conduit 62 of second rotatable shutter 18 at various locations within second chamber 12.

First rotatable shutter 16 allows and prevents, i.e. controls, fluid flow of first coolant fluid 44 from first inlet port 42 through first coolant conduit 58 and first outlet port 20 of first chamber 10, so as to be delivered as coolant flow 30 to first component 32. First rotatable shutter 16 also allows and prevents, i.e. controls, fluid flow of second coolant fluid 48 from second inlet port 46 through second coolant conduit 60 and second outlet port 22 of first chamber 10, so as to be delivered as coolant flow 30 to first component 32. Second rotatable shutter 18 allows and prevents, i.e. controls, fluid flow of coolant flow 54 from inlet port 52 through second outlet port 22 of second chamber 12, so as to be delivered as coolant flow 38 to second component 40.

First rotatable shutter 16 and second rotatable shutter 18 of rotary valve 2 are designed such that various rotational positions of shaft 8 provide for various flow configurations. In various embodiments, first rotatable shutter 16 and second rotatable shutter 18 are configured such that the respective conduits 58, 60, 62 are arranged such that full or partial flow occurs through one or multiple conduits.

It should be understood that, in other embodiments, rotatable shutters 16, 18 may have different features other than the illustrated conduits, that enable flow through the chamber depending on the position of the respective rotatable shutter 16, 18. Depending on the design of the respective rotatable shutter 16, 18, fluid flow may take place through the rotatable shutter or around the rotatable shutter within the respective chamber.

Furthermore, it is to be noted that in Figure 3 (and in the subsequent Figures 4-8) the lateral surface 68 of the shutter in plane (i.e. the circular surface of the shutter is shown in plane) has been subdivided in a plurality of angular intervals A-E which will be better described in the following description.

In general, it can be observed a first angular interval of rotation A of the shaft 8, a second angular interval of rotation C,D of the shaft 8 wherein such second angular interval of rotation can be further subdivided in a first sub-interval C and a second sub-interval D and a third angular interval of rotation B, E of the shaft 8, wherein such third angular interval of rotation can be further subdivided in a third sub-interval B and a fourth sub-interval E.

In general, the first and second sub-intervals C and D may be not adjacent.

With the wording “not adjacent” in this context it is intended that in order to pass from a certain sub-interval to another non-adjacent sub-interval there may be necessity of rotating the shaft 8 of a certain of rotation spanning an angle of rotation that does not belong to any of the non-adjacent sub-intervals.

Also, the third and fourth sub-intervals B, E may be not adjacent.

Figure 4 illustrates a possible operating position, i.e. a particular configuration of the rotary valve 2 shown in Figure 3. In Figure 4, first rotatable shutter 16 and second rotatable shutter 18 are positioned by actuator 4, such that no flow goes through rotary valve 2. In the exemplary configuration shown in Figure 4, first coolant conduit 58 is not aligned with first inlet port 42 and second coolant conduit 60 is not aligned with second inlet port 46. As such, the “X’s” covering flow arrows associated with first coolant fluid flow 44 and second coolant fluid flow 48 indicate that no flow occurs at these locations because there is no open fluid flow path through first chamber 10. It should be understood that first coolant fluid flow 44, is coupled to first fluid source 45 as shown in Figure 3. Similarly, second coolant fluid flow 48, as indicated by flow arrow, is coupled to second fluid source 47, and coolant fluid flow 54 is also coupled to third fluid source 55 as shown in Figure 3, and this is true in Figure 4 and throughout the subsequent figures. Each of first fluid source 45, a second fluid source 47, and third fluid source 55, may be a coolant. In this illustrated configuration, first coolant conduit 58 terminates at wall 24 of first chamber 10 as does second coolant conduit 60. In other words, flow cannot take place through first coolant conduit 58 or second coolant conduit 60. Figure 4 also illustrates no flow as indicated by the “X” over flow arrow identifying coolant fluid flow 54. This is because, in the illustrated arrangement, conduit 56 is not aligned with second outlet port 22 but rather terminates at wall 26 of second chamber 12 and this arrangement blocks any flow through second chamber 12. Although first inlet port 42, second inlet port 46 and second outlet port 22 appear as circular openings in the illustrated embodiments such as on the left-hand side of Figure 4, these features may take on other shapes in other embodiments and are advantageously designed in conjunction with the respective conduits 58, 60, 62. According to the arrangement of Figure 4, no fluid flow takes place through rotary valve 2.

In other words, the coolant conduits 58,60,62 of the first and second rotatable shutters 16,18 respectively are configured in such a way that in a first angular interval of rotation A of the shaft 8, fluid passage between the inlet ports 42,46 and the outlet port 20 of the first chamber 10 and between the inlet port 52 and the outlet port 22 of the second chamber 12 is inhibited.

Figure 5 shows an arrangement in which fluid flow takes place through first chamber 10 but not through second chamber 12. Actuator 4 provides a shaft 8 position in which first rotatable shutter 16 is positioned to allow flow of first coolant fluid flow 44 through first inlet port 42, first coolant conduit 58 and through first outlet port 20 as indicated by coolant flow 30, delivered to first component 32. As indicated by the “X” over flow arrow associated with second coolant fluid flow 48, fluid flow does not take place through second inlet port 46, i.e. there is no open fluid flow path from second inlet port 46 through first chamber 10 and to first outlet port 20. This is because, as indicated on the left-hand side of Figure 5, first coolant conduit 58 is aligned with first inlet port 42 to produce an open fluid flow path, but second coolant 60 is not aligned with second inlet port 46, thus blocking flow through second inlet port 46. In this arrangement, rotary valve 2 only delivers coolant flow 30 which enters first chamber 10 at first inlet port 42. Due to the position of second rotatable shutter 18 in this shaft 8 position, no flow takes place through second chamber 12 because conduit 62 is not configured to allow fluid flow through second outlet port 22. Figure 5 shows an advantage of the present disclosure in that the design of first rotatable shutter 16 is such that it can selectively allow for flow from only one of the inlet ports (from only one of first inlet port 42 and second inlet port 46), through first chamber 10. The twochamber design advantageously provides for the selective flow through first chamber 10 to take place without an associated flow through second chamber 12.

Also in Figure 5, flow through the second fluid outlet port 22 is blocked.

In other words, the third angular interval of rotation B,E of the shaft 8 comprises a third subinterval B in which a first coolant conduit 58 of the first rotatable shutter 16 allows fluid passage between the first inlet port 42 and fluid passage between the inlet port 52 and the outlet port 22 of the second chamber 12 is inhibited. This angular position of the shutter can be advantageously used for example during the warm-up phase of the engine to quickly and effectively heating the lubrication oil by allowing a fluid flow from the first fluid source 45, that has mentioned above is preferably a source of hot coolant, through the first inlet port 42 and the outlet port 20 of the first chamber 10 towards the oil heat exchanger 32 connected to the outlet port 20. At the same time, fluid flow between the inlet port 52 and the outlet port 22 of the second chamber 1.2 is prevented.

The two chamber design also provides for selective flow through first chamber 10 and also with associated flow through second chamber 12, as shown in Figure 6.

Figure 6 shows a shaft 8 position providing another arrangement in which rotary valve 2 provides for the delivery of coolant flow 30 to first component 32 and the simultaneous delivery of coolant flow 38 to second component 40. The delivery of first coolant fluid flow 44, takes place through first chamber 10. First coolant fluid flow 44, enters first chamber 10 at first inlet port 42, continues through first conduit 58 and exits first chamber 10 through first outlet port 20 and is delivered as coolant flow 30 to first component 32. As in Figure 5, the X over the flow arrow associated with second coolant fluid flow 48 indicate that coolant flow does not take place through second inlet port 46. The arrangement of Figure 6 also shows partial flow through second chamber 12. The partial flow is achieved because only portion of conduit 62 is coincident with second outlet port 22 and therefore only a portion of the maximum flow through second rotatable shutter 18 is achieved. Stated alternatively, second outlet port 22 is exposed to a portion of conduit 62 and also a portion of a surface 68 of second rotatable shutter 18. In this manner, the volume of flow passing through the respective chambers of the valve, i.e, flow rate, is controlled.

Figure 6 shows multiple representations of first inlet port 42, second inlet port 46 and second outlet port 22 to represent the various relative positions of moveable first rotatable shutter 16 and moveable second rotatable shutter 18. According to various embodiments, actuator 4 causes shaft 8 to rotate to position the first and second rotatable shutters in the various positions shown in Figure 6.

The outlet flows shown in Figure 6, i.e. coolant flow 30 and coolant flow 38, are associated with the position indicated by the solid representations of first inlet port 42, second inlet port 46 and second outlet port 22. In Figure 6, each of the positions of first inlet port 42 with respect to the movable first rotatable shutter 16, indicated by the solid and dashed lines, allows for flow through first inlet port 42 and each of the positions of second inlet port 46, also indicated by solid and dashed lines, prevents flow from taking place as indicated by the “X” over flow arrow associated with second coolant fluid flow 48. Regarding second rotatable shutter 18, the positions of second rotatable shutter 18 respect to second outlet port 22, as indicated by the three representations of outlet port 22, indicate a partial flow takes place for the center and right relative positions (corresponding to sub-interval C), whereas the left-most relative position (corresponding to sub-interval B) of second outlet port 22 with respect to second rotary shaft 18, shown in dashed lines, provides for essentially no flow through second chamber 12 as there is virtually no overlap between conduit 62 and second outlet port 22.

In other words, in figure 6 are shown possible positions of the shutters, according to angular interval B and according to sub-interval C of the second angular interval of rotation of the shaft 8 in which a first coolant conduit 58 of the first rotatable shutter 16 allows fluid passage between the first inlet port 42 and the outlet port 20 of the first chamber 10 and the coolant conduit 62 of the second rotatable shutter 18 allows fluid passage between the inlet port 52 and the outlet port 22 of the second chamber 12. The positions shown in Figure 6, according to intervals B and C, can be used to selectively control oil heating by allowing a fluid flow from the first fluid source 45 (that as mentioned above is preferably a hot coolant source) through the first inlet port 42 and the outlet port 20 of the first chamber 10 towards the oil heat exchanger 32 and allowing or preventing (according to angular interval C or B) fluid flow between the inlet port 52 and the outlet port 22 of the second chamber 12 towards the radiator 40. It has to be noted that the difference between angular interval C and B is that the in interval B the fluid flow through the second chamber, e.g. to the to the radiator is prevented.

Figure 7 shows another arrangement in which coolant fluid is simultaneously delivered through both chambers. Figure 7 shows shaft 8 position represented by the solid representations of first inlet port 42, second inlet port 46 and second outlet port 22. The dashed line representations of these features represent other relative positions that may be achieved.

According to this arrangement, coolant flow 30 is delivered by rotary valve 2 through first chamber 10, as received from second coolant fluid flow 48 entering first chamber 10 at second inlet port 46 as indicated by the flow arrow, and in in which no first coolant flow takes place at first inlet port 42, as indicated by the “X” over the flow arrow associated with first coolant fluid flow 44. Coolant flow 38 is a partial flow delivered from second chamber 12, due to the relative position of second rotatable shutter 18 with respect to the second outlet port 22, as indicated by the solid representation of second outlet port 22. When conduit 62 of second rotatable shutter 18 is positioned with respect to second outlet port 22 as indicated by the dashed line representation of outlet port 22 on the right-hand side of the drawing, no flow takes place (corresponding to angular interval E). When conduit 62 of second rotatable shutter 18 is positioned with respect to second outlet port 22 as indicated by the dashed line representation of second outlet port 22 on the left-hand side of the drawing (corresponding to angular interval D), a full coolant flow 38 is achieved. Each of the positions of Figure 7 shows a portion of conduit 62 overlapping second outlet port 22.

In other words, in figure 7 are shown possible positions of the shutters, according to angular interval E and according to sub-interval D of the second angular interval of rotation of the shaft 8 in which a second coolant conduit 60 of the first rotatable shutter 16 allows fluid passage between the first inlet port 42 and the outlet port 20 of the first chamber 10 and the coolant conduit 62 of the second rotatable shutter 18 allows fluid passage between the inlet port 52 and the outlet port 22 of the second chamber 12.

The positions shown in Figure 7, according to angular intervals E and D, can be used to selectively control oil cooling by allowing a fluid flow from the second fluid source 47 (that as mentioned above is preferably a cold coolant source) through the second inlet port 46 and outlet port 20 of the first chamber 10 towards the oil heat exchanger 32 and allowing or preventing (according to angular interval D or E) fluid flow between the inlet port 52 and the outlet port 22 of the second chamber 12 towards the radiator 40. It has to be noted that the difference between angular interval E and D is that the in interval E the fluid flow through the second chamber, e.g. to the to the radiator is prevented. In fact, in the fourth sub-interval E, the second coolant conduit 60 of the first rotatable shutter 16 allows fluid passage between the first inlet port 42 and the outlet port 20 of the first chamber 10 and the outlet port 22 of the second chamber 12 is inhibited.

Figure 8 shows a shaft 8 arrangement in which no flow of first coolant fluid takes place at inlet port 42 (according to angular interval D) as indicated by the X over the flow arrow associated with first coolant fluid flow 44, and in which second coolant fluid flow 48 is delivered through second inlet port 46. This is produced because first inlet port 42 is not aligned with first coolant conduit 56 whereas second inlet port 46 is aligned over second coolant conduit 60 providing for full coolant flow through second inlet port 46. Figure 8 also indicates that coolant flow 38 is delivered from second outlet port 22 because of the arrangement and relative positions of conduit 62 and second outlet port 22.

It should be understood that various other arrangements to allow full or partial flow through either or both of first chamber 10 and second chamber 12 can be used in other embodiments. In other words, the positions of first coolant conduit 58, second coolant conduit 60 and coolant conduit 62 may vary with respect to one another, in other embodiments.

This position, according to angular interval D can be for example used when there is the need of maximum cooling of both the oil via the oil heat exchanger 32 and coolant via the radiator 40. In this position, fluid flow from the first fluid source 45 (that as mentioned above is preferably a cold coolant source) through the first inlet port 42 and the outlet port 20 of the first chamber 10 towards the oil heat exchanger is provided, and fluid flow between the inlet port 52 and the outlet port 22 of the second chamber 12 towards the radiator 40 is also provided.

Figure 9 is a schematic showing a block diagram of a cooling system according to various embodiments of the disclosure. Figure 9 shows cooling system 500 for an internal combustion engine such as the internal combustion engine 110 shown above although cooling system 500 may be used in conjunction with other engines in other embodiments. According to an embodiment, cooling system 500 comprises rotary valve 2 as described above and rotary valve 2 is coupled to first fluid source 45, second fluid source 47 and third fluid source 55 as well as first component 32 and second component 40. Each of these features is as described above.

While at least one exemplary embodiment has been presented in the foregoing summary and detailed description, it should be appreciated that a vast number of variations exist. It should also be appreciated that the exemplary embodiment or exemplary embodiments are only examples, and are not intended to limit the scope, applicability, or configuration in any way. Rather, the foregoing summary and detailed description will provide those skilled in the art with a convenient road map for implementing at least one exemplary embodiment, it being understood that various changes may be made in the function and arrangement of elements described in an exemplary embodiment without departing from the scope as set forth in the appended claims and their legal equivalents.

REFERENCE NUMBERS rotary valve actuator shaft first chamber second chamber first rotatable shutter second rotatable shutter first outlet port second outlet port wall wall coolant flow first component rotation direction coolant fluid flow second component first inlet port first coolant fluid flow first fluid source second inlet port second fluid source second coolant fluid flow inlet port coolant fluid flow third fluid source first coolant conduit second coolant conduit coolant conduit flow direction flow direction shutter surface automotive system internal combustion engine engine block cylinder cylinder head camshaft piston crankshaft combustion chamber cam phaser fuel injector fuel rail fuel pump fuel source intake manifold air intake pipe intake port valves exhaust port exhaust manifold turbocharger compressor turbine intercooler exhaust system exhaust pipe exhaust aftertreatment device

VGT actuator

EGR system

EGR cooler

EGR valve throttle body mass airflow and temperature sensor manifold pressure and temperature sensor combustion pressure sensor coolant and oil temperature and level sensors fuel rail pressure sensor cam position sensor crank position sensor exhaust sensors

EGR temperature sensor accelerator pedal position sensor electronic control unit ECU memory system cooling system angular intervals of rotation of shaft

Claims

1. A rotary valve (2) comprising;

a rotatable shaft (8) extending at least into a plurality of chambers including a first chamber (10) and a second chamber (12), said first chamber (10) having a fluid outlet port (20), a first inlet port (42) and a second inlet port (46), said second chamber (12) having a fluid outlet port (22) and an inlet port (52), the first chamber (10) having therein a first rotatable shutter (16) provided with coolant conduits (58, 60), the second chamber (12) having therein a second rotatable shutter (18) provided with at least a coolant conduit (62), the first rotatable shutter (16) and the second rotatable shutter (18) being both coupled to said rotatable shaft (8), wherein the coolant conduits (58, 60, 62) of the first and second rotatable shutters (16, 18) are configured in such a way that:

- in a first angular interval of rotation (A) of the shaft (8) fluid passage between the inlet ports (42, 46) and the outlet port (20) of the first chamber (10) and between the inlet port (52) and the outlet port (22) ofthe second chamber (12) is inhibited,

- in a second angular interval of rotation (C,D) of the shaft (8), at least one of the coolant conduits (58, 60) of the first rotatable shutter (16) allows fluid passage between at least one of the inlet ports (42, 46) and the outlet port (20) of the first chamber (10) and the coolant conduit (62) ofthe second rotatable shutter (18) allows fluid passage between the inlet port (52) and the outlet port (22) ofthe second chamber (12), and

- in a third angular interval of rotation (B,E) of the shaft (8), at least one of the coolant conduits (58, 60) of the first rotatable shutter (16) allows fluid passage between at least one of the inlet ports (42, 46) and the outlet port (20) of the first chamber (10) and fluid passage between the inlet port (52) and the outlet port (22) ofthe second chamber (12) is inhibited.

2. The rotary valve (2) according to claim 1, wherein the second angular interval of rotation (C,D) of the shaft (8) comprises a first sub-interval (C) in which a first coolant conduit (58) of the first rotatable shutter (16) allows fluid passage between the first inlet port (42) and the outlet port (20) of the first chamber (10) and the coolant conduit (62) of the second rotatable shutter (18) allows fluid passage between the inlet port (52) and the outlet port (22) of the second chamber (12).

3. The rotary valve (2) according to claim 1 or 2, wherein the second angular interval of rotation (C,D) of the shaft (8) comprises a second sub-interval (D) in which a second coolant conduit (60) of the first rotatable shutter (16) allows fluid passage between the first inlet port (42) and the outlet port (20) of the first chamber (10) and the coolant conduit (62) of the second rotatable shutter (18) allows fluid passage between the inlet port (52) and the outlet port (22) of the second chamber (12).

4. The rotary valve (2) according to any previous claims, wherein the third angular interval of rotation (B,E) of the shaft (8) comprises a third sub-interval (B) in which a first coolant conduit (58) of the first rotatable shutter (16) allows fluid passage between the first inlet port (42) and fluid passage between the inlet port (52) and the outlet port (22) of the second chamber (12) is inhibited.

5. The rotary valve (2) according to any previous claims, wherein the third angular interval of rotation (B,E) of the shaft (8) comprises a fourth sub-interval (E) in which a second coolant conduit (60) of the first rotatable shutter (16) allows fluid passage between the first inlet port (42) and the outlet port (20) of the first chamber (10) and the outlet port (22) of the second chamber (12) is inhibited.

6. The rotary valve (2) according to claims 2 or 3, wherein the first (C) and second sub-intervals (D) are not adjacent.

7. The rotary valve (2) according to claims 4 or 5, wherein the third (B) and fourth sub-intervals (E) are not adjacent.

8. The rotary valve (2) according to claim 2 or 3, wherein the coolant conduit (62) of the second rotatable shutter (18) is positioned in such a way as to make only a portion of coolant conduit (62) coincident with the outlet port (22) of the second chamber (12).

9. A cooling system (500) for an internal combustion engine (110) comprising the rotary valve (2) according to any of the preceding claims.

10. The cooling system according to claim 9, wherein said first fluid outlet port (20) is in fluid communication with an oil heat exchanger (32), said second fluid outlet port (22) is in fluid communication with a radiator (40), and said first chamber (10) and said second chamber (12) are in fluid communication with different inlet coolant sources (45,55).

11. The cooling system according to claims 9 or 10, wherein said first chamber (10) comprises said first inlet port (42) in fluid communication with a first fluid source (45), and the second inlet port (46) is in fluid communication with a second fluid source (47), said first and second fluid sources (45,47) having different temperatures.

12. A method of operating a cooling system (500) for an internal combustion engine (110) according to claims 9-11, the method comprising the steps of selectively rotating the rotatable shaft (8) of the valve (2) to selectively carry out one or more phase of:

- oil heating by allowing a fluid flow from the first fluid source (45) through the first inlet port (42) and the outlet port (20) of the first chamber (10) towards the oil heat exchanger (32) and inhibiting fluid flow between the inlet port (52) and the outlet port (22) of the second chamber (12);

- selectively controlling oil heating by allowing a fluid flow from the first fluid source (45) through the first inlet port (42) and the outlet port (20) of the first chamber (10) towards the oil heat exchanger (32) and allowing or preventing a fluid flow between the inlet port (52) and the outlet port (22) of the second chamber (12) towards the radiator (40) or selectively controlling oil cooling by allowing a fluid flow from the second fluid source (47) through the second inlet port (46) and outlet port (20) of the first chamber (10) towards the oil heat exchanger (32) and allowing or preventing fluid flow between the inlet port (52) and the outlet port (22) of the second chamber (12) towards the radiator (40);

- oil cooling by allowing a fluid flow from the first fluid source (45) through the first inlet port (42) 5 and the outlet port (20) of the first chamber (10) towards the oil heat exchanger (32) and allowing fluid flow between the inlet port (52) and the outlet port (22) of the second chamber (12) towards the radiator (40).

Intellectual

Property

Office

GB1612544.5

1-12