Device for driving a rotary valve

Abstract

A hydraulic rotary distributor comprising a case (2) and a core (4), said case (2) being a side wall (8) and two end walls (6, 10) defining a hydraulic chamber, the two end walls (6, 10) in which a core (4) capable of rotating within the chamber around a rotation axis (XX’) is housed, and an axial orifice (11) for example for supply, the side wall of the case including at least two lateral orifices opening into the hydraulic chamber, for example outlets (12, 20), the core (4) including a lateral surface (32) facing the side wall (8), an axial opening (18), at least one lateral orifice (34), the core (4) comprising coupling means (282) for coupling an end of a shaft (330) of an actuator (33) to the core (4), including a part (36) provided with a groove (361) for receiving the end of the shaft, the core comprising a housing (41) capable of receiving said part, whereby said part transmits rotation from the shaft to the core, a hydraulic rotary distributor is provided.

Description

Technical Field

[0001] The present invention relates to a device for driving a rotary valve or a hydraulic distributor used for cooling, for example, in the automotive industry. The valve or the distributor is preferably electrically operated. The present invention is also applicable to the distribution of the coolant of a fuel cell.

Background Art

[0002] In the automotive field, it is common to use valves or hydraulic distributors to cool some parts of the engine. For example, these are electric valves having one or two inlets and two outlets, and solenoid valves having one inlet and two outlets. These valves or distributors are generally controlled via an electric motor.

[0003] There are several types of hydraulic valves or distributors (although the term "distributor" is used in the following description, it should be understood that it also applies to valves), and these are particularly slide valves and rotary distributors.

[0004] A rotary distributor, also called a ball and plug distributor, comprises a case defining a chamber in the shape of a rotating cylinder provided with at least one fluid inlet intended to be connected to a source of liquid and at least one fluid outlet intended to be connected to a pipe carrying the liquid towards the zone to be cooled. The inlet and the outlet open into the cylindrical wall of the chamber. The distributor also includes a central rotating part or core mounted within the chamber. The core includes a rotating outer face facing the cylindrical wall of the chamber. The core is provided on its outer face with at least two orifices connected by flow paths. The two orifices are oriented relative to each other such that when one of the orifices faces the inlet, the other faces the outlet. Thus, by rotating the core within the chamber, it is possible to allow or block the circulation between the inlet and the outlet, and thus between the source of liquid and the zone to be cooled.

[0005] One problem is to drive a rotary distributor device of the type described above, for example, and a simple drive system is required that enables the movement from the actuator to be easily transmitted to the core.

[0006] Also, for example, when supplying a duct, there is also the problem of automatically returning the core to its equilibrium or starting position when it has been moved to another position.

[0007] Furthermore, such distributors are generally supplied laterally, and the lateral fluid inlet generates a torque acting on the entire device. It is one problem to fabricate a distributor device that enables this problem to be solved.

[0008] Fabricating a rotary distributor device that enables simultaneous proportional distribution of fluid between two distributor outlets is another problem. In fact, there is no known device that can distribute fluid between two outlets according to a predetermined distribution method.

[0009] The problem of sealing between the core and the case is another problem, which is usually formed by using joints, raising the problems of monitoring the state of these joints and fabricating a device that must be provided with grooves in which these joints are positioned. As a result, the device and the manufacturing method become complicated. There is a clear need to fabricate a distributor using a simple and reliable design with fewer parts.

Prior Art Documents

Patent Documents

[0010]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0011] Therefore, one objective of the present invention is to provide a highly reliable hydraulic rotary distributor with simplified manufacturing in relation to conventional hydraulic distributors.

[0012] Another objective of the present invention is to provide a hydraulic rotary distributor that enables solving at least one of the problems described above.

Means for Solving the Problems

[0013] The present invention relates in particular to a hydraulic rotary distributor comprising a case and a rotating central part, i.e. a core, said case including a chamber in the shape of a rotating cylinder for receiving the core. The case comprises side walls, two end walls defining a hydraulic chamber in which a core capable of rotating within said chamber around a rotation axis (XX') is housed, at least one axial orifice, such as a supply orifice, and at least one lateral orifice, such as two lateral orifices, opening into the hydraulic chamber and forming, for example, one or two outlet orifices. The core comprises a lateral surface facing the side walls of the case, an axial surface, for example for an inlet or supply, at least one lateral orifice, such as a lateral outlet, and a duct, i.e. a chamber, connecting said axial surface and said lateral orifice and enabling circulation, for example supply, from and to each of said lateral orifices of the case depending on the angular position of the core within the case. The core comprises coupling means for coupling an end of an actuator shaft to the core.

[0014] For example, the coupling means may include a grooved part for receiving or capable of receiving an end of the actuator shaft, and the core comprises a housing capable of receiving said part, whereby said part transmits rotation from the shaft to the core.

[0015] Said part and the housing may each have a cylindrical shape and may advantageously be provided with a lug having a parallelepiped shape, the housing including a space for receiving said lug.

[0016] Said groove and said lug may extend along directions perpendicular or substantially perpendicular to each other. This makes it possible to compensate for misalignment or non-alignment by an axis perpendicular to the rotation axis.

[0017] Alternatively, said part and the housing may each have a parallelepiped shape.

[0018] The hydraulic rotary distributor according to the present invention can further include a return means for returning the core to an equilibrium or initial position after it has been moved to a position away from this equilibrium or initial position.

[0019] For example, these return means include a torsion spring with one end fixed to the core and the other end fixed to a part of the distributor that remains stationary when the core is rotationally driven.

[0020] The present invention thus relates to a hydraulic rotary distributor comprising a case and a core, wherein the case delimits a hydraulic chamber having side walls and two end walls within which a core that can rotate within the chamber around the rotation axis XX' is housed, at least one axial orifice, such as a supply orifice, and at least one lateral orifice, such as an outlet orifice, opening into the hydraulic chamber, the core having a lateral surface facing the side walls of the case, an axial surface, such as forming an inlet opening, at least one lateral orifice, and ducts, i.e., chambers, connecting the at least one lateral orifice and the axial surface and enabling circulation, such as supply, from or to each of the lateral orifices of the case depending on the angular position of the core within the case, and the distributor further includes return means for returning the core to an equilibrium or initial position after it has been rotationally moved to a position away from this equilibrium or initial position.

[0021] For example, the return means include a torsion spring with one end fixed to the core and the other end fixed to a part of the distributor that remains stationary when the core is rotationally driven.

[0022] In the hydraulic rotary distributor according to the invention, the sealing between the lateral surface of the core and the side wall of the case can be ensured by a narrow passage or a small clearance between this lateral surface and this side wall, for example between 50 μm and 200 μm or even up to 300 μm (for example, 250 μm for a leakage of 1% at 700 l / min in particular).

[0023] Furthermore, the hydraulic rotary distributor according to the invention can comprise means for limiting its angular rotational movement when driven by an actuator. For example, the core comprises slots having a circular shape which are stopped by stoppers in the initial position of the core and then in the maximum position of the latter.

[0024] According to one embodiment of the hydraulic rotary distributor according to the invention, one of the end walls comprises a supply orifice extending substantially perpendicular to the rotation axis XX' or coaxially with the latter, and the side wall of the case comprises at least two lateral orifices, for example two outlet orifices, opening into the hydraulic chamber, and the core comprises a lateral surface facing the side wall of the case and an axial surface facing an axial orifice, for example an inlet surface, which is a supply orifice.

[0025] Preferably, in the hydraulic rotary distributor according to the invention, the lateral orifices of the core have a shape which enables a partial supply of the two lateral orifices of the case to be simultaneous at at least one other or several intermediate angular positions between the first angular position and the second angular position.

[0026] For example, the lateral orifices of the core have an elongated, rectangular or oval or ellipsoidal shape following an axis substantially perpendicular to the rotation axis XX'.

[0027] According to a particular embodiment, - The transverse orifice of the core has an angled opening that is larger than the angle separating two transverse orifices within the side wall of the case, measured in a plane perpendicular to the axis of rotation of the core and within the same plane. - And / or the distance separating the two points furthest from the transverse orifice of the core is greater than the distance separating the two transverse orifices of the case. - And / or the inner duct of the core connects the axial plane of the core and the transverse orifice of the core, and the duct has a cross-section that increases from the axial plane towards the transverse orifice perpendicular to the direction of fluid flow, for example, the cross-section of the inner duct preferably increases by a value between 1% and 3% for any increase between, on the one hand, 5° or rather 7° and, on the other hand, 12° or rather 15° of the angle measured between the axial plane of the core and a plane perpendicular to the direction of fluid flow or circulation.

[0028] Advantageously, the case and / or the core are made of molded plastic, which makes it possible to reduce the mass of the distributor and shorten the manufacturing time.

[0029] For example, the case and / or the core are made of plastic.

[0030] According to an advantageous embodiment of the hydraulic rotary distributor according to the invention, the transverse orifice of the case is extended by a duct that extends along an axis X having an intersection point A located behind the center C of the core with respect to the transverse orifice of the case. 12 、X 20

[0031] Regardless of the intended embodiment of the hydraulic rotary distributor according to the invention, - The axial plane of the core can include an opening facing the axial orifice of the case. - And / or the case can include one, two, or more transverse orifices.

[0032] Another object of the present application is also a hydraulic rotary solenoid distributor comprising a distributor according to one or the other of the embodiments of the invention and an actuator for rotationally driving the core, such as a motor or a geared motor.

[0033] For example, the actuator comprises an output shaft aligned along the rotation axis XX'.

[0034] The present invention also relates to a method of distributing a fluid using a hydraulic rotary solenoid distributor according to the present invention, wherein the fluid is introduced, for example, by axial orifices, which are supply orifices, along the direction of the rotation axis XX' or in a direction perpendicular thereto, and is guided by the inner duct of the core towards the lateral orifices of the latter and then, according to the orientation of the core in the case, towards one and / or the other of the two lateral orifices of the case, which thus become outlet orifices.

[0035] According to one example, the fluid is a mixture of water and glycol, for example 60% water and 40% glycol. This fluid is suitable, for example, for cooling a fuel cell.

[0036] The present invention also relates to a method of distributing a fluid using a hydraulic rotary solenoid distributor according to the present invention, wherein the fluid is introduced by two lateral orifices of the case, which are thus inlet or supply orifices, and these fluids are guided by the inner duct of the core towards the axial orifices and are at least partially mixed in this inner duct. These two fluids may be of the same nature or may be identical but in different temperature states, one originating, for example, from a heating member or element, such as a fuel cell, and the other from a cooling member or element, such as a radiator.

[0037] The present invention will be better understood based on the following description and the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0038]

Figure 1

Figure 2A

Figure 2B

Figure 3

Figure 4

Figure 5A

Figure 5B

Figure 6

Figure 7A

Figure 7B

Figure 8

Figure 9A

Figure 9B

Figure 10A

Figure 10B

Figure 10C

Figure 11A

Figure 11B

Figure 11C

DETAILED DESCRIPTION OF THE INVENTION

[0039] FIG. 1 shows an exemplary embodiment of a hydraulic rotary distributor to which the present invention can be applied and of the type having one inlet and two outlets. It is understood that the distributor may have one or more outlets. Further, one or more inlets can be reversed relative to the outlets as will be described below (in connection with FIG. 9B).

[0040] The distributor D includes a case 2 or valve body portion having a shape of a rotating cylinder substantially centered on axis XX', and a central portion 4 called a core, which is mounted within the case 2 and can rotate therein.

[0041] In the example shown, case 2 includes a bottom 6, a substantially cylindrical one-piece side wall 8, and an inlet cover 10 with an opening 11 through which fluid enters the device. The fluid thus flows in a direction that coincides with axis XX', and is then distributed by the core 4, preferably in one or more lateral outlets of the case, oriented in the YZ plane perpendicular to axis XX' (see for example FIG. 9A). The inlet cover 10 is assembled or firmly connected to the case 2, for example, in a removable manner, for example by screws, or in a fixed manner, for example by welding, or also, for example (especially when the parts are made of plastic material), by ultrasonic welding.

[0042] It should be noted that the coaxial arrival of the fluid makes it possible to reduce the torque caused by the latter on the entire distributor. This is advantageous regardless of the fluid flow rate, but is particularly advantageous at high flow rates, for example in the range from 200 to 700 liters per minute. Case 2 may be extended by a first outlet orifice 20 formed in the side wall 8, which is intended, for example, to carry a liquid to a given zone, for example a zone to be cooled, by a first duct 20', and a second outlet orifice 12, which is also intended here to carry the liquid to a given zone, for example also a zone to be cooled, by a second duct 12'. These ducts 12', 20 are welded, for example, onto the bases of orifices 12 and 20 respectively. Case 2 defines a hydraulic chamber 26. The outlet orifices 12 and 20 are angularly distributed on the side wall around axis XX'.

[0043] Case 2 also comprises a motor cowl 18 which can be assembled or firmly connected to the case 2, for example in a removable manner, for example by means of screws, or in a fixed manner, for example by welding, here also for example by ultrasonic welding (especially if the parts are made of plastic material). The device is entirely actuated by an actuator 33 (for example a motor or a geared motor). The coupling means, i.e. the member, 36 connects the shaft of the actuator to the core 4 and drives the latter in rotational drive about the axis XX'.

[0044] For example, adaptation means 39, including a crown 391 and fastening means 392, for example screws, can be provided for assembling the actuator 33 with the cowl 18. The axis of the actuator passes through the central orifice of the crown.

[0045] The device of FIG. 1 is shown in the assembled state in FIG. 9A.

[0046] FIGS. 2A and 2B show that the core 4 also has the shape of a rotating cylinder about the axis XX'. This core 4 is mounted in a hydraulic chamber and can rotate about the axis XX'. It includes two end faces 28, 30 and a lateral surface 32.

[0047] When this core 4 is mounted within the hydraulic chamber, its end face 28 faces the bottom of the case 2 (which is disposed on the actuator side), and its end face 30 faces the cover 10. This end face 30 is provided with an opening 31 which, in this example, is intended to be aligned with the opening 11 of the cover 10 along the axis XX' so as to receive the flow of the fluid flowing. The lateral surface 32 of the core 4 includes a lateral opening 34 which enables the fluid to be directed towards one or more outlet orifices 12, 20. A rolling bearing 37 may be provided which ensures the guidance of the rotation of the core 4 within the case 2. Further, a static joint may advantageously be provided between the case 2 and the cover 10, thereby enabling the avoidance of liquid leakage. Similarly, one or more joints 40 are advantageously provided between the end face 6 and the cowl 18, thereby enabling the avoidance of liquid leakage. The reference numeral 37' also refers to a rolling bearing.

[0048] The duct 38 connects the opening 31 which serves as the inlet of the fluid into the core 4 and the opening 34 which serves as the outlet of the fluid from the core. The shape of this duct is shown in more detail in FIG. 3. Preferably, this duct widens from an inlet opening 31 which is, for example, circular, towards an outlet opening 34 which preferably has an elongated shape as described hereinafter.

[0049] A plane P which is substantially orthogonal to the direction of the fluid flow is shown in FIG. 3. According to an exemplary embodiment, this plane P forms an angle α with the plane P in which the inlet opening 31 is disposed. The intersection of this plane P with the duct 38 has a surface area S which increases, for example linearly, as the angle α increases. This progressive increase enables the reduction of the head loss. 0 The following Table 1 shows various values of the surface area S which can increase as the angle α increases, as already shown above, for various values of the angle α.

[0050] The following Table 1 shows various values of the surface area S which can increase as the angle α increases, as already shown above, for various values of the angle α.

[0051]

Table 1

[0052] At its final part, the angle α is equal to 90°, but the surface area S can further increase as understood from the above table (see the difference between the value of S for 90° and the "final" value).

[0053] For example, each time the angle α increases by 10°, or more generally between 7° (or even 5°) and 12° (or even 15°), the surface area S can increase by a relative value between 1 and 3%, for example 2%.

[0054] Preferably, the outlet orifice 34 has an elongated or oval shape along an axis YY' substantially perpendicular to the axis XX' in the projection in a plane parallel to the axis XX' and perpendicular to the direction of the fluid outlet. For example, the projection of this outlet orifice has an ellipsoidal shape, and the major axis of the ellipsoid is the same as the axis YY'.

[0055] The distance d (Figure 2B) between the points furthest from this opening along the axis YY' is greater than the distance d separating two adjacent outlet openings 12, 20 of the rotary case 2, as illustrated in Figure 4. This figure represents a schematic of the case 2 having two outlets 12, 20 and the core 4 having the outlet orifice 34. In Figure 4, the latter opens partially onto the outlet 12 and partially onto the outlet 20, thereby enabling a first flow F12 to flow through the outlet 12 and a second flow F20 to flow through the outlet 20. The ratio of these flows can be corrected by using the actuator 33 to correct the orientation of the core 4 within the case 2. 1 More preferably, the distance d (Figure 2B) between the points furthest from this opening along the axis YY' is greater than the distance d separating two adjacent outlet openings 12, 20 of the rotary case 2, as illustrated in Figure 4. This figure represents a schematic of the case 2 having two outlets 12, 20 and the core 4 having the outlet orifice 34. In Figure 4, the latter opens partially onto the outlet 12 and partially onto the outlet 20, thereby enabling a first flow F12 to flow through the outlet 12 and a second flow F20 to flow through the outlet 20. The ratio of these flows can be corrected by using the actuator 33 to correct the orientation of the core 4 within the case 2.

[0056] The ratio of these flows can be corrected by using the actuator 33 to correct the orientation of the core 4 within the case 2. For some positions of the core, the orifice 34 opens partially onto the outlet 12 and partially onto the outlet 20, and for each of these positions, the ratio of these flows is different from the ratio at other positions.

[0057] At some positions, the outlet orifice 34 can open only to one or the other of the outlets 12, 20. This is shown in FIG. 5A (where the outlet of the flow is entirely directed towards outlet 20) and FIG. 5B (where the outlet of the flow is entirely directed towards outlet 12).

[0058] Preferably, the clearance between the core 4 and the inner surface of the case 2 enables ensuring sealing between two adjacent outlet paths 12, 20 without implementing a joint. This - additional friction (between the joint and the inner surface of the case 2 or between the joint and the outer surface of the core 4), - monitoring the state of the joint and the step of replacing it when the latter wears out makes it possible to avoid.

[0059] For this purpose, it is possible to calculate the maximum clearance h that can be implemented between the outer surface of the core and the inner surface of the case 2. The slot can be modeled by a system consisting of two plates spaced by a width b over a length l, the slot having a thickness h, with a pressure p1 (upstream pressure) applied at one of the outlets and a pressure p2 (downstream pressure, p1 > p2) applied at the other outlet. Since the fluid has a kinematic viscosity η, the following equation applies, which gives the leakage flow rate dV / dt. [Equation 1] dV / dt=(h 3 b / 12ηl).(p1 - p2) Here, - the fluid consists of a mixture of water (60%) and glycol (40%). - at 100 °C, it has a viscosity of 2×10 -3 Pa.s. - the pressure difference (p1 - p2) is 1 bar. - the values are b = 4.5×10 -2 m and L = 1.77×10 -2 m.

[0060] 1.85×10-4 The maximum radial clearance of m is obtained, and it has a leakage flow rate of up to 4 l per minute at most.

[0061] The above formula can be modified to fit according to the desired maximum leakage rate, the viscosity of the fluid (which may itself depend on temperature), geometric parameters, and pressure difference. The actual part dimensions 2, 4 obtained during manufacturing are then compared with the maximum clearance obtained according to the above modeling, thereby verifying whether these parts meet the desired sealing requirements.

[0062] Generally, since the flow rate of leakage is inversely proportional to the viscosity, it is possible to use the operating temperature that results in the lowest viscosity. This temperature is, in most cases, the maximum operating temperature. For example, when using a coolant that is used between -40°C and 100°C, the latter value of 100°C is used.

[0063] More generally, the clearance is, for example, between 50 μm and 200 μm or even up to 300 μm (for example, 250 μm for a 1% leakage of 700 l / min in particular).

[0064] This sealing without using a joint can be applied not only to the distributor described above with respect to FIGS. 1 to 3, but also to any distributor that implements a rotating element within the distribution body part, in particular - including the injection of fluid in a direction transverse to the body part 2 rather than in the axial direction (along axis XX') as described above, - and / or the core includes a distribution channel with a uniform cross-section and is arranged facing the outlet orifice, the end of which may have an elongated shape as described above, or a circular shape corresponding to or the same as the cross-section of the openings 12, 20, It can be applied to any distributor.

[0065] As a result, the sealing can be ensured by a narrow passage or a small clearance between this transverse surface and this side wall.

[0066] Another aspect of the present invention is described with respect to FIGS. 11A - 11C. The lateral ducts 12, 20 lie in the same plane (in a plane perpendicular to the axis XX') along axes X 12 , X 20 respectively, and intersect at point A. This point can be the same as the center C of the core 4 (which is also the center of the bore of the body part 2 into which the core is inserted). However, according to the noted embodiment of the present invention, point A is displaced and is located behind point C at a distance l from the latter. Point C is thus closer to the orifices 12, 20 than point A, and the two points A and C are located on the axis EE', which is the central axis of the core (and the bore of the body part 2) in the plane perpendicular to the axis XX' (or the median plane of the body part 2). A is thus further away from the orifices 12, 20 than point C. This makes it possible to increase the distance (which is called the overlapping length and is also the length d 1 shown in FIG. 4) separating these ducts for a given diameter of the ducts 12', 20'. As this distance increases, the leakage flow rate, calculated according to the formula given above, decreases. The example of FIG. 11B is an example of a device where the intersection point A and the center C are the same. The inner diameter of the conduit 38 is equal to 80 mm in the plane of the axes X 12 , X 20 . The length d 1 is 1.36 mm. In FIG. 11C, point A is offset by a distance l of 20.8 mm behind point C, and the length d 1 is equal to d' 1 = 11.33 mm, or more than 8 times larger than the initial length, and thus the leakage itself is reduced to 1 / 8 or less. The gain obtained by the relative offset of points A and C can thus be a very substantial value.

[0067] According to the present invention, the device coupling or driving means or parts 36 as described above can have the shapes shown in FIGS. 1, 6, and 7. These means take the shape of a cylinder (FIG. 7A) in the lower part where a groove 361, preferably having a parallelepiped shape, can be made to enable receiving the end of the shaft 330 of the actuator 33 (see FIG. 1). The coupling part 36 is housed within the lower section 41 of the core 4 (see FIGS. 6 and 7) and includes, at its upper part, a lug 360, for example having a parallelepiped shape, which enables the core 4 to be rotationally actuated when the shaft 330 also rotationally actuates the part 36. Preferably, the groove 361 and the lug 360 each extend along a direction perpendicular to the axis XX' (each having a width smaller than its length, which is substantially the diameter of the cylinder 36), and both extend along two mutually perpendicular directions (in other words, the groove 361 extends along a direction perpendicular to the direction of the lug), which enables compensating for coaxial misalignment by two axes perpendicular to the rotation axis XX'.

[0068] The lower section 41 of the core 4 has a shape complementary to the shape of the part 36 and, in particular, it includes a slot 282 into which the lug 360 is inserted.

[0069] Alternatively (see FIG. 7B), the coupling means 36' can have a parallelepiped shape within the lower part including a groove 361' enabling receiving the end of the shaft 330 of the actuator 33. This part 36' is housed within the lower section 41 of the core 4 having a parallelepiped shape (see FIGS. 6 and 7), and thus when the actuator 33 rotationally drives the part 36', the latter subsequently rotationally drives the core 4.

[0070] Advantageously, the lower face 28 of the core 4 has a circular groove 280 (see FIGS. 1, 5, and 6) enabling it to receive a pin 181 connected to the engine cowl 18, this pin forming a stopper against the movement of the core 4 when the latter is rotated by the actuator 33. This stopper stops or limits the movement of the slot at the initial position of the core, then at its maximum position, the initial position corresponding, for example, to a flow of 0 at the outlet 20 and the final position corresponding to a flow of 0 at the outlet 12 (see FIGS. 5A and 5B).

[0071] According to another aspect of this invention, the torsion spring is connected to the core 4 by one of its ends (for example, the slot is formed at the top of the latter to insert said end of the spring therein), and by the other of its ends to a part remaining stationary when the core is rotationally driven, such as a cover or an end part 10 (for example, the slot is formed in this cover or this end part to insert this other end of the spring therein). Thus, the actuator 33 can rotationally drive the core from a first position towards a second position, and the stopping of the actuation of the actuator automatically causes the core to return towards the first position, i.e., the initial position. For example, the device is in a stationary position where the fluid flows towards the outlet 12, the actuator drives the core 4 towards a position where the fluid flows towards the outlet 20, and the stopping of the actuation of the actuator can automatically cause the core to return towards the initial position, i.e., the position where the fluid flows towards the outlet 12. This aspect of the invention is illustrated in FIG. 8, where a torsion spring 60 can be seen, one end 61 of which is connected to the upper part 30 of the core 4 and the other end 63 of which is connected to the lower part of the inlet cover 10.

[0072] The coupling means 36, and their housing within the lower section of the core 4, and / or the return means described above with respect to FIGS. 6 - 8, are attached not only to the distributor described above with respect to FIGS. 1 - 3, but also to any other distributor implementing a rotating element within the distribution body part, in particular, - Instead of in the axial direction (along axis XX’) as described above, it includes the injection of fluid in the lateral direction of the body 2, in which case the case and the core each have a fluid inlet in the side wall 8 and the lateral surface 32, - And / or the core includes a distribution channel with a uniform cross-section, and the end 34, which is arranged facing the outlet orifice, may have an elongated shape as described above or a circular shape corresponding to the cross-section of the openings 12, 20, It can be attached to any distributor.

[0073] Preferably, the case 2 and the core 4 are made of a plastic material that reduces the mass of the distributor, which is particularly preferred in the automotive field. Furthermore, the plastic material is preferably loaded with a material that reduces friction. For example, the case and / or the core are made from polyphthalamide, such as of the PA6T / 6I-GF30 type, very preferably loaded with PTFE.

[0074] Furthermore, they are preferably made by injection molding, which simplifies their manufacture. Regarding the core, the shape of the inner duct 38 can be formed, for example, into two parts 38-1 and 38-2 as illustrated in FIGS. 10A and 10B, and then the core can be molded by injection molding around this shape. In these figures, the shapes of the two parts 38-1 and 38-2 also have an increasing cross-section, although not as gradually as in the case of FIG. 3.

[0075] Still, the case and the core can be made of a metallic material, such as stainless steel or aluminum. The constraints on the surface condition of the inner surface of the case and the surface of the core are substantially relaxed since they do not guarantee sealing.

[0076] Figure 9 shows an embodiment of the assembly of the distributor of FIG. 1 after assembly. The reference numbers are those already described above with respect to FIG. 1. The coolant enters this device via the opening 11, following the direction of the axis of rotation when the core is rotated by the actuator 33. The actuator is, for example, a gear motor MR whose output shaft is coupled to the core 4, for example as already described above. The gear motor is, for example, the one described in Patent Document 1.

[0077] Next, the operation of the distributor incorporating the operating mechanism according to the present invention will be described.

[0078] The supply inlet 11 is connected to a source of pressurized liquid, for example a pump connected to a liquid tank, and the two outlet orifices 12, 20 are connected to, for example, a heat or electric engine to be cooled.

[0079] When it is desired to supply the maximum flow rate to the outlet orifice 20, the core 4 is rotated by the actuator 33 about the axis X to position the outlet 34 of the core facing the outlet orifice 20. The pressurized liquid circulates through the duct 38 from the supply orifice 18 towards the outlet orifice 20 as shown in FIG. 5A.

[0080] When it is desired to supply the maximum flow rate to the outlet orifice 12, as shown in FIG. 5A, the core 4 is rotated by the actuator 33 about the axis XX' to align the outlet 34 with the outlet orifice 20, whereby the duct 38 connects the supply orifice 11 and the outlet orifice 20.

[0081] As already described above, the core 4 can occupy any intermediate angular position to ensure a proportional supply of the outlet orifices 12 and 20.

[0082] Other relative angular orientations of the outlets 12 and 20 are possible.

[0083] The present invention makes it possible to provide a distributor that performs reliable operation while substantially eliminating constraints on dimensions, surface conditions, required materials, and manufacturing methods.

[0084] The example described includes one supply orifice and two outlet orifices, but as noted above, the present invention is applicable to distributors having one inlet orifice and one outlet orifice, or one supply orifice and more than two outlet orifices, as well as distributors having two supply orifices. The distributor according to the present invention can have two axial fluid inlets, and the actuator can be moved to allow fluid to pass to a second end or more ends, and one or more outlet orifices. Configurations having several supply orifices and several outlet orifices can implement a core with several cavities or recesses 43 to allow several flows, whether simultaneous or not, within the distributor.

[0085] In the example described above, the fluid flows through duct 38 via orifice 11 and exits the device via one or both of the lateral ducts 12, 20 (see, for example, the arrows in FIG. 9A indicating the direction of fluid flow).

[0086] It is also possible to use the same device in reverse operation. That is, these are the lateral ducts 12, 20 that are used as supply ducts and are supplied with fluid, and these fluids mix within the inner duct 38 and the mixture flows through orifice 11, which becomes the outlet orifice. The proportion of fluid supplied to the device is corrected according to the angular position (around axis XX') of the core within the case. Thus, depending on the number of lateral ducts 12, 20, it is possible to introduce two or more fluids to be mixed. This use is illustrated in FIG. 9B, where the arrows indicate the direction of fluid flow.

[0087] For example, the two fluids at the inlet can be different. Alternatively, they can be of the same nature or the same, but in different temperature states, one being, for example, from a heating member or element, such as a fuel cell, and the other being from a cooling member or element, such as a radiator.

[0088] The distributor according to the invention, particularly associated with a geared motor, is particularly suitable for use in the automotive field (thermal engine or electric engine) due to its mass reduction.

[0089] The operating mechanism according to the invention can be attached to a distributor provided in a vehicle equipped with a thermal, hybrid, or electric engine that implements, for example, a system for regulating temperature and / or a system for orienting the air flow.

Explanation of Signs

[0090] D Distributor F12 First flow F20 Second flow XX’ Axis 2 Case 4 Central part 4 Core 6 Bottom 8 Substantially cylindrical integrally formed side wall 10 Inlet cover 11 Opening 12 Second outlet orifice 12’ Second duct 18 Motor cowl 20 First outlet orifice 20’ First duct 26 Hydraulic chamber 28 End face 28 Lower side face 30 End face 31 Opening 33 Actuator 34 Opening 36 Coupling means, i.e., member 36’ Coupling means 36’ parts 37 rolling bearing 38 duct 38-1, 38-2 parts 39 fitting means 40 joint 41 lower section 43 cavity or recess 60 torsion spring 61 one end 63 the other end 181 pin 280 circular groove 282 slot 330 shaft 360 lug 361’ groove 391 crown 392 fastening means

Claims

**Claim 1** A hydraulic rotary distributor comprising a case (2) and a core (4), wherein said case (2) has side walls (8) and two end walls (6, 10) defining a hydraulic chamber, and two end walls (6, 10) in which said core (4) which can rotate within said chamber around a rotation axis (XX') is housed, at least one axial orifice (11), and at least one lateral orifice (12, 20) opening into said hydraulic chamber, said core (4) having a lateral surface (32) facing said side wall (8) of said case (2), an axial opening (18), at least one lateral orifice (34), and a duct (38) i.e. a chamber connecting said axial opening (18) and said lateral orifice (34) and enabling circulation of fluid from and to each of said lateral orifices (12, 20) according to the angular position of said core within said case, said core (4) comprising coupling means (28, 36, 36', 282) for coupling an end of a shaft (330) of an actuator (33) to said core (4), said coupling means (28, 36, 36', 282) including parts (36, 36') provided with a groove (361) for receiving said end of said shaft of said actuator (33), said core (4) comprising a housing (41) capable of receiving said parts (36, 36'), whereby said parts transmit the rotation of said shaft to said core, a hydraulic rotary distributor. **Claim 2** The hydraulic rotary distributor according to claim 1, wherein said parts (36, 36') and said housing (41) have a cylindrical shape and comprise a lug (360) having a parallelepiped shape, and said housing (41) comprises a space (282) for receiving said lug. **Claim 3** The hydraulic rotary distributor according to claim 2, wherein said groove and said lug (360) extend vertically or substantially vertically. **Claim 4** The hydraulic rotary distributor according to claim 1, wherein said parts (36, 36') and said housing (41) have a parallelepiped shape. **Claim 5** A hydraulic rotary distributor comprising a case (2) and a core (4), said case (2) having side walls (8) and two end walls (6, 10) defining a hydraulic chamber, said core (4) being rotatable within said chamber about a rotation axis (XX') and being housed between said two end walls (6, 10), at least one axial orifice (11), and at least one lateral orifice (12, 20) opening into said hydraulic chamber, said core (4) having a lateral surface (32) facing said side wall (8) of said case (2), an axial opening (18), at least one lateral orifice (34), and a duct (38) or chamber connecting said axial opening (18) and said lateral orifice (34) and enabling circulation of fluid from or to each of said lateral orifices (12, 20) depending on the angular position of said core within said case, said distributor further comprising return means (60, 61, 63) for returning said core (4) to an equilibrium or initial position after it has been rotationally moved to a position away from this equilibrium or initial position, said return means (60, 61, 63) including a torsion spring having one end fixed to said core (4) and the other end fixed to a part of said distributor that remains stationary when said core (4) is rotationally driven, a hydraulic rotary distributor.

6. The hydraulic rotary distributor according to any one of claims 1 to 5, wherein the sealing between said lateral surface of said core and said side wall of said case (2) is ensured by the clearance between this lateral surface and this side wall.

7. The hydraulic rotary distributor according to claim 6, wherein the clearance between said lateral surface and said side wall is between 50 μm and 320 μm.

8. The hydraulic rotary distributor according to any one of claims 1 to 7, wherein said core (4) comprises means (280) for limiting its rotation when it is rotationally driven by an actuator (33).

9. The hydraulic rotary distributor according to claim 8, wherein said core (4) comprises a slot in the shape of an arc of a circle through which a stopper (181) passes.

10. One of said end walls (6) includes an axial orifice (11) extending substantially perpendicular to said axis of rotation (XX'), and said side walls of said case include at least two lateral orifices (12, 20) opening into said hydraulic chamber, and said core (4) includes a lateral surface (32) facing said side wall (8) of said case (2) and an axial surface (18) facing said axial orifice (11). The hydraulic rotary distributor according to any one of claims 1 to 9.

11. Said case includes at least two lateral orifices (12, 20), and said lateral outlet (34) of said core has a shape enabling a partial flow to and from said two lateral orifices simultaneously at at least one other intermediate angular position between said first angular position and said second angular position. The hydraulic rotary distributor according to any one of claims 1 to 10.

12. Said lateral orifice (34) of said core has an elongated, rectangular, oval or ellipsoidal shape following an axis substantially perpendicular to said axis of rotation (XX'). The hydraulic rotary distributor according to claim 11.

13. The distance separating the two points furthest from said lateral orifice (34) of said core is greater than the distance separating said two lateral orifices (12, 20) of said case (2). The hydraulic rotary distributor according to claim 11 or 12.

14. Said inner duct (38) of said core connects said axial surface (18) of said core to said lateral orifice (34) of said core, and this duct has a cross-section increasing from said axial surface (18) towards said lateral orifice (34) perpendicular to the direction of fluid circulation. The hydraulic rotary distributor according to any one of claims 11 to 13.

15. Said cross-section of said inner duct (38) spreads by a value between 1% and 3% for any increase between 5° and 15° of said angle measured between said axial surface (18) of said core and a plane perpendicular to the direction of said fluid flow. The hydraulic rotary distributor according to claim 14.

16. The hydraulic rotary distributor according to any one of claims 1 to 15, wherein the case and / or the core is made of a plastic material.

17. The case has an intersection (A) located behind the center (C) of the core (4) with respect to the lateral orifices (12, 20) of the case, and is extended by ducts (12', 20') extending along the axis (X １２ , X ２０ ). The hydraulic rotary distributor according to any one of claims 1 to 16, comprising at least two lateral orifices (12, 20).

18. A hydraulic rotary solenoid distributor comprising the distributor according to any one of claims 1 to 17 and an actuator (33) for rotationally driving the core.

19. The hydraulic rotary solenoid distributor according to claim 18, wherein the actuator comprises an output shaft (330) aligned along the rotation axis (XX').

20. A method for distributing a fluid using the hydraulic rotary solenoid distributor according to claim 18 or 19, wherein the fluid is introduced via the axial orifice (11) along, for example, the direction of the rotation axis (XX') or a direction perpendicular to the rotation axis (XX'), and is guided by the inner duct (38) of the core towards the lateral orifice (34) of the core, and then, according to the orientation of the core in the case (2), towards one and / or the other of the two lateral orifices (12, 20) of the case.

21. The method according to claim 20, wherein the fluid is a mixture of water and glycol.

22. The method according to any one of claims 20 or 21, wherein the fluid is a coolant for a fuel cell.

23. A method for distributing a fluid using the hydraulic rotary solenoid distributor according to claim 18 or 19, wherein the fluid is introduced via the two lateral orifices (12, 20) of the case, and these fluids are guided by the inner duct (38) of the core towards the axial orifice (11) and are at least partially mixed within this inner duct (38).

24. The method according to claim 23, wherein the two fluids have the same properties or are the same but are in different temperature states.

25. The method according to claim 24, wherein one of the fluids is derived from a heating member or element, for example a fuel cell, and the other is derived from a cooling member or element, for example a radiator.

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