Fluid control device and magnetocaloric machine comprising said fluid control device

Abstract

The invention relates to a fluid control device (10), in particular for a magnetocaloric machine, comprising at least one fluidic distributor (11), comprising a first duct (C1) connected to a first circuit portion (5a), and a second duct (C2) connected to a second circuit portion (5b), said ducts being separate. The fluidic distributor comprises a body (12), and a shutter (13) that is movable with respect to said body between two switching positions in order to allow flow along said first duct (C1) and said second duct (C2) alternately. The body and the shutter each comprise an outlet orifice (OA1, OA2) corresponding to the first duct (C1) and a return orifice (OR1, OR2) corresponding to the second duct (C2). The device further comprises an eccentric control mechanism (20) coupled on the one hand to a rotary actuator (4) and on the other hand to said shutter (13) in order to move it from one switching position to the other in a continuous output movement.

Description

[0001] DESCRIPTION

[0002] Title: Fluidic control device and magnetocaloric machine comprising said fluidic control device

[0003] Technical field

[0004] The present invention relates to a fluid control device in general and more particularly intended to equip a magnetocaloric machine, comprising at least one fluid distributor comprising at least a first conduit arranged to be connected to a first circuit portion and a second conduit arranged to be connected to a second circuit portion, said first conduit and said second conduit being separate, said fluid distributor comprising a body and a shutter movable relative to said body between at least two switching positions to alternately pass said first conduit and said second conduit, said body and said shutter each comprising at least one forward orifice corresponding to the first conduit and at least one return orifice corresponding to the second conduit.

[0005] The invention also relates to a magnetocaloric machine comprising at least one fluid distributor connected to a fluid circuit, a magnetic arrangement, a set of active elements based on magnetocaloric material, said magnetic arrangement and said set of active elements being arranged to be movable relatively to each other to create an alternation of magnetic cycles according to a defined frequency, and a heat transfer fluid arranged to circulate in said fluid circuit through said active elements.

[0006] Prior art Current magnetocaloric (MC) machines have hydraulic distributions made from diverted elements, such as commercial distributors designed for gas or oil, industrial solenoid valves, custom distributors not integrated into the machine design, experimental hydraulic distribution devices not optimized for industrial integration.

[0007] Commercially available diverted distributors designed for gas or oil have a reduced number of cycles and produce significant pressure drop. The service life of these components is insufficient given the number of cycles performed by an MC machine over its lifetime. When diverted distributors are pooled in groups of synchronous active elements (AMR) (Active Magnetic Regenerative), they require a large quantity of pipes, which complicates industrial integration and is not feasible in series production. Their internal design is not mastered and consequently, the flow sections as a function of the stroke are poorly understood, especially since they are not designed to operate in intermediate positions halfway between the expected common switching extreme positions.

[0008] Industrial solenoid valves are inefficient in terms of energy consumption and also have a limited lifespan. Custom distributors have a suitable footprint for prototypes but are difficult to integrate with magnetocaloric technology. They are controlled by cams which are a source of noise and mechanical friction. Fluidic distributors of any kind have a discontinuous movement and therefore require an inertial force to be set in motion. Conventional cam profiles do not allow the kinetic energy of moving distributors to be recovered when they slow down. The discontinuity of movement of distributors driven by cams generates shocks and consequently noise and energy loss. Generally speaking, the use of unsuitable distributors poses problems of lifespan and leaks between circuits and with the external environment. Presentation of the invention

[0009] The present invention aims to overcome these drawbacks by proposing a fluid control device specially designed and adapted to the needs of an MC machine, which is compact, and which can be integrated into the size of the machine, positioned as close as possible to the AMRs to reduce or even eliminate piping and fluid losses, can be shared to simplify the fluid circuits internal to the machine, easily industrialized, driven by a continuous movement, silent, producing few losses by friction or shock and therefore consuming little energy.

[0010] The invention also aims to propose a fluid control device whose internal design is perfectly controlled, the passage sections being able to be determined as a function of the travel of the shutter relative to the body in order to reduce as much as possible the transient phases between the extreme switching positions (open / closed).

[0011] The object of the invention is achieved by a fluid control device as defined in the preamble, characterized in that it further comprises an eccentric control mechanism, movable relative to the body of said at least one hydraulic distributor, said control mechanism being configured to be coupled on the one hand to a rotary actuator and being coupled on the other hand to said shutter to be able to move said shutter relative to said body according to a continuous output movement, from a continuous input movement of said rotary actuator. This arrangement has the advantage of moving the shutters according to a continuous movement, without interruption or jolts, silent, low energy consumption, preserving the integrity of the moving parts to guarantee a service life compatible in particular with that of magnetocaloric machines.In a preferred form of the invention, said control mechanism comprises a driving part secured to said rotary actuator, said driving part having a shape of revolution provided with a geometric center distinct from the center of rotation of said actuator, and a transmission part assembled to said driving part by a pivot connection to be movable in circular translation, said transmission part being coupled to said shutter. This arrangement has the advantage of guaranteeing control of the fluid distribution synchronized with the magnetic cycles within the framework of an MC machine by means of a simple, inexpensive, reliable, durable and maintenance-free mechanism.

[0012] In a first variant embodiment of the invention, said shutter is movable in rotation around an axis of rotation and comprises a coupling end piece eccentric relative to said axis of rotation of the shutter, said transmission plate comprising a circular housing housing said eccentric coupling end piece by a pivot connection.

[0013] In a second variant embodiment of the invention, said shutter is a double-acting shutter which is movable in translation along a translation axis and comprises a follower finger, said transmission plate comprising a groove housing said follower finger by a sliding connection.

[0014] In a third variant embodiment of the invention, said shutter is a single-acting shutter which is movable in translation along a translation axis and comprises a follower member held in contact with the transmission part by a deformable part.

[0015] In the first variant, said first conduit and said second conduit are at least partly coaxial and parallel to the axis of rotation of the shutter. And in the second and third variants, said first conduit and said second conduit each pass through said body transversely to the translation axis of the shutter. The opening amplitudes between the forward orifices, respectively the return orifices, may not be identical, to generate short transition times between the opening and closing of said first conduit, respectively of said second conduit. Preferably, the forward orifice and the return orifice of one of the parts of said body or of said shutter are formed by a narrow oblong opening or by a slot, and the forward orifice and the return orifice of the other part of said body or of said shutter are formed by an opening wider than said narrow opening.This arrangement has the advantage of avoiding the presence of dead volumes and the phenomenon of passive thermo-fluidic regeneration resulting from the forward and return passage of a heat transfer fluid at two different temperature levels in the same conduit or in the same volume of the distributor, which has the effect of fluidically isolating the AMRs from thermal sources.

[0016] The fluid control device advantageously comprises a number N of fluid distributors, arranged in a circle at equal distance from an axis of rotation of said rotary actuator, the shutters of said distributors being controlled by said eccentric control mechanism. This arrangement has the advantage of centralizing and synchronizing the control of said shutters.

[0017] The object of the invention is also achieved by a magnetocaloric machine as defined in the preamble, characterized in that it comprises at least one fluidic control device described above, comprising at least one fluidic distributor per active element, in fluidic contact with a first end of said active element, and in that said fluidic distributor is arranged to circulate said heat transfer fluid through said active element, alternately in a first direction of circulation in a first circuit portion and in a second direction of circulation, reversed with respect to the first direction of circulation, in a second circuit portion of said fluidic circuit, according to a switching frequency between said at least two switching positions of said fluidic distributor which is a multiple of the frequency of the magnetic cycles.

[0018] This arrangement has the advantage of separating the distribution of heat transfer fluid for each AMR, by separating the direction of circulation of the fluid from each AMR in conduits dedicated to each direction of circulation, at any point in the system outside the AMR, between the control devices and the AMRs on the one hand, as well as between the control devices and the thermal sources on the other hand. It guarantees a low leakage rate between the conduits of opposite circulation directions, between the conduits and the AMR, as well as between the conduits and / or the AMR and the external environment. It is also easily configurable, or even controllable, in phase shift with respect to the magnetic field and in opening time, so as to be able to modulate the evolution of the fluid speed with respect to the evolution of the magnetic field applied to the AMR and thus vary the operating point of the AMRs.

[0019] Said eccentric control mechanism is preferably coupled to a rotary actuator coupled to said magnetic arrangement or said set of active elements. This arrangement has the advantage of synchronizing the fluid distribution with the magnetic cycles of the MC machine by means of a simple, inexpensive, reliable, durable and maintenance-free mechanism.

[0020] The number of forward and return ports provided respectively in the body or in the shutter of said at least one fluid distributor may be equal to the number of magnetic poles of said magnetic arrangement, the switching frequency between the two switching positions of said fluid distributor being in this case equal to the frequency of the magnetic cycles generated by said magnetic arrangement. This arrangement makes it possible to exploit all of the magnetic cycles.

[0021] In a preferred form of the invention, said fluid control device comprises two fluid distributors per active element, in fluid contact with a first end and a second end of said active element. This arrangement has the advantage of balancing the circulation of the heat transfer fluid, of guaranteeing the homogeneity of the fluid flow rates between the AMRs, and of ensuring optimal movement of the fluid in alternating back and forth in each AMR.

[0022] In this case, said fluid control device advantageously comprises two control mechanisms arranged on both sides of said set of active elements to control the two fluid distributors per active element, and the two control mechanisms being coupled to said rotary actuator, with or without means of phase shifting one relative to the other. This arrangement makes it possible to balance the forces required for control, while making it possible to introduce a phase shift and / or a configurable, or even automatable, opening time of the alternating flow of the fluid relative to the applied magnetic field to achieve an optimal AMRR (Active Magnetic Regenerative Refrigeration) cycle from an imperfect magnetic field evolution.

[0023] Preferably, the opening amplitude of the forward orifice and the return orifice of one of the parts of said body or said shutter corresponds substantially to the amplitude of a magnetic pole of said magnetic arrangement. This arrangement offers the possibility of a speed evolution in slots, in accordance with the needs of a Brayton or close to Ericsson magnetocaloric cycle in AMRR.

[0024] Said fluid control device advantageously comprises a number N of fluid distributors or pairs of fluid distributors, N being equal to the number of active elements of said assembly, arranged in a circle at equal distance from an axis of rotation of said rotary actuator, and controlled by said control mechanism(s). This arrangement has the advantage of dissociating the distribution of the heat transfer fluid for each AMR and of being able to share the fluid channels leaving the distribution, between the MC machine and the thermal sources, while simplifying the fluid circuits internal to the machine. It also makes it possible to synchronize the fluid control with the evolution of the magnetic field varying in a phase-shifted manner for each AMR.

[0025] Brief description of the drawings

[0026] The present invention and its advantages will appear better in the following description of several embodiments given as non-limiting examples, with reference to the appended drawings, in which:

[0027] - figure 1 is a schematic diagram of an MC machine equipped with a fluidic control device according to a particular embodiment of the invention,

[0028] - figure 2 is a diagram of the fluid circuit of an MC machine equipped with a fluid control device according to a particular embodiment of the invention,

[0029] - Figure 3 A is an axial sectional view of a rotary fluid distributor according to a first embodiment of the invention in a first switching position,

[0030] - figure 3B is a radial sectional view of the fluid distributor of figure 3A along section plane III-III,

[0031] - Figure 4A is an axial sectional view of the fluid distributor of Figure 3A in a second switching position,

[0032] - figure 4B is a radial sectional view of the fluid distributor of figure 4A according to section plane IV-IV,

[0033] - Figure 5 is a perspective view of the body of the fluid distributor of Figures 3A and 4A,

[0034] - figure 6 is a perspective view of the movable shutter of the fluid distributor of figures 3A and 4A,

[0035] - Figure 7 is a plan view of a fluid control device equipped with rotary fluid distributors according to Figures 3A and 4A and an eccentric control mechanism for the movable shutters,

[0036] - Figure 8 is a plan view similar to Figure 7, showing the principle of eccentric control of the movable shutters, - Figure 9 is an axial sectional view of the fluid distributor of Figure 3A integrated in a partially represented MC machine,

[0037] - figure 10 is a perspective view of an MC machine equipped with a fluidic control device according to a preferred embodiment of the invention,

[0038] - figure 11 is a plan view of a fluid control device according to a second embodiment of the invention, equipped with linear fluid distributors and an eccentric control mechanism for the movable shutters,

[0039] - figure 12 is an axial sectional view of the device of figure 11, in a first switching position,

[0040] - Figure 13 is an axial sectional view similar to that of Figure 12, in a second switching position, and

[0041] - figure 14 is an axial sectional view of the device of figure 11 according to an alternative embodiment of the eccentric control mechanism.

[0042] Description of the embodiments

[0043] In the illustrated embodiments, identical elements or parts bear the same reference numbers. Furthermore, terms that have a relative meaning, such as vertical, horizontal, right, left, front, rear, above, below, etc., must be interpreted under normal conditions of use of the invention, and as shown in the figures. The X, Y and Z axes are defined by an orthonormal reference system illustrated in Figure 1. Furthermore, the geometric positions indicated in the description and the claims, such as “perpendicular”, “parallel”, “symmetrical” are not limited to the strict sense defined in geometry, but extend to geometric positions that are close, that is to say which accept a certain tolerance in the technical field considered, without influence on the result obtained.This tolerance is notably introduced by the adverb “substantially”, without this term necessarily being repeated before each adjective. With reference to the figures, the fluid control device 10, 30 according to the invention primarily concerns magnetocaloric machines 1, hereinafter called MC machine 1, for the reasons set out above, but extends to any other technical field in which it is necessary to switch a fluid circuit according to a determined frequency to circulate a fluid alternately in two opposite directions, without mixing the forward fluid and the return fluid.

[0044] In MC 1 machines, the direction of movement of a heat transfer fluid as a function of the magnetic cycles undergone by AMRs depending on whether they are under a magnetic field or outside a magnetic field makes it possible to perform a heat pumping function from magnetic work, or to recover magnetic, and therefore mechanical, work from a temperature differential. The present invention therefore applies to MC heat pumps and thermomagnetic motors, an example of which is described in publication WO2021 / 255040 belonging to the applicant. The principle of active regeneration in a porous matrix (AMR) can be extended to all caloric devices, such as electrocaloric (EC), barocaloric, elastocaloric (eC), etc., without limitation of the vector used to vary the temperature adiabatically or the entropy of the active matrix isothermally.

[0045] Figure 1 schematically illustrates the operation of a machine MC 1, described succinctly, given that it is not the subject of the invention as such. The following description refers to a machine MC 1 operating as a heat pump. In the example shown, it comprises a fixed assembly in the form of a stator S provided with a set of active elements 2 based on magnetocaloric material, hereinafter called AMR 2, and a mobile assembly in the form of a rotor R provided with a magnetic arrangement forming magnetic poles 3. The rotor R is rotated about an axis A, parallel to the axis X of the orthonormal reference frame, by a motor 4 to subject the AMR 2 to a variation in magnetic field and generate within said AMR 2 a temperature variant in the vicinity of their Curie temperature.Of course, the reverse configuration exists in which the AMR 2 assembly is carried by a rotor R and the magnetic arrangement 3 by a stator S, but this configuration complicates the connection of the AMR 2 to the fluid circuit.

[0046] In Figure 1 and solely for the purpose of explaining the operation of the MC 1 machine, only two AMR 2 and only one magnetic pole 3 are shown. The MC 1 machine comprises an internal fluid circuit 5 in which a heat transfer fluid circulates via a pump 6 through said AMR 2 and heat exchangers E1 and E2 allowing the AMR 2 to exchange heat with the external devices DI, D2. Depending on the applications, the heat transfer fluid may be liquid or gaseous. The fluid circuit 5 may also comprise a buffer tank 7 of heat transfer fluid to compensate for any losses of heat transfer fluid and / or variations in the volumes of the heat transfer fluid as a function of the temperature and / or the pressure.

[0047] The fluid circuit 5 comprises two circuit portions 5a and 5b, namely a first circuit portion 5a and a second circuit portion 5b, coupled respectively to a heat exchanger El, called hot exchanger El and a heat exchanger E2, called cold exchanger E2. The two circuit portions 5a, 5b are connected by a fluid control device 10, 30 arranged to connect in series the AMR 2 to the heat exchangers El, E2 alternately in one and the other circuit portions 5a, 5b and create an alternation of thermal cycles at a determined frequency, synchronized with the alternation of the magnetocaloric cycles induced by the rotation of the rotor R.

[0048] In the example shown, the fluid control device 10, 30 comprises for each AMR 2 two fluid distributors 11, 31 arranged on either side of the AMR 2, and more precisely, attached to the ends of the AMR to be in direct fluid contact with the AMR without any intermediate connection or pipe. The fluid control device 10, 30 is designed to impose a single direction of circulation of the heat transfer fluid in the circuit portions 5a, 5b and in the heat exchangers E1, E2, illustrated by the arrows F. In an embodiment not shown, the fluid control device 10, 30 may comprise for each AMR 2 only a single fluid distributor 11, 31 arranged on a single side of the AMR 2. In this case, the opposite side of the AMR 2 comprises members for controlling the direction of circulation of the heat transfer fluid in the circuit portions 5a, 5b to impose the single direction of circulation of the heat transfer fluid in the heat exchangers E1, E2.

[0049] With reference to Figure 1, the operation of the machine 1 is briefly described. In a first thermal cycle, the fluid distributors 11 are in a first switching position, as illustrated in Figure 1 and the heat transfer fluid circulates in a first circuit portion 5a shown in solid lines in a clockwise direction. It passes through the AMR 2 located at the bottom of Figure 1 which undergoes a heating cycle being located in the magnetic field of one of the magnetic poles 3 of the rotor R, passes through the hot exchanger El where it restores the collected heat to an external device Dl, then passes through the AMR 2 located at the top of Figure 1 which undergoes a cooling cycle being located outside the magnetic field, passes through the cold exchanger E2 where it restores the collected cold to an external device D2.

[0050] In a second thermal cycle, the fluid distributors 11 are in a second switching position, not shown in Figure 1, and the heat transfer fluid circulates in a second circuit portion 5b, which is shown, outside the exchangers E1 and E2, the pump 6 and the reserve 7, in short broken lines in the counterclockwise direction. It passes through the AMR 2 located at the bottom of Figure 1 which is now undergoing a cooling cycle being located outside the magnetic field (not shown), passes through the cold exchanger E2 where it returns the collected cold to an external device D2, then passes through the AMR 2 located at the top of Figure 1 which is now undergoing a heating cycle being located in the magnetic field of one of the magnetic poles 3 of the rotor R, passes through the hot exchanger E1 where it returns the collected heat to an external device D1.

[0051] The first and second thermal cycles are repeated according to a switching frequency determined by the fluid control device 10, 30 which comprises a control mechanism 20 for the fluid distributors 11, 31. The control mechanism 20 can be coupled to the motor 4, or to a dedicated actuator (not shown). If it is coupled to a dedicated actuator, then a control unit (not shown) is provided to synchronize the operation of the dedicated actuator with the motor 4 of the rotor R in the case in particular of a magnetic cold generator.

[0052] Figure 2 schematically illustrates a part of the fluid circuit 5 of the machine MC 1 equipped with the fluid control device 10, 30 of the invention. In this example, the machine MC 1 is seen from one of its ends, in the plane YZ, the axis of rotation A of the rotor R being perpendicular to said plane. The rotor R comprises two diametrically opposed magnetic poles 3, each extending over approximately a quarter of a circle. Eight AMR 2 are regularly distributed around the axis A, including four AMR 2 located in the magnetic field of the magnetic poles 3, and four AMR 2 located outside the magnetic field of the magnetic poles 3.The fluid circuit 5 is illustrated by a large circle corresponding to the first portion of circuit 5a in which the heat transfer fluid circulates from the tank 7 and the pump 6, through the cold exchanger E2, towards the AMR 2 under a magnetic field, via a first of the fluid distributors 11, and by a small circle concentric with the large circle still corresponding to the first portion of circuit 5a in which the heat transfer fluid circulates from the other AMR 2, which are not exposed to the magnetic field, via a second of the fluid distributors 11, towards the tank 7.Figure 2 also shows the control mechanism 20 of the fluid control device 10, 30 shown diagrammatically by an eccentric central part coupled to the axis A in which are housed coupling tips 21 linked to the fluid distributors 11, 31 to generate their movement from one switching position to another synchronously with the variation of the magnetic cycles.

[0053] With particular reference to a first variant of the invention shown in Figures 3A to 9, the fluid distributors 11 are rotary distributors and positioned axially in the machine MC 1, parallel to the axis A. They each comprise a tubular body 12 with an axis B parallel to the axis A, mounted where appropriate in the stator S and a shutter 13 in the form of a slide movable in rotation relative to the body 12 along the axis B, between at least two switching positions. In the example shown, the shutter 13 passes right through the body 12, and comprises a first end in direct communication with an AMR 2, and a second end, provided with the coupling end piece 21. This coupling end piece 21 has a shape of revolution whose geometric center C is eccentric relative to the axis of rotation B of the shutter 13.

[0054] The fluid distributor 11 comprises a first conduit C1 and a second conduit C2 fluidly separated from each other. It is particularly designed to alternately pass the first conduit C1 and the second conduit C2 according to a switching frequency determined and synchronized with the magnetic cycles undergone by the AMR 2.

[0055] The first conduit C1 is arranged to be connected to the first circuit portion 5a in a first switching position of the distributor illustrated in FIGS. 3A and 3B, in which the heat transfer fluid enters the AMR 2 (forward circuit). The body 12 and the shutter 13 each comprise a forward orifice OA1, OA2 opposite each other. The first conduit C1 comprises the forward orifice OA1 of the body 12 which communicates directly with the first circuit portion 5a and with the forward orifice OA2 of the shutter 13, which preferably opens into an annular channel 14 which communicates via an openwork intermediate zone 15 into a central channel 16, which communicates directly with the AMR 2 at a first end.

[0056] The second conduit C2 is arranged to be connected to the second circuit portion 5b in a second switching position of the distributor illustrated in FIGS. 4A and 4B, in which the heat transfer fluid leaves the AMR 2 (return circuit) through its first end. The body 12 and the shutter 13 each comprise a return orifice OR1, OR2 opposite. The second conduit C2 preferably comprises a peripheral channel 17 arranged around the central channel 16, which communicates directly with the AMR 2 at its first end, and with the return orifice OR2 of the shutter 13, which opens into the return orifice OR1 of the body 12, which communicates directly with the second circuit portion 5b.

[0057] Figure 5 illustrates the body 12 of the fluid distributor 11 showing the relative arrangement between the forward orifice OA1 and the return orifice OR1, as well as the shape of the opening of these orifices. Axially, they are offset by a distance d corresponding to the distance existing between the forward orifices OA2 and return orifices OR2 of the shutter 13. Radially, they are offset by an angle defined by the center distance between a magnetic zone and a non-magnetic zone. The forward orifices OA1 and return orifices OR1 have an enlarged opening which extends radially from the axis of rotation B of the shutter 13 over an angle a, illustrated in Figures 3B and 4B, determined by the magnetic zone corresponding to the angular extent of the magnetic pole 3 on the one hand, and by the non-magnetic zone corresponding to the angular extent between two consecutive magnetic poles 3.In this case, the angle a is substantially equal to 90°, corresponding to the extent of a magnetic pole 3, which is relevant for a machine comprising two diametrically opposed magnetic poles 3. The opening of the forward orifices OA1 and return OR1 extends over an axial length L preferably corresponding to the length of the forward orifices OA2 and return OR2 of the shutter 13. The forward orifices OA1 and return OR1 of the body 12 of the distributor 11 preferably have an identical section. Each forward orifice OA1 and OR1 has in the example an opening of rectangular section inclined radially in the body 12. This shape is only a non-limiting example and can vary depending on the desired velocity profiles for the heat transfer fluid as explained below.

[0058] Figure 6 illustrates the shutter 13 of the fluid distributor 11 showing the relative arrangement between the flow orifice OA2 and the return orifice OR2. Axially, they are offset by the distance d. Radially, they are aligned on a generatrix of the shutter 13. The flow orifices OA2 and return OR2 preferably have a narrow opening of oblong shape, which extends axially over a length L corresponding to the length of the flow orifices OA1 and return OR1 of the body 12. The flow orifices OA2 and return OR2 of the shutter 13 of the distributor 11 preferably have an identical section and determined to be equal to the passage section through an AMR 2, in order to avoid pressure losses.

[0059] The number of pairs of a forward orifice OA2 and a return orifice OR2 is a function of the number of magnetic poles 3 of the machine MC 1. In the example illustrated, the shutter 13 comprises two pairs of a forward orifice OA2 and a return orifice OR2 which are aligned respectively on two diametrically opposed generatrices of the shutter 13, and the machine MC 1 comprises two diametrically opposed magnetic poles 3. In this configuration, the rotation frequency of the shutter 13 is equal to the rotation frequency of the magnetic arrangement.

[0060] The amplitude and shape of the opening of the forward orifices OA1, OA2 and the return orifices OR1, OR2 are determined in order to make maximum use of the heat transfer fluid which circulates through the AMR 2 during the entire duration of each magnetic cycle, given that the opening amplitude corresponds to the amplitude of a magnetic pole 3. It also makes it possible to drastically reduce the duration of the transient phases between two consecutive magnetic cycles thanks in particular to the oblong shape of the forward orifices OA2 and return orifices OR2 of the shutter 13 generating very short opening and closing times of the fluid circuit.

[0061] In the transient phases of the magnetic cycles corresponding to the positions in which the magnetic field generated by the magnetic poles 3 is highly non-uniform, the restriction and stopping of the circulation of the heat transfer fluid are achieved when the enlarged orifices of at least one of the fluid distributors 10 at at least one of the ends of F AMR 2 do not open onto one of the narrow orifices of said distributor. The shape of the enlarged orifices, in an arc of a circle, triangle, rectangular, etc., makes it possible to achieve restrictions in the fluid passages upon closing which are progressive, to slow down the heat transfer fluid before stopping and gradually restore its circulation upon opening. This makes it possible to avoid water hammer and to obtain a change in the fluid speed which is favorable and in phase with the change in the magnetic field applied in the transient magnetic phases.A square shape of the ends of the narrow orifices and / or the enlarged orifices allows an abrupt closure of the fluid passage section.

[0062] Figures 7 and 8 illustrate the control mechanism 20 of a fluid control device 11 arranged to control the synchronous movement of the shutters 13 of a number N of fluid distributors 11. In the example illustrated, the fluid control device 11 comprises sixteen fluid distributors 11, arranged in a circle around the axis A of the machine MC 1 and distributed regularly, in which each fluid distributor 11 corresponds to an AMR 2. The control mechanism 20 is eccentric.

[0063] The control mechanism 20 comprises a driving part 22 having a shape of revolution, such as an annular plate, provided with a geometric center D distinct from the center of rotation of the motor 4 corresponding to the axis A. The driving part 22 is fitted onto a shaft 8 of the motor 4 to be driven in a continuous eccentric rotational movement by said motor. It also comprises a transmission part 23 having a shape of revolution, such as an annular plate, provided with a geometric center coinciding with the center D. The transmission part 23 is assembled to the driving part 22 by a pivot connection to be driven in a circular translational movement. The transmission part 23 further preferably comprises a number N of circular housings 24 arranged in a circle around the axis A and distributed regularly, each circular housing 24 being assembled to a coupling end piece 21 of one of the shutters 13 by a pivot connection.Thus, the continuous rotation of the motor 4 of the magnetic arrangement preferably causes the continuous rotation in the same direction and synchronously of the shutters 13 of all the distributors 11, with a phase shift from one to the other determined by their angular arrangement relative to the magnetic poles 3.

[0064] Figure 8 represents the fictitious deformable parallelogram which allows the transmission of the rotational movement of the motor 4 to a rotational movement of the shutter 13 via a circular translational movement of the transmission part 23. The parallelogram comprises two fixed points, namely the axes of rotation A of the motor 4 and B of the shutter 13, and is deformed by the continuous rotation of the two moving points, namely the geometric center D of the driving part 22 and of the transmission part, and the geometric center C of the coupling end piece 21, around the two fixed points A and B respectively.

[0065] Figure 9 illustrates an example of integration of a fluid distributor 11 in the stator S of a machine MC 1, facing an AMR 2. In the right part of the figure, the AMR 2 is mounted in a specific support 9, which is fixed and is part of the stator S. The fluid distributor 11 is mounted in one of the parts SI of the stator S, in direct contact with the support 9 of the AMRs. The shutter 13 of the fluid distributor 11 extends through the support 9 to the corresponding end of the AMR 2. The fluid seal between the different parts of the distributor, the stator part SI and the support 9 is ensured by sealing members OE. In the left part of the figure, the coupling end piece 21 is mounted in a circular housing 24 of the transmission part 23. The forward orifices OA1, OA2 of the fluid distributor 11 communicate with the first portion of circuit 5a, visible in this figure, which is formed by channels directly drilled in the part S 1 of the stator.This arrangement eliminates the need for piping and corresponding fittings.

[0066] Figure 10 shows an example of an MC 1 machine assembled in the form of a compact module, ready to be installed in a thermal installation. The MC 1 machine has two fluid ports at one of its ends: an inlet port OE and an outlet port OS for the circulation of the heat transfer fluid between the core of the machine and the hot E1 and cold E2 exchangers via a pipe connection to transport the thermal energy to the sources. The various conduits and channels internal to the machine have the advantage of being able to be pooled to open into common collectors also provided inside the machine for the inlet and outlet of the heat transfer fluid, limiting the fluid connection with an application external to the machine to the two ports OE and OS.

[0067] Figures 11 to 14 illustrate another fluid control device 30 according to an alternative embodiment of the invention. In this alternative, the fluid distributors

[0068] 31 are linear distributors positioned radially in the machine MC 1, i.e. perpendicular to the axis A. They each comprise a hollow body 32 of axis E, mounted in the stator S and a shutter 33 in the form of a slide movable in translation relative to the body 32 along the axis E, between at least two switching positions. The contact surface between the body 32 and the shutter 33 may be cylindrical as in the previous example to facilitate machining and sealing. However, any other shape of contact surface may be suitable. The external surface of the body 32 may be of any shape and for example polygonal as illustrated, without this shape being limiting. In the example shown, the body

[0069] 32 therefore comprises a first face (on the right in figures 12 and 13) in direct communication with an AMR 2, and a second face (on the left in figures 12 and 13) in direct communication with the circuit portions 5a and 5b.

[0070] In the variant shown, the shutter 33 is a double-acting shutter. It has an L-shaped end, the return of the L forming a follower finger 21 which is housed in an annular groove 25 of the transmission part 23 for driving in both directions of translation of the shutter 33 along the axis T. Of course, any other follower member moving in said groove may be suitable, such as a fork with a roller, a pin, or the like.

[0071] In another variant not illustrated, the shutter 33 may be single-acting. In this case, it comprises one end forming a follower member held in contact against the transmission part 23 by a deformable part, such as a return spring, a pressurized fluid, a compressible gas, or the like.

[0072] The fluid distributor 31 comprises a first conduit C1 and a second conduit C2 fluidically separated from each other. The first conduit C1 is arranged to be connected to the first circuit portion 5a in a first switching position of the distributor illustrated in FIG. 12, in which the heat transfer fluid enters the AMR 2 (forward circuit). The body 32 and the shutter 33 each comprise a forward orifice OA1, OA2 opposite each other. The first conduit C1 comprises a first forward orifice OA1 provided in a first wall of the body 32, which communicates directly with the first circuit portion 5a and with the forward orifice OA2 of the shutter 33, which communicates with a second forward orifice OA1 provided in a second wall of the body 32 parallel to the first wall, which communicates directly with the AMR 2 at its first end.

[0073] The second conduit C2 is arranged to be connected to the second circuit portion 5b in a second switching position of the distributor illustrated in FIG. 13, in which the heat transfer fluid leaves the AMR 2 (return circuit) through its first end. The body 32 and the shutter 33 each comprise a return orifice OR1, OR2 opposite each other. The second conduit C2 comprises a first return orifice OR1 provided in the second wall of the body 32, which communicates directly with the AMR 2 at its first end, and with the return orifice OR2 of the shutter 33, which communicates with a second return orifice OR1 provided in the first wall of the body 32, which communicates directly with the second circuit portion 5b.

[0074] The forward orifice OA1 and the return orifice OR1 provided in the two parallel walls of the body 32 are separated in the axis E by a distance d corresponding to the distance existing between the forward orifices OA2 and return orifices OR2 of the shutter 33. They are further aligned on the axis E and comprise a narrow opening of oblong shape, oriented perpendicular to the axis E over a width ^corresponding to the width of the forward orifices OA2 and return orifices OR2 of the shutter 33. The forward orifices OA1 and return orifices OR1 of the body 32 preferably have an identical section and determined to be equal to the passage section through an AMR 2, in order to avoid pressure losses.

[0075] The forward orifices OA2 and return OR2 provided in the shutter 33 have an enlarged opening which extends along the axis E over a height determined by the magnetic zone corresponding to the angular extent of the magnetic pole 3 on the one hand, and by the non-magnetic zone corresponding to the angular extent between two consecutive magnetic poles 3. The opening of the forward orifices OA2 and return OR2 extends over a width ^perpendicular to the axis E preferably corresponding to the width of the forward orifices OA1 and return OR1 of the body 32. The forward orifices OA2 and return OR2 of the shutter 33 preferably have an identical section. The design of the forward orifices OA1, OA2 and return OR1, OR2 allows the same advantages as those described with reference to the previous fluid control device 10. Figure 11 shows the eccentric control mechanism 20 as described with reference to Figures 7 and 8, adapted to the fluid control device 30.It comprises the same parts, namely the driving part 22 secured to the shaft 8 of the motor 4, and the transmission part 23 assembled to the driving part 22 by a pivot connection, the two parts having the same geometric center D. The transmission part 23 further comprises the groove 25, for example annular centered on the axis D, in which the follower finger 21' of the shutters 33 is assembled by a sliding connection. In this variant, the continuous rotation of the motor 4 of the magnetic arrangement causes the sinusoidal and synchronous translation of the shutters 33 of all the distributors 31, with a phase shift from one to the other determined by their angular arrangement relative to the magnetic poles 3.In this configuration, the diametrically opposed shutters 33 move in the same direction of translation T because they are linked to the same transmission part 23, which requires reversing the location of the forward and return orifices for these distributors.

[0076] Figure 14 shows a variant of the eccentric control mechanism 20 adapted to the fluid control device 30. It comprises an additional transmission part 26, parallel to the transmission part 23, but phase-shifted by 180°. A first half of the shutters 33 is connected to the transmission part 23 with geometric center D, while the other half of the shutters 33, diametrically opposite the first half, is connected to the additional transmission part 26 with geometric center D', the two geometric centers D and D' being diametrically opposite with respect to the axis A. This configuration makes it possible to move the diametrically opposite shutters 33 in opposite translation directions T, which makes it possible to use identical fluid distributors 31 for all the AMR 2 regardless of their position with respect to the control mechanism 20.

[0077] According to the embodiment variants of the machine MC 1, the fluid control device 10, 30 according to the invention may comprise two fluid distributors 11, 31 per AMR 2, directly in fluid contact with the two ends of the AMR. In this case, the fluid control device 10, 30 may comprise two control mechanisms 20 arranged on both sides of the AMR 2 to control the two fluid distributors 11, 31 per AMR 2. The two control mechanisms 20 are coupled to the motor 4, with or without means for phase shifting one relative to the other depending on the desired operation.

[0078] The present invention is of course not limited to the embodiments described but extends to any modification and variant obvious to a person skilled in the art within the limits of the appended claims. Furthermore, the technical characteristics of the different embodiments and variants mentioned above may be, in whole or in some cases, combined with each other.

Claims

Claims

1. Fluid control device (10, 30), comprising at least one fluid distributor (11, 31), comprising at least a first conduit (Cl) arranged to be connected to a first circuit portion (5 a), and a second conduit (C2) arranged to be connected to a second circuit portion (5 b), said first conduit and said second conduit being separate, said fluid distributor comprising a body (12, 32), and a shutter (13, 33) movable relative to said body between at least two switching positions to alternately pass said first conduit (Cl) and said second conduit (C2), said body and said shutter each comprising at least one forward orifice (OA1, OA2) corresponding to the first conduit (Cl) and at least one return orifice (OR1, OR2) corresponding to the second conduit (C2), characterized in that said control device further comprises at least one eccentric control mechanism (20), movable relative to the body (12,32) of said at least one hydraulic distributor, said control mechanism (20) being configured to be coupled on the one hand to a rotary actuator (4) and being coupled on the other hand to said shutter (13, 33) to be able to move said shutter (13, 33) relative to said body (12, 32) according to a continuous output movement, from a continuous input movement of said rotary actuator.,

2. Fluid control device according to claim 1, characterized in that said control mechanism (20) comprises a driving part (22) integral with said rotary actuator (4), said driving part having a shape of revolution provided with a geometric center (D) distinct from an axis of rotation (A) of said actuator, and a transmission part (23) assembled to said driving part (22) by a pivot connection to be movable in circular translation, said transmission part (23) being coupled to said shutter (13, 33).

3. Fluid control device according to claim 2, characterized in that said shutter (13) is movable in rotation around an axis of rotation (B) and comprises a coupling end piece (21) eccentric with respect to the axis of rotation (B) of said valve, and in that said transmission part (23) comprises a circular housing (24) housing said coupling end piece (21) by a pivot connection.

4. Fluid control device according to claim 2, characterized in that said shutter (33) is a double-acting shutter which is movable in translation along a translation axis (T) and comprises a follower finger (21'), and in that said transmission part (23) comprises a groove (25) housing said follower finger (21') by a sliding connection.

5. Fluid control device according to claim 2, characterized in that said shutter is a single-acting shutter which is movable in translation along a translation axis (T) and comprises a follower member held in contact with the transmission part (23) by a deformable part.

6. Fluid control device according to claim 3, characterized in that said first conduit (Cl) and said second conduit (C2) are at least partly coaxial and parallel to the axis of rotation (B) of the shutter (13).

7. Fluidic control device according to any one of claims 4 and 5, characterized in that said first conduit (Cl) and said second conduit (C2) each pass through said body (32) transversely to the translation axis (T) of the shutter (33).

8. Fluidic control device according to any one of claims 5 to 7, characterized in that the opening amplitudes between the forward ports (OA1, OA2), respectively between the return ports (OR1, OR2), are not identical to generate short transition times between the opening and closing of said first conduit (Cl), respectively of said second conduit (C2).

9. Fluid control device according to claim 8, characterized in that the flow orifice (OA1, OA2) and the return orifice (OR1, OR2) of one of the parts of said body (12, 32) or of said shutter (32, 33) are formed by a narrow oblong opening or by a slot, and in that the flow orifice (OA1, OA2) and the return orifice (OR1, OR2) of the other part of said body or of said shutter are formed by an opening wider than said narrow opening.

10. Fluid control device according to any one of claims 1 to 9, characterized in that it comprises a number N of fluid distributors (11, 31), arranged in a circle at equal distance from an axis of rotation (A) of said rotary actuator (4), and in that the shutters (11, 31) of said distributors are controlled by said eccentric control mechanism (20).

11. Magnetocaloric machine (1) comprising at least one fluid distributor (11, 31) connected to a fluid circuit (5), a magnetic arrangement (3), a set of active elements (2) based on magnetocaloric material, said magnetic arrangement and said set of active elements being arranged to be movable relative to each other to create an alternation of magnetic cycles according to a defined frequency, and a heat transfer fluid arranged to circulate in said fluid circuit (5) through said active elements (2), characterized in that it comprises at least one fluid control device (10, 30) according to any one of claims 1 to 10, comprising at least one fluid distributor (11, 31) per active element (2), in fluid contact with a first end of said active element, and in that said fluid distributor (11, 31) is arranged to circulate said heat transfer fluid through said active element (2), alternately in a first direction of circulation in a first circuit portion (5a) and in a second direction of circulation, reversed with respect to the first direction of circulation, in a second circuit portion (5b) of said fluid circuit (5), according to a switching frequency between said at least two switching positions of said fluid distributor which is a multiple of the frequency of the magnetic cycles.

12. Magnetocaloric machine according to claim 11, characterized in that said eccentric control mechanism (20) is coupled to a rotary actuator (4) coupled to said magnetic arrangement (3) or to said set of active elements (2).

13. Magnetocaloric machine according to any one of claims 11 and 12, characterized in that the number of forward orifices (OA1, OA2) and return orifices (OR1, OR2) provided in the body (12, 32) and the shutter (13, 33) of said at least one fluid distributor (11, 31) is equal to the number of magnetic poles (3) of said magnetic arrangement, and in that the switching frequency between the two switching positions of said fluid distributor (11, 31) is equal to the frequency of the magnetic cycles generated by said magnetic arrangement.

14. Magnetocaloric machine according to any one of claims 11 to 13, characterized in that said fluidic control device comprises two fluidic distributors (11, 31) per active element (2), in fluidic contact with the two ends of said active element.

15. Magnetocaloric machine according to claim 14, characterized in that the fluidic control device (10, 30) comprises two control mechanisms (20) arranged on both sides of said set of elements active elements (2) for controlling the two fluid distributors (11, 31) by active element (2), and in that the two control mechanisms are coupled to said rotary actuator (4).

16. Magnetocaloric machine according to any one of claims 11 to 15, characterized in that the opening amplitude of the forward orifice (OA1, OA2) and of the return orifice (OR1, OR2) of one of the parts of said body (12, 32) or of said shutter (13, 33) corresponds substantially to the amplitude of a magnetic pole (3) of said magnetic arrangement.

17. Magnetocaloric machine according to any one of claims 11 to 16, characterized in that said fluidic control device (10, 30) comprises a number N of fluidic distributors (11, 31) or pairs of fluidic distributors, N being equal to the number of active elements (2) of said assembly, arranged in a circle at equal distance from an axis of rotation (A) of said rotary actuator. (4), and controlled by said control mechanism(s) (20).

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